WO2005108796A1

WO2005108796A1 - A centrifugal pump with high force ratio, inner reduction friction and centripetal increasing pressure and its method threrof

Info

Publication number: WO2005108796A1
Application number: PCT/CN2004/000467
Authority: WO
Inventors: Zigang Jiang
Original assignee: Zigang Jiang
Priority date: 2004-05-10
Filing date: 2004-05-10
Publication date: 2005-11-17

Abstract

A centrifugal pump with high force ratio, inner reduction friction and centripetal increasing pressure and its method thereof belong to a centrifugal pump of impeller machine. Blades of the impeller with L-shape form fluid channel therebetween. T fluid channel is curved in the sense of opposite tangent direction of rotation and provides low flowing speed. Comb vanes regularly arranged in the fluid channel form even speed turnoffs to restrain relative vortex. The end chamber of the impeller to be charged can carry out gas-phase friction and reduce one scale of wastage. To compare the vortex channel centripetal guide impeller and centripetal increasing pressure module comprised of different impellers with modularize combination single stage and multistage pump, the former can improve efficiency, cavitation resistance and reduce cost to a great extent.

Description

高势比、内减摩、向心增压离心泵及其技术组合方法技术领域 High potential ratio, internal friction reduction, centrifugal booster centrifugal pump and technical combination method thereof

本发明涉及离心泵的结构、原理的改进及其技术组合方法。改进设计形成高势比、内减摩、向心增压型离心泵产品，在节流、效率、功率、气蚀诸特性上体现高性能，或同时在体积、成本和使用方便度等方面具有优势。新方法用于在各新技术间或新技术与现有技术间进行模块化组合，能形成更多种类的离心泵新产品。 The invention relates to the improvement of the structure and principle of a centrifugal pump and a technical combination method thereof. Improve the design to form a high potential ratio, internal friction reduction, centrifugal booster centrifugal pump product that reflects high performance in terms of throttling, efficiency, power, and cavitation, or at the same time in terms of volume, cost and ease of use Advantage. The new method is used for modular combination between new technologies or between new technologies and existing technologies, which can form more kinds of new centrifugal pump products.

离心泵由叶轮、'导流器、机壳和轴系部件组成。其中，叶轮为带动液流旋转对其做功的部件，导流器为将液流动能转换为压力势能的部件。离心泵是一种使用量最大的流体机械，广泛装备于国民经济各行业。在矿山、电力、石油、化工、机械、轻纺、环境、城乡建设和水利等行业领域，在传统的农、林、牧、渔各业，离心泵都是一种常用设备，其装机容量非常巨大。例如，仅中国农用排灌泵的装机量即超过 1亿千瓦，其中多数是离心泵。背景技术 The centrifugal pump consists of an impeller, a deflector, a casing, and a shafting component. Among them, the impeller is a component that drives the liquid flow to perform work, and the deflector is a component that converts liquid flow energy into pressure potential energy. Centrifugal pumps are the most widely used fluid machinery and are widely equipped in various industries of the national economy. In the fields of mining, electric power, petroleum, chemical industry, machinery, light textile, environment, urban and rural construction, and water conservancy, in the traditional agriculture, forestry, animal husbandry, and fishery industries, centrifugal pumps are all commonly used equipment, and their installed capacity is very huge. For example, the installed capacity of agricultural irrigation and drainage pumps in China alone exceeds 100 million kilowatts, most of which are centrifugal pumps. Background technique

离心泵 17世纪末发明于法国，至今已有 300多年的历史。其基本方程 18世纪中叶就已导出，至今仍然是新理论演进的共同基础。水泵被人类用作第一大流体驱动设备的历史，是与工业文明和城市化进程相伴随的，一些人甚至将水泵比作国民经济的心脏，但大多数人包括发明人在内并不知晓或不曾理解。这里所说的水泵，主要还是指离心泵。 Centrifugal pumps were invented in France at the end of the 17th century and have a history of more than 300 years. Its basic equations were derived in the middle of the 18th century and are still the common basis for the evolution of new theories. The history of water pumps being used by humans as the largest fluid-driven device is accompanied by industrial civilization and urbanization. Some people even compare water pumps to the heart of the national economy, but most people, including the inventors, do not know Or never understood. The water pump mentioned here mainly refers to the centrifugal pump.

自 19世纪以来，特别是 20世纪末，离心泵研究较为热门，其设计和生产工艺经历过多次重要改进，其性能不断提高。然而，现有技术产品还是不尽如人意，其效率仍然偏低，其设计制造成本仍然偏高，其安装和调节模式也经常不能满足用户的需要。 Since the 19th century, especially at the end of the 20th century, the research on centrifugal pumps has been more popular. Its design and production process have undergone several important improvements, and its performance has been continuously improved. However, the existing technology products are still not satisfactory, their efficiency is still low, their design and manufacturing costs are still high, and their installation and adjustment modes often fail to meet the needs of users.

离心泵效率偏低的主要原因在于以下几个方面： The main reasons for the low efficiency of centrifugal pumps are the following:

第一，叶轮输出流速太高，动能比例太大。动能在导流器中的水力损耗与速度的平方甚至三次方成正比，当速度太高时，动能的大部分将被损耗掉。 First, the impeller output velocity is too high and the kinetic energy ratio is too large. The hydraulic loss of kinetic energy in the deflector is proportional to the square or even the cube of the speed. When the speed is too high, most of the kinetic energy will be lost.

流速太高导致离心泵效率降低，这为学术界所公知。所有的学术论著都主荐后弯式叶轮，就是为了降低速度。当今的离心泵产品，绝大多数釆用了这种叶轮，但问题仍然没有解决。从下面的分析可知，后弯式叶片并没有使液流速度降低多少。 Too high a flow rate causes a reduction in the efficiency of the centrifugal pump, which is well known in the academic community. All academic treatises recommend backward curved impellers to reduce speed. Most of today's centrifugal pump products use this impeller, but the problem remains unsolved. It can be seen from the following analysis that the backward curved blade does not reduce the flow velocity much.

根据出口速度三角形，叶轮出口液流的绝对速度 v₂是出口牵连速度 U₂与相对速度 W₂ 的矢量和，由于 ^¥₂较11₂小一个数量级，因而对 V₂的影响很小。在普遍因袭的速度图中，相对速度w₂的图形比例常被夸大（画小了看不清），以致于看起来出口角 3 ₂较小的后弯式叶片可以使绝对速度 v₂降低很多。实际上，由于叶轮出口面积大，其出口相对速度 w₂ 较之圆周速度 u₂是很小的。按真实比例构造的三角形显示，出口角 β₂的邻边 u₂很大，而另一邻边 w₂却很小，变动 β₂并不能显著改变其对边 v₂的长度。因此，传统叶轮比功的欧 Y_T=u₂v₂cos a₂— uiV!Cos a ! ^o.5 (u₂ ²— u +Wi²— w₂ ²) +0.5 (v₂ ²~Vi²)中的比势能项 0.5u₂ ²和比动能项 0.5v₂ ²在数值上是很接近的，由于其他比能项的数值都很小，因而叶轮输出势动比实际上接近于 1。 According to the exit velocity triangle, the absolute velocity v ₂ of the impeller exit flow is the vector sum of the exit implication velocity U ₂ and the relative velocity W _2. Since ^ ¥ ₂ is an order of magnitude smaller than 11 ₂ , the effect on V ₂ is small. In the general velocity map, the graphic proportion of the relative speed w ₂ is often exaggerated (the picture is too small to see clearly), so that it seems that the backward curved blade with a smaller exit angle 3 ₂ can reduce the absolute speed v ₂ much. . In fact, due to the large area of the impeller outlet, which outlet relative velocity than the circumferential velocity w ₂ u ₂ it is small. The triangle constructed according to the real proportion shows that the adjacent side u _{2 of the} exit angle β ₂ is large, while the other adjacent side w ₂ is small. The variation β ₂ cannot significantly change the length of the opposite side v ₂ . Therefore, Y _T = u ₂ v ₂ cos a ₂ — uiV! Cos a! ^ O.5 (u ₂ ² — u + Wi ² — w ₂ ² ) +0.5 (v ₂ ² ~ Vi ² ) in The specific potential energy term 0.5u ₂ ² and the specific kinetic energy term 0.5v ₂ ² are very close in value. Since the values of the other specific energy terms are small, the impeller output potential-to-motion ratio is actually close to 1.

髙速入导加重了导流负荷，降低了导流流程的水力效率，这是离心泵水力效率和总效率偏低的首要原因。 The rapid inflow diversion increases the diversion load and reduces the hydraulic efficiency of the diversion process. This is the primary reason for the low hydraulic and total efficiency of the centrifugal pump.

第二，在叶轮流程中，流场速度分布很不均匀，而且很不稳定，湍流、回流、脱流等现象一直难以消除，严重影响了该流程的水力效率。在叶轮流程与导流流程的结合部，液流处于严重的欠约束状态，以致相对涡旋外展，湍流、回流、脱流驱动力互馈，影响区域扩大，局部激励现象严重，所有这些因素都导致损耗增加。 Second, in the impeller process, the velocity distribution of the flow field is very uneven and unstable, and turbulence, backflow, and outflow have always been difficult to eliminate, which seriously affected the hydraulic efficiency of the process. At the junction of the impeller process and the diversion process, the liquid flow is in a severely under-constrained state, so that the relative vortex abduction, turbulence, backflow, and deflow driving force mutual feedback, the area of influence is enlarged, and the local excitation phenomenon is serious. All these factors Both result in increased losses.

第三，叶轮轮盘摩擦损耗占有不容忽视的比例，降低了内机械效率。该项损耗与液流速度无关，却与叶轮直径及其转速高幂次锐相关。随着叶轮直径或转速增加，损耗急剧增大。对于低比转数和高扬程的离心泵，轮盘摩擦可能造成 10%以上的效率下降。 Thirdly, the friction loss of the impeller discs can not be ignored, which reduces the internal mechanical efficiency. This loss has nothing to do with the velocity of the liquid flow, but it has a sharp correlation with the impeller diameter and its high power. As the impeller diameter or speed increases, the losses increase dramatically. For centrifugal pumps with low specific speeds and high heads, disc friction may cause a decrease in efficiency of more than 10%.

上述三大原因，加上其他各类损耗的存在，决定了离心泵不可能有令人满意的效率指标。市场提供的产品样本资料显示，现有技术产品的标称效率大部分在 50%上下，最高者标称 82%，最低者只有 30%多，其平均值在 50%〜60%之间。 The above three major reasons, together with the existence of other types of losses, determine that the centrifugal pump cannot have a satisfactory efficiency index. The product sample data provided by the market shows that the nominal efficiency of the prior art products is mostly around 50%, the highest is nominally 82%, and the lowest is more than 30%, with an average value between 50% and 60%.

标称效率是运行于最优工况时才能达到的指标。实际上，由于泵的型谱规格的离散分布与实际需求的连续分布的差异，由于泵的应用条件的可能的变动，压力和流量等主要参数在运行中经常需要使用外部手段进行调节，这使得离心泵偏离设计工况运行的情况十分普遍，造成了离心泵实际运行效率的统计分布性降低。其根源在于： Nominal efficiency is an index that can only be achieved when operating under optimal conditions. In fact, due to the discrepancies between the discrete distribution of the pump's profile specifications and the continuous distribution of actual needs, and due to possible changes in the application conditions of the pump, main parameters such as pressure and flow often need to be adjusted using external means during operation, which makes It is very common for the centrifugal pump to deviate from the design conditions, which has caused the statistical distribution of the actual operating efficiency of the centrifugal pump to decrease. Its roots are:

第四，叶轮和导流器的结构设计中未曾照顾变工况运行这一广泛存在的实际需要，普遍采用了一种损耗特性优化于设计流量的、对液流方向敏感的流道设计，例如叶轮叶片的入口角和出口角、导流器的导叶和反导叶的角度等。在实际变工况运行时，流量改变引起速度方向改变，方向改变产生撞击损耗，导致实际效率低于最优工况效率。 Fourth, the structural design of the impeller and the deflector did not take into account the widely existing practical needs of variable operating conditions. A flow channel design that is sensitive to the flow direction and has a loss characteristic optimized for the design flow is generally used. For example, The inlet and outlet angles of the impeller blades, the angles of the guide vanes and the counter guide vanes of the impeller, etc. During actual variable operating conditions, the change in flow rate causes a change in velocity direction, and a change in direction produces impact losses, resulting in actual efficiency being lower than the optimal operating efficiency.

外部阻性调节的采用，对设计工况的偏离，不但造成泵的内部损耗增加，还同时存在发生于外部的能量损失。用户实际上承受了分别发生于内部和外部的双重能量损失，外部损失不能在泵效率指标中表达，也没有单独的计量显示和统计。为了计算这种损失，应该考察机组效率和整个液流***的能量利用率，它们显然比泵效率更低。 The use of external resistive adjustment, which deviates from the design conditions, not only causes an increase in the internal loss of the pump, but also an external energy loss. The user actually bears the double energy loss that occurs internally and externally. The external loss cannot be expressed in the pump efficiency index, and there is no separate measurement display and statistics. In order to calculate this loss, the unit efficiency and the energy utilization rate of the entire flow system should be examined, which are obviously lower than the pump efficiency.

水泵是现代社会名列前茅的耗能设备，其低效运行造成了巨大的社会经济损失。仅在中国，水泵的年耗电量超过 4000亿度，其中属于可挖潜节约的部分按保守的估计也在 500 亿度以上。这加大了国民经济的运行成本，也加重了能源生产中的环境污染负荷。离心泵的效率问题是一个必须解决的重大技术经济问题，其紧迫性在世界范围内普遍存在。 Water pumps are among the top energy-consuming equipment in modern society, and their inefficient operation has caused huge socioeconomic losses. In China alone, the annual power consumption of water pumps exceeds 400 billion kWh, and the part that can be tapped to save potential is conservatively estimated to be more than 50 billion kWh. This has increased the operating costs of the national economy and also increased the environmental pollution load in energy production. The efficiency of centrifugal pumps is a major technical and economic issue that must be addressed, and its urgency is widespread throughout the world.

除了提高效率的紧迫需求以外，减小尺寸、简化结构和工艺、降低制造成本、增加功能价值等关乎性价比的各类问题，也都为泵行业人士和各界用户所普遍关心。发明内容 In addition to the urgent need to improve efficiency, reducing size, simplifying structure and technology, reducing manufacturing costs, increasing functional value and other issues related to cost performance are also generally concerned by the pump industry and users from all walks of life. Summary of the invention

本发明的任务在于克服离心泵的上述缺点，并进一步创造新的价值。 The task of the present invention is to overcome the above disadvantages of centrifugal pumps and to create new values further.

本发明的第一个具体目的是：优化叶轮输出的比能属性结构，设计出实现这种优化的新叶轮并改善其流场特性，使导流程和叶轮程的水力效率同时大幅度提高。 The first specific object of the present invention is to: optimize the specific energy attribute structure of the impeller output, design a new impeller to achieve such optimization and improve its flow field characteristics, so that the hydraulic efficiency of the guide flow and the impeller stroke is greatly improved at the same time.

本发明的第二个具体目的是：改变离心泵叶轮轮盘外侧的摩擦介质，降低其粘滞系数，从而大幅度降低轮鸯摩擦损耗和提高泵的内机械效率。 The second specific object of the present invention is to change the friction medium on the outside of the impeller wheel disc of a centrifugal pump and reduce its viscosity coefficient, thereby greatly reducing the friction loss of the wheel hub and improving the internal mechanical efficiency of the pump.

本发明的第三个具体目的是：改进导流器和其他组成部分的结构，使之与整体设计相匹配，以进一步降低导流损耗和提高全程水力效率，并从根本上减小导流器和机壳的比尺寸，使制造成本更低和使用更方便。 The third specific object of the present invention is to improve the structure of the deflector and other components to match the overall design, so as to further reduce the diversion loss and improve the overall hydraulic efficiency, and to reduce the deflector fundamentally. Compared with the case size, the manufacturing cost is lower and the use is more convenient.

本发明的第四个具体目的是：设计一种方法，在各类新型部件之间，在新型部件与传统技术部件之间，进行最有效的技术组合，以产生效率、成本或者使用功能方面的积极效果。由于本发明是以相关技术理论的改进和技术观念的创新为前提的，因而这方面的必要论证也附带在各发明目的之中。本发明实现第一个目的的技术路线是：设计一种新型的离心泵叶轮，该叶轮之输出具有较高的势扬程和较低的动扬程，以两者的比值——势动比作为衡量参数，使该比值较之现有技术有显著的提高。提高势动比体现了把叶轮改造为将轴功主要转化为压力势能的部件的目的性设计，因为在叶轮流道中依靠离心力与路径点积的线积分增压方程中没有相对速度因子，选择在相对低速的叶轮中尽可能多地生产势能可以降低流态损耗的比率。动扬程的进一步降低意味着叶轮输出的绝对速度必须在现有技术后弯式叶片降速方案极限值的基础上有进一步的降低，其好处是后续导流器的水力损耗随着流速的降低而迅速减少，动能比值的减少和动能损耗率的降低将导致泵效率线性提高。 The fourth specific object of the present invention is: to design a method to perform the most effective technical combination between various types of new components, and between new types of components and traditional technology components, so as to generate efficiency, cost, or use functions. Positive effect. Since the present invention is premised on the improvement of related technical theories and the innovation of technical concepts, the necessary arguments in this regard are also attached to the purpose of each invention. The technical route for achieving the first objective of the present invention is: design a new type of centrifugal pump impeller, the output of the impeller has a higher potential head and a lower dynamic head, and the ratio of the two is measured as the potential-dynamic ratio. Parameters, so that the ratio is significantly improved compared to the prior art. Increasing the potential-to-motivation ratio reflects the purposeful design of transforming the impeller into a component that mainly converts the shaft work into pressure potential energy, because there is no relative speed factor in the line integral supercharging equation relying on the centrifugal force and the path dot product in the impeller flow path. Producing as much potential energy as possible in relatively low speed impellers can reduce the rate of flow loss. The further reduction of dynamic head means that the absolute speed of the impeller output must be further reduced based on the limit value of the prior art backward curved blade speed reduction scheme. The advantage is that the hydraulic loss of subsequent deflectors decreases with the decrease of flow velocity. Rapid reduction, reduction of kinetic energy ratio and reduction of kinetic energy loss rate will result in a linear increase in pump efficiency.

势动比与现有技术概念中的反作用度或反应系数具有单调增的对应函数关系，因此，提髙势动比就是提高反作用度或者反应系数。本发明定义和使用势动比概念，是因为它更容易理解，并能更明确、更具体地表达本发明的特点和价值所在。 There is a monotonically increasing correspondence function between the potential ratio and the reaction degree or reaction coefficient in the prior art concept. Therefore, raising the potential ratio is to increase the reaction degree or reaction coefficient. The concept of momentum ratio is defined and used in the present invention because it is easier to understand, and it can more clearly and specifically express the characteristics and value of the present invention.

如前所述，后弯式叶片存在降速极限。为突破该极限，必须对现有技术叶轮进行改造。这些改造将包括把大出'口改为小出口、将液流出口角进一步减小到等于或几乎等于 0等新设计，以产生方向有利、大小满足要求的出口速度。这些改造的目的性意义在于，对具有不同损耗率的两条势能生产途径作恰当的权重安排，以优化泵效率指标。本发明实现第一个发明目的的技术方案是：采用高势动比叶轮，该叶轮的叶槽流道尾部朝反切向弯曲并且截面积逐渐减小，流体在离心力做功的路径末端被加速和改变方向，最后以较大的相对速度和接近于 0的出口角流出叶轮，出口绝对速度相应减小，转向和加速过程产生的反作用力矩使转轴减功。本发明方案是在机械能守恒定律的基础上设计的。在旋转坐标系中的叶槽流程末端进行能量转换来改变输出势动比，是一种对势能生产环境选择有利和回避不利的策略应用，施加的动力学手段是抗性力，转换过程是低损耗的。 As mentioned earlier, there is a speed limit for backward curved blades. To overcome this limit, prior art impellers must be retrofitted. These modifications will include new designs such as changing the large outlets to small outlets and further reducing the liquid flow outlet angle to equal to or almost equal to zero to produce outlet speeds with favorable directions and sizes that meet requirements. The purpose of these transformations is to make proper weighting arrangements for two potential energy production paths with different loss rates to optimize pump efficiency indicators. The technical solution for achieving the first object of the present invention is: adopting a high-potential-dynamic-ratio impeller, the tail of the impeller channel of the impeller is curved in the tangential direction and the cross-sectional area is gradually reduced, and the fluid is accelerated and changed at the end of the path of work performed by centrifugal force Direction, finally exiting the impeller with a relatively large relative speed and an exit angle close to 0, the absolute speed of the exit correspondingly decreases, and the reaction torque generated during the steering and acceleration processes reduces the work of the rotating shaft. The solution of the invention is designed on the basis of the law of conservation of mechanical energy. The energy conversion at the end of the leaf groove process in the rotating coordinate system to change the output potential-to-dynamic ratio is a strategic application that favors the potential energy production environment and avoids disadvantages. The applied dynamics is resistance, and the conversion process is low. Lossy.

本发明的原理演绎于描述叶轮比功的欧拉方程，是对该方程进行组项优化的结果。考察方程

a i O.S (u₂ ²— u ) +0.5 (wi²— w₂ ²) +0.5 (v₂ ²— V!²)，其中描述了叶轮对由静止坐标系中的牵连运动和旋转坐标系中的相对运动合成的液流运动赋能的数量关系。 0.5 (u₂ ²-Ui² ) 是离心力功转化为比势能的线积分值，在静止坐标系中的离心力场之绝对运动路径上完成。 0.5 (W!²-W₂ ²) +0.5 (v₂ ² -Vi²) 包含两个坐标系中的运动合成之比动能的全部相关项，隐含动能与势能互换机制，并遵守机械能守恒定律（不计摩擦损耗）。液流在叶轮流道中的比动能增量是 0.5 (v₂ ² -_Vl ²) ，直接来自叶片法向力功（等于比功扣除补充离心力功失能后之剩余部分），而其比势能增量则是 0.5 (u₂ ²-u_l ²+w_l ²-w₂ ²) ，分别来自离心力功和相对运动的比动能减量。 The principle of the present invention is deduced from the Euler equation describing the specific work of the impeller, which is the result of optimizing the system term of the equation. Examine the equation

ai OS (u ₂ ² — u) +0.5 (wi ² — w ₂ ² ) +0.5 (v ₂ ² — V! ² ), which describes the impeller pair's implicated motion in the stationary coordinate system and the rotational coordinate system. Quantitative relationship of relative motion synthesizing energetic flow. 0.5 (u ₂ ² -Ui ² ) is the line integral value of centrifugal force work converted to specific potential energy, which is completed on the absolute motion path of the centrifugal force field in the stationary coordinate system. 0.5 (W! ² -W ₂ ² ) +0.5 (v ₂ ² -Vi ² ) Contains all relevant terms of the specific kinetic energy of the motion synthesis in the two coordinate systems, implicit mechanism of kinetic energy and potential energy exchange, and observing the conservation of mechanical energy Law (excluding friction losses). The specific kinetic energy increase of the liquid flow in the impeller flow channel is 0.5 (v ₂ ² - _Vl ² ), which is directly derived from the normal force work of the blade (equal to the remaining work after deducting the supplemental centrifugal work power loss), and the specific potential energy increases. The quantity is 0.5 (u ₂ ^2- u _l ² + w _l ^2- w ₂ ² ), which are derived from the centrifugal force work and the specific kinetic energy reduction of the relative motion, respectively.

出于增大产能的目的，现有技术一直将相对运动比动能减量项 0.5 (_Wl ²-w₂ ²) 设定为正值，因为这样做能够导致比功和势扬程的同时增加。但是，传统观念对于由运动合成之出口速度三角形寄予了太多的希望。实际上，余弦定理公式 v₂ ²=u₂ ²+w₂ ²— 2u₂w₂cos β₂不可能给出所希望的结果，这是由于 w₂比 u₂小一个数量级，以致于 w₂ ²— 2u₂w₂cos β₂相对于 u₂ ²来说几乎等于 0，于是有 _V2 ² u₂ ²。放任很高的绝对速度 v₂进入导流流程，会产生巨大的损耗，以致形成制约泵效率的第一大瓶颈。解决这个问题的唯一出路在于将相对运动比动能减量项 0.5 (Wi²— w₂ ²)改为负值，即通过反向能量转换来增大 w₂，这时，上述余弦定理公式将给出较低的绝对速度 V₂，离心泵的效率瓶颈就能被突破。 For the purpose of increasing the production capacity, the prior art has always set the relative motion specific kinetic energy reduction term 0.5 ( _Wl ² -w ₂ ² ) to a positive value, because doing so can result in a simultaneous increase in specific work and potential lift. However, traditional ideas place too much hope on the exit velocity triangle synthesized by motion. In fact, the cosine theorem formula v ₂ ² = u ₂ ² + w ₂ ² — 2u ₂ w ₂ cos β ₂ cannot give the desired result. This is because w ₂ is an order of magnitude smaller than u ₂ , so w ₂ ² — 2u ₂ w ₂ cos β ₂ is almost equal to 0 with respect to u ₂ ² , so there is _V2 ² u ₂ ² . Allowing a very high absolute speed v _{2 to} enter the diversion process will cause huge losses, so that it will form the first major bottleneck that restricts pump efficiency. The only way to solve this problem is to change the relative motion ratio kinetic energy reduction term 0.5 (Wi ² — w ₂ ² ) to a negative value, that is, to increase w ₂ through reverse energy conversion. At this time, the above cosine theorem formula will give With a lower absolute speed V ₂ , the efficiency bottleneck of the centrifugal pump can be broken.

基于以上分析，本发明的主要设计特征——接近于 0的出口角、适当大的出口相对速度就有理由成立了。 Based on the above analysis, the main design feature of the present invention—an exit angle close to zero and a relatively large exit relative speed—are justified.

当出口角 β₂ 0时，出口相对速度 w₂与牵连速度 u₂反向，可以最大限度地抵消 u₂。设定 β₂ 0还有另一项重要作用， gp : 在减小出口面积而使出口相离分布的情况下，需要很小的出口角来组织液流出口后的速度场整理，以避免不利的速度分布造成湍流。 β₂ 0 意味着出口速度三角形缩小为直线段，绝对速度将由代数运算 v₂=u₂— w₂=(l— K)u₂给出。式中，系数 K=w₂/u₂称为反馈减速比。 K是重要的调控参数，其大小线性地反映了绝对速度减小的程度。之所以称为反馈减速比，是因为在旋转坐标系中生成反切向相对速度 w₂时，其反作用力矩使转轴减功，这是一个无损耗的动能反馈过程。动能反馈减速在旋转坐标系中表现为加速，所以叶轮结构中必须有加速流道。 When the exit angle β ₂ 0, the exit relative speed w _{2 is} opposite to the implication speed u ₂ , which can offset u _{2 to the} greatest extent. There is another important effect of setting β ₂ 0, gp: In the case of reducing the outlet area and separating the outlets, a small outlet angle is required to organize the velocity field after the liquid flow exit to avoid unfavorable Velocity distribution causes turbulence. β ₂ 0 means that the exit velocity triangle is reduced to a straight line segment, and the absolute velocity will be given by the algebraic operation v ₂ = u ₂ — w ₂ = (l— K) u ₂ . In the formula, the coefficient K = w ₂ / u _{2 is} called a feedback reduction ratio. K is an important control parameter, and its size linearly reflects the degree of absolute speed reduction. The reason why it is called the feedback reduction ratio is that when the inverse tangential relative speed w ₂ is generated in the rotating coordinate system, the reaction torque reduces the work of the rotating shaft, which is a lossless kinetic energy feedback process. The kinetic energy feedback deceleration appears as acceleration in the rotating coordinate system, so there must be an acceleration flow path in the impeller structure.

为了使绝对速度 v₂显著减小， w₂在数值上必须设置得比现有技术的极限值还要大许多，应该达到与 u₂同数量级的水平。减小出口面积和在叶槽流道末端设置逐渐减小截面积的加速段可以实现这一目标。当 K=0.5左右时， W₂=Ku₂ 0.5 R₂。相对速度 w₂的增加必然以消耗势能为代价，因此，叶轮的输出比势能增量将因为 w₂的增大而减小。由于比势能增量的减小量为 0.5 ω ^{2 2}Κ²，与真小数 Κ的平方成正比，因而数值较小。而比动能增量的减小量则等于 0.5u₂ ²—0.5 (U₂-KU₂) ²=0.5 ω ¾₂ ² (2Κ-Κ²) ，这比比势能的减小量大得多，两者的比值为（2— Κ) / Κ，因而叶轮的输出势动比将大幅度增加。计算表明，实用区间的 Κ值可以使输出势动比增加 2〜8倍。本发明方案对于提高泵效率具有显著的效果。髙势比叶轮输出液流绝对速度较小，导流负荷轻，速度幂次类损耗将大幅度减少，因而具有比现有技术高得多的导流效率。 In order to reduce the absolute speed v ₂ significantly, w ₂ must be set to be much larger than the limit value of the prior art in value, and should reach a level of the same order of magnitude as u ₂ . This can be achieved by reducing the exit area and setting an accelerating section that gradually reduces the cross-sectional area at the end of the blade channel. When K = 0.5, W ₂ = Ku ₂ 0.5 R ₂ . The increase in the relative speed w ₂ is necessarily at the expense of potential energy, so the output specific potential energy increase of the impeller will decrease as w ₂ increases. Thanks to The reduction of the potential energy increase is 0.5 ω ^{2 2} κ ² , which is proportional to the square of the true decimal κ, so the value is small. The reduction in specific kinetic energy increase is equal to 0.5u ₂ ² —0.5 (U ₂ -KU ₂ ) ² = 0.5 ω ¾ ₂ ² (2Κ-Κ ² ), which is much larger than the reduction in potential energy. The ratio of this is (2-K) / K, so the output momentum ratio of the impeller will increase significantly. Calculations show that the K value of the practical interval can increase the output momentum ratio by 2 to 8 times. The solution of the invention has a significant effect on improving the efficiency of the pump. The potential is smaller than the absolute speed of the impeller output liquid flow, the diversion load is light, and the speed power loss will be greatly reduced, so it has a much higher diversion efficiency than the existing technology.

离心泵的水力损耗大部分发生在导流器。现有技术离心泵的入导流速很髙，通常超过 20米 /秒，比水力规范高一个数量级，这必然产生大的损耗。在导流器中，高速边际摩擦、大梯度内摩擦难以避免；高速撞击、脱流、局部激励也经常发生。这些损耗对入导速度有着 2次幂或 3次因式锐相关的敏感性。导流损耗在中小型、低比转数以及偏离设计工况运行等情况下尤其严重，这时的动能损耗率可能超过 50%。本发明对挽救这些损失具有特别大的作用，下面区分局部阻力型和沿途阻力型两类导流损耗具体讨论这种作用的效果。 Most of the hydraulic loss of centrifugal pumps occurs in the deflector. The inlet flow rate of the prior art centrifugal pump is very high, usually more than 20 meters per second, which is an order of magnitude higher than the hydraulic specification, which inevitably results in large losses. In deflectors, high-speed marginal friction and large-gradient internal friction are difficult to avoid; high-speed impacts, deflows, and local excitation often occur. These losses are sensitive to the 2nd power or 3rd factor of the conduction velocity. Diversion loss is especially serious in small and medium-sized, low specific revolutions, and deviations from design conditions. At this time, the kinetic energy loss rate may exceed 50%. The present invention has a particularly significant effect on rescuing these losses. The following is a detailed discussion of the effect of this effect by distinguishing between two types of diversion losses, the local resistance type and the along-path resistance type.

对于局部阻力型导流损耗，例如撞击、局部激励、流速剧变等湍阻性流态，其损耗是集中于局部发生的。这类损耗与流速的平方成正比，与局部阻力系数成正比。为简化分析和直接对比，定义高势比液流与常势比液流（势比为 1 ) 的这类导流损耗之比为局部阻力型导流损耗比，该比值随前者的调控参数 Κ变动情况列于表 1第 3行。 ' 对于沿途阻力型导流损耗，例如导流器的典型增压流道损耗，其分析计算依赖于路径积分，参与运算的参数很多。现确定对比前提为：高势比和常势比入导液流比能相同，流量相同，截面积扩张率相同，摩擦系数相同，入导速度之比已知，几何结构类似，等等。为简化分析，还假设导流出口速度相同，并且对结果的影响可以忽略。根据这些前提，用流体力学相关理论可以推出：高势比与常势比导流的沿途对比段之比损耗比（单位长度上的比能损耗之比）与速度比的平方成正比，其数据列于表 1第 4行；由两者导流负荷比决定的导流流程长度比与入导速度比成正比，其数据列于表 1第 5行。再用与处理局部损耗类似的方法定义两者之沿途阻力型导流损耗比，忽略出口速度引起的高阶小量，积分可得该损耗比与两者入导速度比的 3次方成正比，其数据列于表 1第 6行。 For local resistance-type diversion losses, such as turbulent flow regimes such as impacts, local excitations, and sudden changes in velocity, the losses are concentrated locally. This type of loss is proportional to the square of the flow velocity and proportional to the local drag coefficient. In order to simplify the analysis and direct comparison, the ratio of this type of conduction loss of high potential ratio liquid flow to constant potential ratio liquid flow (potential ratio is 1) is defined as the local resistance type conduction loss ratio, and this ratio depends on the former control parameter κ The changes are listed in the third row of Table 1. '' For resistance-type diversion losses along the way, such as the typical booster flow path losses of a deflector, its analysis and calculation rely on path integrals, and there are many parameters involved in the calculation. The premise of the comparison is as follows: the high potential ratio and the constant potential ratio have the same specific energy in the inflow, the same flow rate, the same cross-sectional area expansion rate, the same friction coefficient, the inflow velocity ratio is known, the geometry is similar, and so on. To simplify the analysis, it is also assumed that the speed of the diversion outlet is the same, and the effect on the result can be ignored. Based on these prerequisites, theories related to fluid mechanics can be used to derive: The ratio loss ratio (ratio of specific energy loss per unit length) of the high-potential ratio and the constant-potential ratio diversion section along the way is directly proportional to the square of the velocity ratio. It is listed in the fourth row of Table 1. The length ratio of the diversion flow determined by the diversion load ratio of the two is proportional to the ratio of the inflow speed. The data is listed in the fifth row of Table 1. Then use a similar method to process the local loss to define the two-way resistance type guide loss ratio along the way. Ignoring the high-order small amount caused by the exit speed, the integral can be obtained that the loss ratio is proportional to the third power of the two guide speed ratios. The data are listed in the sixth row of Table 1.

表 1 髙势比液流与常势比液流之导流损耗与前者速度测度 Κ关系表高势比测度（反馈减速比 Κ) 0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 高势比液流势动比 λ典型值 1.00 1.25 1.60 2.12 3.02 5.07 17.2 局部阻力型导流损耗比 1.00 0.81 0.64 0.49 0.36 0.25 0.16 0.09 比损耗比 1.00 0.81 0.64 0.49 0.36 0.25 0.16 0.09 沿途阻力型导流流程长度比 1.00 0.90 0.80 0.70 0.60 0.50 0.40 0.30 导流损耗比 1.00 0.729 0.512 0.343 0.216 0.125 0.064 0.027 参照表 1，其中第 1 '行是自变量，为高势比叶轮的控制参数——反馈减速比 κ，是各损耗参数比式分子的速度测度。第 2行是高势比液流势动比的典型值，为比式分子的比能属性测度。其余因变 3、 4、 5、 6行数据是比对参数的比值，分别表示两种液流的局部阻力型导流损耗比、沿途阻力型导流比损耗比、导流流程长度比、沿途阻力型导流损耗比。 Table 1 Relation between the flow loss of the pseudo-potential ratio liquid flow and the constant-potential ratio liquid flow and the former velocity measure κ High potential ratio measure (feedback reduction ratio κ) 0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 λ typical value 1.00 1.25 1.60 2.12 3.02 5.07 17.2 Local resistance type guide loss ratio 1.00 0.81 0.64 0.49 0.36 0.25 0.16 0.09 Specific loss ratio 1.00 0.81 0.64 0.49 0.36 0.25 0.16 0.09 Resistance ratio guide flow length ratio 1.00 0.90 0.80 0.70 0.60 0.50 0.40 0.30 Diversion loss ratio 1.00 0.729 0.512 0.343 0.216 0.125 0.064 0.027 Refer to Table 1, where the first row is the independent variable, which is the control parameter of the high-potential-ratio impeller—the feedback reduction ratio κ, which is the speed measurement of each loss parameter ratio numerator. The second line is the typical value of the high potential specific liquid flow potential dynamic ratio, which is the measure of the specific energy property of the ratio molecule. The remaining variable 3, 4, 5, and 6 rows of data are the ratios of the comparison parameters, which respectively represent the local resistance type diversion loss ratio of two liquid flows, the resistance type diversion ratio loss ratio along the way, the diversion flow length ratio, and Resistance type diversion loss ratio.

第 1列数据全为 1，因为两者都是常势比液流，参数相同。其余各列全是真小数，表示高势比液流具有较低的导流损耗指标，这些比值均随着高势比液流速度测度 κ的增大而减小。第 3行和第 6行直接给出了局部阻力型导流损耗与沿途阻力型导流损耗的比值，该两比值都是与 Κ锐相关地减小的。 The data in the first column are all 1, because both are constant potential specific flow and the parameters are the same. The remaining columns are all true decimals, indicating that the high potential specific flow has lower conductivity loss indexes. These ratios decrease as the high potential specific flow velocity measure κ increases. Lines 3 and 6 directly give the ratio of the local resistance-type diversion loss to the along-path resistance-type diversion loss, both of which are reduced in sharp correlation with κ.

第 6行数据显示，在 Κ的取值范围内，高势比液流的导流损耗较常势比液流下降一个数量级。其实际意义是：对于居主模式地位的沿途阻力型导流，高势比液流的损耗比常势比液流小一个数量级。实际上，由于常势比导流技术中还经常包含一些局部阻力型损耗混杂于其中，特别是变流量运行引起的变角度撞击类 2次型损耗普遍和经常性地存在，使得比式的实际分母更大，髙势比导流特性中无此类因素，且有完备约束的低损耗导流技术配套，因而实际的比值还将小于甚至远小于表 1中的数据，这且留待后续文字说明。结论是：高势比叶轮输出的高势比液流，具有成数量级地降低导流损耗的特性。可以举例说明本发明的积极效果。例如，设某现有技术离心泵的势动比为 1，其局部阻力型导流的动能损耗率为 50%，换算成比能损耗率则为 25%，在所有其他损耗均为 0 的理想状态下，该泵的效率将只有 75 %。改用本发明的高势比叶轮，设其流量和比能等对比参数相同，但势动比提高 3倍，即由 1增加到 4，则导流器的归一化导流负荷比为 1/( 1+4) =20% , 减少为对比泵相应负荷比 1/ ( 1+1 ) =50%的 40%，其入导速度减少为对比泵相应速度的（0.2/0.5 ) ⁵=63.25%，其动能损耗量以及与之成正比的比能损耗率均按速度平方律减少为对比泵的 40%，但两者的动能及比动能的损耗率却是相等的。在同样的假设条件下，其比能损耗率减少为 25 % Χ 40% = 10%，其效率将提高到 90%。 The data in line 6 shows that, within the value range of K, the drainage loss of high potential ratio liquid flow is one order of magnitude lower than that of normal potential liquid flow. Its practical significance is: For the resistance-type diversion along the way in the dominant mode, the loss of the high potential ratio liquid flow is an order of magnitude smaller than the normal potential liquid flow. In fact, because the constant potential ratio diversion technology often contains some local resistance type losses mixed in, especially the variable angle impact secondary type losses caused by variable flow operation exist universally and often, making the ratio formula practical The denominator is larger, there is no such factor in the pseudo-potential than the diversion characteristics, and there is a complete set of low-loss diversion technology supporting, so the actual ratio will be smaller or even much smaller than the data in Table 1, and this is left to the following text . The conclusion is that the high potential ratio liquid flow output by the high potential ratio impeller has the characteristic of reducing the conduction loss by orders of magnitude. The positive effects of the invention can be exemplified. For example, suppose that the potential-to-kind ratio of a prior art centrifugal pump is 1, and the kinetic energy loss rate of its local resistance type diversion is 50%, and the specific energy loss rate is 25% when converted. Ideally, all other losses are 0. In this state, the efficiency of the pump will be only 75%. If the high potential ratio impeller of the present invention is used instead, it is assumed that the comparison parameters such as the flow rate and the specific energy are the same, but the potential ratio is increased by 3 times, that is, from 1 to 4, the normalized guide load ratio of the deflector is 1 / (1 + 4) = 20%, reduced to 40% of the corresponding load ratio of the comparison pump 1 / (1 + 1) = 50%, and its conduction speed reduced to (0.2 / 0.5) ⁵ = 63.25 of the corresponding speed of the comparison pump %, The amount of kinetic energy loss and the specific energy loss rate proportional to it are both reduced to 40% of the contrast pump according to the speed square law, but the kinetic energy and specific energy loss rates of the two are equal. Under the same assumptions, the specific energy loss rate is reduced to 25% x 40% = 10%, and its efficiency will be increased to 90%.

上述举例分析采用的是***损耗分析方法。不失一般性，去掉 "所有其他损耗均为 0" 的假设，引进导流***效率概念就能方便地单独分析导流损耗的规律。导流***效率即导流水力效率，定义为导流程的输出比能与输入比能之比，在效率方程中，它是全程水力效率和总效率的非线性因子，忽略高阶小量可视为线性因子。在这种分析方法中，将势动比选作变动参数较为方便，因为比动能的损失量与流速的平方成正比，也即与比动能成正比。注意到例中动能及比动能的损耗率不随势动比改变的规律，据以引进比例常数，将损耗动能对比能归一化处理，得高势比液流局部阻力型导流的效率公式如（1 ) 式。 The above example analysis uses the insertion loss analysis method. Without loss of generality, removing the assumption that "all other losses are 0", the introduction of the concept of diversion insertion efficiency can easily analyze the law of diversion losses separately. Diversion insertion efficiency is the diversion hydraulic efficiency, which is defined as the ratio of the specific energy of the output of the diversion process to the specific energy of the input. In the efficiency equation, it is a non-linear factor of the overall hydraulic efficiency and the total efficiency. Is a linear factor. In this analysis method, it is more convenient to select the potential kinetic ratio as the variation parameter, because the loss of specific kinetic energy is proportional to the square of the velocity, that is, proportional to the specific kinetic energy. Note that in the example, the loss rate of kinetic energy and specific kinetic energy does not change with the potential kinetic ratio. Based on the introduction of a proportionality constant, the loss kinetic energy contrast energy is normalized. The efficiency formula for local resistance type flow guidance of high potential ratio liquid flow is as follows: (1) Formula.

n_hini = i - ξ ι/ ( ΐ+ λ ) ( 1 ) 式中 ^为设计流量下局部阻力型导流的比动能损耗系数。 S i/ d+ A )是比能损耗率，与比动能成正比，因而与（ι+ λ )成反比。如前所述，现有技术离心泵的势动比基本上为 1，因而其效率为 ΐΗω-Ι— ξ ί ^, 改用髙势比叶轮以后，其效率按（1) 式规律提高，其增效性能如表 2。表 2 高势比与常势比液流局部阻力型导流效率比较表 n _h ini = i-ξ ι / (ΐ + λ) (1) where ^ is the specific kinetic energy loss coefficient of the local resistance type guide at the design flow. S i / d + A) is the specific energy loss rate, which is directly proportional to the specific kinetic energy, and therefore inversely proportional to (ι + λ). As mentioned before, the potential ratio of the prior art centrifugal pump is basically 1, Therefore, its efficiency is ΐΗω-Ι— ξ ί ^. After switching to the potential ratio impeller, its efficiency is improved according to the formula (1). Table 2 Comparison of local resistance type diversion efficiency of liquid flow with high potential ratio and constant potential ratio

从表 2中可以看出，即使是比较差的导流器，例如比动能损耗系数 t OJ的导流器，当势动比 λ =3〜9 时，其局部阻力型导流效率将由现有技术的 75%提高到 87.5%〜95.0 %。可见，提高势动比可以大幅度提高局部阻力型导流效率。更接近实际的是沿途阻力型导流损耗。仍釆用上例中的数据和条件对这类损耗进行分析对比，例中高势比与常势比的导流负荷比为 40%、入导速度比为 63.25%两个推算比值不变，增设导流器几何相似、截面积扩张率和摩擦系数均相同等条件，则高势比液流的导流流程长度将减少为对比泵的 63.25%，其沿途单位长度上的动能损耗量按速度平方律均减少为对比泵的 40%，其沿途动能损耗量将减少为对比泵的 0.6325³ = 25.3%，显然，两者的比动能损耗率已经不再相等，该指标是与入导速度成正比的。则在同样的假设条件下，其比能损耗率将减少为 25%Χ25.3%=6.3%，其效率将提高到 93.7%。 It can be seen from Table 2 that even for a relatively poor deflector, such as a deflector with a specific kinetic energy loss coefficient t OJ, when the potential-to-kind ratio λ = 3 to 9, the local resistance-type diversion efficiency will be changed from the existing 75% of the technology increased to 87.5% ~ 95.0%. It can be seen that increasing the potential-to-dynamic ratio can greatly improve the efficiency of local resistance type diversion. Closer to reality is the resistance-type diversion loss along the way. Still use the data and conditions in the above example to analyze and compare this type of loss. In the example, the diversion load ratio of the high potential ratio to the normal potential ratio is 40%, and the inlet velocity ratio is 63.25%. The two estimated ratios are unchanged. The conditions of the deflectors are similar, the cross-sectional area expansion rate and the friction coefficient are the same. Then, the length of the diversion flow of the high potential ratio liquid flow will be reduced to 63.25% of the contrast pump, and the kinetic energy loss per unit length along the way is squared according to the speed. The law is reduced to 40% of the comparison pump, and the amount of kinetic energy loss along the way will be reduced to 0.6325 ³ = 25.3% of the comparison pump. Obviously, the specific kinetic energy loss rates of the two are no longer equal, and this index is directly proportional to the conduction speed. of. Under the same assumptions, the specific energy loss rate will be reduced to 25% × 25.3% = 6.3%, and its efficiency will be increased to 93.7%.

对于沿途阻力型导流损耗，注意到比动能损耗率与入导速度成正比的特点，因而只有该速度的最大值即无势能液流的比动能损耗率才可能作为不变的共用常数，引进该常数，并将损耗对比能作归一化处理，得高势比和常势比液流的导流效率公式如（2) 式。

Regarding the resistance type conduction loss along the way, note that the specific kinetic energy loss rate is proportional to the inductive velocity, so only the maximum value of the velocity, that is, the specific kinetic energy loss rate of the potentialless fluid flow, can be introduced as a constant common constant. This constant, and the normalization of the loss contrast can be used to obtain the formula for the efficiency of flow guidance of liquids with high potential ratio and constant potential ratio, such as (2).

式中 ξ 2为具有相同流量和相同比能的无势能液流（ λ =0)在结构相似、扩张率相同、摩擦系数相同、出口速度相同等设定条件下之沿途阻力型导流的动能损耗率，是此类导流器的结构及工艺的质量水平的测度。当 λ改变时，匹配导流器的比损耗系数和流程长度都不相同，比动能损耗率也不相同，但其比能损耗率都受同一常数 ξ 2的客观制约而具有可比性。式中， ξζΛΙ+ λ )¹·⁵是导流器的比能损耗率，与流速的 3次方成正比，因而与 (1+λ ) "成反比。现有技术离心泵的势动比为 1，其导流效率为 n _hi_n2= l— ξ₂/2^{1 5}= 1 -0.3536 ξ_{2 ο} 改用高势比叶轮以后，导流效率按（2) 式规律提髙，其增效性能如表 3。高势比和常势比液流沿途阻力型导流效率比较表 Where ξ 2 is the kinetic energy of the resistance-type flow guidance along the set flow conditions with the same flow rate and the same specific energy of the potential-free flow (λ = 0) under the conditions of similar structure, same expansion rate, same friction coefficient, and same exit speed The loss rate is a measure of the quality of the structure and process of such deflectors. When λ is changed, the specific loss coefficient and flow length of the matching deflector are not the same, and the specific kinetic energy loss rate is also different. However, the specific energy loss rate is subject to the objective constraint of the same constant ξ 2 and has the potential Than sex. In the formula, ξζΛΙ + λ) ¹ · ⁵ is the specific energy loss rate of the deflector, which is proportional to the third power of the flow velocity, and thus inversely proportional to (1 + λ). 1, which flow efficiency _{_{_{n h i n2 = l- ξ 2}}} /2 1 5 = 1 -0.3536 ξ 2 ο higher potential than the wheel after use, flow efficiency press (2) mentioned law Gao, QTLs The performance is shown in Table 3. Comparison table of resistance-type diversion efficiency of liquid flow along the high potential ratio and constant potential ratio

参照表 3，其中高势比各行效率数据的增幅明显高于表 2。即使是比较差或很差的配套导流器，例如比照损耗系数 ξ₂=0.7071〜0.9899的导流器，其常势比导流的导流效率只有 75 %〜65 %， ·当势动比人 4时，高势比导流效率都在 91 %以上。当 ξ₂==0.7071时，常势比导流效率为 75 % , 高势比导流效率却高达 93.7% ~97.8 %。可见，对于沿途阻力型导流器，提高势动比可以更显著地提高导流效率，并具有一个数量级的优势。所谓一个数量级的优势是指由 1— aX lO-ⁿ提高到 1一 aX lO- ^η- 其中 a为带小数， n为正整数。 Referring to Table 3, the increase of the efficiency data of the high potential ratio is significantly higher than that of Table 2. Even if it is a relatively poor or poor supporting deflector, such as a deflector with a comparison of the loss coefficient ξ ₂ = 0.7071 ~ 0.9899, its normal potential is only 75% ~ 65% than the diversion efficiency of the diversion. At 4 hours, the diversion efficiency of high potential ratio is more than 91%. When ξ ₂ == 0.7071, the constant potential specific diversion efficiency is 75%, while the high potential specific diversion efficiency is as high as 93.7% ~ 97.8%. It can be seen that, for the resistance type deflector along the way, increasing the potential-to-dynamic ratio can significantly improve the diversion efficiency, and has an order of magnitude advantage. The so-called advantage of an order of magnitude refers to an increase from 1—aX lO- ⁿ to 1—aX lO- ^η —where a is a decimal number and n is a positive integer.

沿途阻力型导流损耗是离心泵导流器的正则损耗模式，但局部阻力型损耗也是现有技术框架下难以避免的，尤其是实际液流***中的节流调节，会导致变工况运行和局部损耗产生。因此，本发明对导流效率的讨论不得不赘言分叙，因为它们的力学模型有差别，结果也大不相同。要想得到符合实际的比较数据，应该按照现有技术导流器中两种损耗模式的统计数据求得基于统计总体的权重系数，用以对两种导流损耗及效率数据作加权处理，其结果将更合乎现有技术的实际。 Resistance-type diversion loss along the way is a regular loss mode of centrifugal pump deflectors, but local resistance-type loss is also unavoidable under the prior art framework, especially the throttling adjustment in the actual fluid flow system, which will lead to variable operating conditions. And local losses occur. Therefore, the discussion of the diversion efficiency of the present invention has to be elaborated, because their mechanical models are different, and the results are also very different. In order to obtain actual comparison data, the weight coefficient based on the statistical population should be obtained according to the statistical data of the two loss modes in the prior art deflector, which is used to weight the two diversion loss and efficiency data. The results Will be more in line with the actuality of the existing technology.

本发明的目标和结果体现于表 3。沿途阻力型是公认的导流损耗的目标模式，后续说明所公开的导流器可以保障这种模式的实现，并且变工况运行不改变模式。 The objectives and results of the present invention are shown in Table 3. The resistance type along the way is the recognized target mode of diversion loss. The follow-up description of the disclosed deflector can guarantee the realization of this mode, and it does not change the mode under variable operating conditions.

髙势比叶轮还可以有很高的叶轮程水力效率，因而其全程水力效率将达到非常高的指标。水力效率的大幅度提髙意味着制约离心泵效率的第一大瓶颈被突破。除了提高导流效率，本发明方案还可以使离心泵的制造成本有较大幅度的降低。其理由如下：采用高势比叶轮降低液流速度以后，随着动能转换负荷的减轻和工作速度的减小，导流器的流程可以大幅度缩短，结构可以相应简化，其体积可以大大缩小，降低泵的制造成本就成为可能了。在现有技术中，导流器工作于液流髙速流动这一超水力规范条件，入口线速度从每秒十几米到每秒几十米不等，超过水力规范一个数量级。尽管其动能转换效率不可能做得高，但人们还是有理由尽可能地从中挖掘每一个百分点的效率潜力。但在现有技术框架下，提高导流效率所付出的空间代价太大，而潜力却有限。我们看到，布设于叶轮外环空间的导环、导轮、蜗道等导流器，由于其体积与直径尺度成 2次函数关系，它们的体积因而比叶轮还大，低比转数泵的导流器体积比例更大。它们占据了离心泵的大部分体积，耗用了很多的金属材料和加工工时，致使泵的制造成本增加很多。本发明方案使导流器的动能转换负荷减少为若干分之一，工作速度降低一半左右，因而导流器的尺寸和体积可以大幅度减小，精度和表面质量要求也可以适当放宽，导流器占据大部分体积的情况将大为改观，离心泵的制造成本也可望因此而降低许多。本发明方案也产生了一个缺点，那就是，叶轮的理论比功和理论扬程将随着反馈减速比 K的增加而减少， ¾是由于叶轮的输出比势能和输出比动能同时减少所致，这意味着同样直径和同样转速的叶轮的出力将有所减少。选定参数 K以后，要达到同样的理论扬程，必须加大叶轮直径或者增加转速来补偿这种理论比功和理论扬程的损失，显然，这又将增加叶轮线速度和液流绝对速度，并将高幂次地增大轮盘摩擦损耗。 The pseudopotential can also have a higher hydraulic efficiency of the impeller stroke than the impeller, so its overall hydraulic efficiency will reach a very high index. The large increase in hydraulic efficiency means that the first major bottleneck that restricts the efficiency of centrifugal pumps has been broken. In addition to improving the diversion efficiency, the solution of the invention can also greatly reduce the manufacturing cost of the centrifugal pump. The reason is as follows: After using the high potential ratio impeller to reduce the liquid flow speed, as the kinetic energy conversion load is reduced and the working speed is reduced, The flow of the deflector can be greatly shortened, the structure can be simplified correspondingly, its volume can be greatly reduced, and it is possible to reduce the manufacturing cost of the pump. In the prior art, the deflector works under the super-hydraulic specification condition that the liquid flow flows at a rapid speed, and the inlet linear velocity ranges from a dozen meters per second to tens of meters per second, which is an order of magnitude greater than the hydraulic specification. Although it is impossible to achieve high kinetic energy conversion efficiency, there is still reason to dig out every percentage of efficiency potential from it as much as possible. However, under the existing technology framework, the space cost of improving the diversion efficiency is too great, and the potential is limited. We see that the guide rings, guide wheels, worms and other deflectors arranged in the outer ring space of the impeller have a larger volume than the impeller due to their volume and diameter function, and their volume is larger than that of the impeller. The deflector has a larger volume ratio. They occupy most of the volume of the centrifugal pump, consume a lot of metal materials and processing hours, resulting in a large increase in the manufacturing cost of the pump. The solution of the present invention reduces the kinetic energy conversion load of the deflector to a fraction, and reduces the working speed by about half. Therefore, the size and volume of the deflector can be greatly reduced, and the accuracy and surface quality requirements can be appropriately relaxed. The situation that the device occupies most of the volume will be greatly improved, and the manufacturing cost of the centrifugal pump is expected to be greatly reduced as a result. The solution of the present invention also has a disadvantage, that is, the theoretical specific work and theoretical head of the impeller will decrease as the feedback reduction ratio K increases. This is due to the fact that the output specific potential energy and output specific kinetic energy of the impeller are reduced at the same time. It means that the output of the impeller with the same diameter and the same speed will be reduced. After the parameter K is selected, to achieve the same theoretical head, the diameter of the impeller or the speed must be increased to compensate for the loss of theoretical specific work and theoretical head. Obviously, this will increase the impeller linear velocity and the absolute velocity of the liquid flow, and The friction loss of the disk will be increased at a high power.

这种缺点初看起来令人耽心，但深入分析表明，缺点所造成的损失只有增大轮盘摩擦一项，并且本发明的后述措施可以解决这一问题。其他似乎不利的特性实际上可以排除，甚至反而能由这种缺点引出令人鼓舞的新结论。其理由是：第一，理论比功和理论扬程与牵连速度成平方关系，而绝对速度与 K是线性关系，因而理论上需要补偿的直径增量或直径与转速（转速不便连续增加）乘积的增量较小，所需牵连速度增量远小于因 K造成的绝对速度的减少量。第二，由于效率的大幅度提髙，对理论比功和理论扬程的需求大幅度降低了，以致于实际上不需要补偿。从下文将要讨论的压力系数分析也可以看到，本发明方案在推荐的 K值范围内，其理论压力系数和变动不大的实际压力系数与现有技术常用的设计压力系数基本相当， .大致等于 1 , 因而基本不需要补偿或者补偿量很小，这是考虑效率因素以后的实际效果。'该结论可以这样理解：本发明理论比功和理论扬程的降低实际上是减少了现有技术设计上预留的那部分因效率低而必须考虑的损失能量，主要是导流水力损失，也包括部分叶轮流程的水力损失。第三，理论比功和理论扬程的减少并且是可参数控制的减少正是本发明改变离心泵参数刚性的基点，正是从这个基点出发，才产生了可调节性和可自控性设计的广阔空间。 This disadvantage may seem disturbing at first, but in-depth analysis shows that the loss caused by the disadvantage can only increase the friction of the disc, and the measures described below can solve this problem. Other seemingly unfavorable characteristics can actually be ruled out, and even such shortcomings can lead to encouraging new conclusions. The reasons are as follows: First, the theoretical specific work and theoretical head have a square relationship with the involved speed, and the absolute speed is linearly related to K. Therefore, the theoretical increase in diameter or the product of diameter and rotational speed (inconvenient continuous increase in rotational speed) The increment is small, and the required speed increase is much smaller than the absolute speed reduction caused by K. Second, due to the large increase in efficiency, the demand for theoretical specific work and theoretical lift has been greatly reduced, so that no compensation is actually required. It can also be seen from the pressure coefficient analysis to be discussed below that the theoretical pressure coefficient and the actual pressure coefficient with little change within the recommended K value range of the scheme of the present invention are basically equivalent to the design pressure coefficient commonly used in the prior art. It is equal to 1, so there is basically no need for compensation or the amount of compensation is small, which is the actual effect after considering the efficiency factor. 'The conclusion can be understood as follows: The reduction of the theoretical specific work and theoretical head of the present invention actually reduces the part of the energy that must be considered due to the low efficiency reserved in the prior art design, mainly the diversion hydraulic loss. Includes hydraulic loss of partial impeller flow. Third, the reduction in theoretical specific work and theoretical lift and the reduction in parameter control is the basis point of the invention for changing the rigidity of the centrifugal pump parameters. It is from this base point that a wide range of adjustable and self-controllable designs has been created space.

结论是，本发明方案的缺点的不利影响可以克服，并且能够转化为优点。本发明之高势比叶轮方案包含下列具体设计，它们可以使目标性能更突出，工作更稳定，其设计步骤也更明确具体： The conclusion is that the disadvantages and disadvantages of the solution of the present invention can be overcome and can be turned into advantages. The high potential ratio impeller scheme of the present invention includes the following specific designs, which can make target performance more prominent and work more stable The design steps are also more specific:

a、流道出口为矩形、或内圆倒角矩形、或圆形，周长尽量小，其前邻加速段有连续过渡的相应截面。采用内圆倒角矩形或圆形截面时，盖板上或有相应补结构。相邻出口之间的角距离等于 360度除以流道数，出口法面与流道垂直。前一出口内侧边到后一出口外侧边之间的连接为光滑的渐开弧线柱面，圆形或内圆倒角出口以由深到浅的槽道吻接。柱面或槽面与圆周柱面之间的流道截面积与圆心角成周期性线性关系。相离分布的出口流束经弧线柱面或槽面的附壁效应整理，在轮沿出口间隔区形成向内弯曲的均布流线，流速的径向分量与切向分量不随圆心角改变，在圆周柱面上，压力、流速及其径向和切向分量处处相等。 a. The outlet of the runner is rectangular, or inner chamfered rectangle, or circular, the perimeter is as small as possible, and its adjacent acceleration section has a corresponding cross section for continuous transition. When using internal chamfered rectangle or circular cross section, the cover may have corresponding supplementary structure. The angular distance between adjacent outlets is equal to 360 degrees divided by the number of channels. The normal surface of the outlets is perpendicular to the channels. The connection from the inside edge of the previous exit to the outside edge of the next exit is a smooth involute arc cylinder, and the round or inner chamfered exits are connected by deep to shallow channels. The cross-sectional area of the channel between the cylindrical surface or the groove surface and the circumferential cylindrical surface has a periodic linear relationship with the center angle. The separated exit stream bundles are sorted by the Coanda effect of the arc cylinder or the groove surface, forming an inwardly curved uniform flow line in the exit interval of the wheel. The radial and tangential components of the velocity do not change with the center angle. On a circular cylinder, the pressure, velocity, and their radial and tangential components are equal everywhere.

b、各流道出口面积之和等于设计体积流量与设计出口相对速度之比，该速度等于叶轮圆周速度与反馈减速比 κ的乘积。 b. The sum of the outlet area of each flow channel is equal to the ratio of the design volume flow rate to the design outlet relative speed, which is equal to the product of the impeller peripheral speed and the feedback reduction ratio κ.

具体方案中的技术要素 a公开了高势比叶轮的一种流道出口形状和轮沿结构及其出口速度场整理机制。较之传统叶轮，这种设计及其机制增加了出口液流的被约束度和稳定度，其摩擦面积也较小。出口角度设计使出口相对速度与牵连速度反向，旨在抵消该速度。出口法面与流道垂直意味着流线光滑和液流稳定，意味着出口角很小。出口角正弦值决定出口相对速度的轴面分量，. 并等于该分量除以出口相对速度。由于出口间隔区连接面的特定造形，其附壁效应使出口区流场的轴面速度分量在整个轮周都是均匀分布的，因而轴面速度分量又正好等于流量除以叶轮出口外圆柱面的面积。其轴面速度小，出口角正弦也小，出口法面与轴面的夹角也很小，几乎就在轴面上。出口角的余弦则几乎等于 1，因而对牵连速度有最大限度的抵消作用。这种设计的目的除了输出高势比液流以外，主要考虑还在于稳定出口区流场。稳定目标包括使液流在出口时既不对前方区域产生局部激励，又不发生轮沿脱流；也包括对附壁效应的利用，使之产生单边轮沿约束；还包括使出口速度的径向分量和切向分量具有最好的方向连续性和分布均匀性。 Technical element a in the specific scheme a discloses a flow channel exit shape and wheel edge structure of a high-potential-ratio impeller and its exit velocity field arrangement mechanism. Compared with the traditional impeller, this design and its mechanism increase the degree of restraint and stability of the outlet liquid flow, and its friction area is also small. The exit angle design reverses the exit relative speed to the implication speed and is designed to counteract that speed. The normal surface of the outlet and the flow channel mean that the flow line is smooth and the liquid flow is stable, which means that the outlet angle is small. The sine of the exit angle determines the axial component of the relative velocity of the exit, and is equal to this component divided by the relative velocity of the exit. Due to the specific shape of the connection surface of the exit interval, the Coanda effect makes the axial surface velocity component of the flow field in the exit area uniformly distributed throughout the wheel circumference, so the axial surface velocity component is exactly equal to the flow divided by the cylindrical surface of the impeller exit Area. Its axial plane speed is small, and the exit angle sine is also small. The angle between the exit normal plane and the axial plane is also very small, almost on the axial plane. The cosine of the exit angle is almost equal to 1, so it has the greatest offsetting effect on the speed of implication. The purpose of this design is to stabilize the flow field in the exit zone in addition to outputting high potential ratio liquid flow. Stability goals include making the liquid flow neither locally stimulate the front area nor rim outflow at the exit; it also uses the Coanda effect to make it a unilateral rim constraint; it also includes the diameter of the exit speed. The directional and tangential components have the best directional continuity and distribution uniformity.

相邻出口之间用光滑的渐开弧线柱面或带槽柱面连接是一项重要特征，其目的在于使出口流束得到轮廓线柱面或槽面的附壁效应的均勾吸附而连续向内弯曲，以免因动量惯性而在较长的出口间隔区域发生脱流或局部激励。附壁效应的生成机制是：在邻域充分约束的条件下和一定的动量惯性幅度内，流束的外侧区域与内侧壁面绝对压力之差能够提供法向作用力使液流产生随壁面连续转向的加速度，其中壁面的绝对压力是随外侧压力自适应变化的，当壁面小邻域内的绝对压力自适应减小到等于或接近于饱和气压时，附壁效应不稳定而发生脱流。本发明利用附壁效应的条件是：出口流束外侧具有由比势能幅度保障的充分大的静压力；液流出口相对速度是受最小势动比制约的，其动量惯性是有限的；轮廓线柱面是数学光滑的，具有曲率的连续性并且曲率半径较大，所需附壁向心加速度恒小于比势能所限定的幅度。因此，附壁效应稳定，不会有脱流发生。 The connection between adjacent exits by smooth involute arc cylinders or grooved cylinders is an important feature, the purpose of which is to make the exit stream beams to be absorbed by the Coanda effect of contour cylinders or grooves Continuously inwardly bent to prevent outflow or local excitation in the longer exit interval area due to momentum inertia. The formation mechanism of the Coanda effect is: Under the condition that the neighborhood is fully constrained and within a certain range of momentum inertia, the difference between the absolute pressure of the outer area of the flow beam and the inner wall surface can provide a normal force to cause the liquid flow to continuously turn with the wall surface. The absolute pressure of the wall is adaptively changed with the external pressure. When the absolute pressure in the small neighborhood of the wall is adaptively reduced to equal to or close to the saturated air pressure, the Coanda effect is unstable and outflow occurs. The conditions for utilizing the Coanda effect in the present invention are: the outside of the exit stream beam has a sufficiently large static pressure guaranteed by the specific potential energy amplitude; the relative velocity of the liquid flow exit is restricted by the minimum potential-to-kinetic ratio, and its momentum inertia is limited; The surface is mathematically smooth, has continuity of curvature, and has a large radius of curvature. The required centripetal acceleration of the Coanda is always less than the amplitude defined by the specific potential energy. Therefore, the Coanda effect is stable and no outflow occurs.

出口外柱面或槽面与圆周柱面之间的流道截面积与圆心角成周期性线性关系是另一项重要特征，其作用除了强化附壁效应的稳定性以外，更主要的目的是在出口间隔区重新生成均勾的径向速度分量。由于出口外柱面或槽面与圆周柱面之间的流道的外侧已经开放，叶轮所能够产生的作用只能是附壁效应的单边约束。依靠该约束就能在出口及其间隔位置形成压力、流速及其径向和切向分量均匀分布的流场，这是本发明的一项创举。单边约束虚拟重构了连续开口的效果，克服了现有技术中无轮沿约束所带来的轮沿回流、脱流等系列问题。这种机制使叶轮流道的内部和出口区同时满足了完备约束条件，因而从源头上解决了叶轮流道与导流器流道连接时的局部激励问题。并且，叶轮圆周面上的压力和速度的均匀分布是一种与运行工况无关的状态，从而产生了变工况运行的完全适应性。 The periodic linear relationship between the cross-sectional area of the flow channel between the outer cylindrical surface of the outlet or the groove surface and the circumferential cylindrical surface and the center angle is another This important feature, in addition to enhancing the stability of the Coanda effect, is more important to regenerate uniform radial velocity components in the exit interval. Because the outer side of the flow channel between the outer cylindrical surface of the outlet or the groove surface and the circumferential cylindrical surface is already open, the effect that the impeller can produce can only be a unilateral constraint of the Coanda effect. Relying on this constraint, a flow field with uniform distribution of pressure, velocity, and radial and tangential components can be formed at the outlet and its spaced position, which is an innovation of the present invention. The unilateral constraint virtually reconstructs the effect of continuous openings, and overcomes a series of problems such as rim backflow and outflow caused by rimless constraints in the prior art. This mechanism makes the internal and outlet areas of the impeller flow path meet the complete constraint conditions at the same time, thus solving the problem of local excitation when the impeller flow path is connected to the deflector flow path from the source. In addition, the uniform distribution of pressure and speed on the impeller's circumferential surface is a state independent of operating conditions, which results in complete adaptability to variable operating conditions.

现有技术的大开口几乎是连续的，由于相对速度很小和没有轮沿径向约束，在有限叶片叶轮流道中的相对涡旋的外展倾向作用下，轮沿出口区附近会产生回流、湍流和吸力面尾部低压区等许多不稳定现象。这些现象危害较烈，叶轮水力效率因而下降许多。这是热门课题，学术界对其进行了许多研究，包括采用三维湍流理论的分析成果和采用超声或激光技术测量的数据，文献浩瀚，规律也已基本摸清。在势流理论的指导下，人们对相对涡旋所造成的压力面大回流已经釆取了许多措施，例如较小的后弯角就可以减缓和控制回流，但付出了增大叶片包角和增加沿途损耗的代价。大开口叶轮的叶片吸力面尾缘涡现象是造成叶轮水力损耗的另一个重要原因，这种现象在欠流量工况运行时会在尾迹区形成强烈的湍流和脱流，严重时可能造成较大角度的出口拥塞。吸力面尾缘涡对于转轴形成吸力阻碍，其作用力臂长，产生的阻力矩大，因而损耗功率大。尾缘涡是全部复杂力场综合作用的结果，不能用势流理论解释。究其技术设计上的原因，缺少约束的判断肯定是正确的。大开口叶轮流道及其出口流场的稳定性和均勾性问题，严重地制约着叶轮流程水力效率的提高，并且长期未能解决。实际上，在现有技术的结构框架下，在众多互相制约的因素中，寻找最优的折中方案是可能的，寻找根本性的解决办法则是困难的或不可能的。 The large opening in the prior art is almost continuous. Due to the small relative speed and no radial restraint of the wheel in the radial direction, under the action of the abduction tendency of the relative vortex in the flow path of the finite blade impeller, a backflow, Many unstable phenomena such as turbulence and low pressure region at the tail of the suction surface. These phenomena are more harmful, and the hydraulic efficiency of the impeller is greatly reduced. This is a hot topic, and a lot of research has been done on it in the academic community, including the analysis results using three-dimensional turbulence theory and data measured using ultrasound or laser technology. The literature is vast and the laws have been basically figured out. Under the guidance of the potential flow theory, people have taken many measures for the large recirculation of the pressure surface caused by the relative vortex. For example, a small back curve can slow down and control the recirculation, but the increase of the blade wrap angle and The cost of increasing losses along the way. The vortex at the trailing edge of the suction surface of the blade of a large-open impeller is another important cause of the hydraulic loss of the impeller. This phenomenon can cause strong turbulence and deflow in the wake area when running under flow conditions, and may cause large Angle of exit congestion. The trailing edge vortex on the suction surface forms a suction obstacle to the rotating shaft. The force arm is long and the resistance torque is large, so the power loss is large. The trailing edge vortex is the result of the combined effect of all complex force fields and cannot be explained by potential flow theory. Investigating its technical design reasons, the lack of constraints is certainly correct. The problems of the stability and uniformity of the large-open impeller flow channel and its exit flow field have seriously restricted the improvement of the hydraulic efficiency of the impeller process, and have not been solved for a long time. In fact, under the structural framework of the prior art, it is possible to find the optimal compromise solution among many mutually constraining factors, and it is difficult or impossible to find a fundamental solution.

本发明方案没有大开口，并且在出口区设置单边轮沿约束，这是一种出口区流场的超稳定机制。在这种设计下，相对涡旋不外展，出口轮沿区无回流的可能，轮沿区的湍流和脱流等导致损耗和气蚀的不稳定现象包括吸力面尾缘涡损耗将不复存在，出口区速度稳定，流线均匀，因而可以指望较高的叶轮程水力效率。 The solution of the present invention does not have a large opening, and a unilateral rim constraint is set in the exit area, which is a super-stability mechanism of the flow field in the exit area. Under this design, the relative vortex is not abducted, and there is no possibility of backflow in the wheel edge area of the exit. Turbulence and deflow in the wheel edge area will cause losses and cavitation instability, including the vortex loss at the trailing edge of the suction surface. The exit zone has a stable speed and a uniform streamline, so higher hydraulic efficiency of the impeller can be expected.

技术要素 b提供了具体计算出口面积和设定反馈减速比的方法。反馈减速比参数 K的重要性前文已经提及，后续说明中还要反复讨论。在叶轮的几何尺寸和转速确定以后，按照所述方法确定 κ和出口面积等参数，实际上已经全面确定了离心泵的设计工况，其各类特性曲线也将随之确定。 Technical element b provides a specific method for calculating the exit area and setting the feedback reduction ratio. The importance of the feedback reduction ratio parameter K has been mentioned before, and will be discussed repeatedly in subsequent descriptions. After the impeller geometry and rotation speed are determined, the parameters such as κ and outlet area are determined according to the method described. In fact, the design conditions of the centrifugal pump have been fully determined, and its various characteristic curves will be determined accordingly.

所述具体设计还同时确定了叶轮的设计工况参数。当运行工况发生变化时，反馈减速比 K与流量成正比地变化，比功或扬程则与流量成线性减函数关系。这些关系还表明，本发明产品能够在一个很宽的范围内变工况运行。变工况运行是一种广泛的需求，本发明不同于现有技术的运行特性，显然更符合变工况运行的实际需要。例如，本发明特有的流量一功率特性体现了较好的变工况适应性：在增大流量运行时轴功率的增大幅度较小，无过载的危险；在减小流量运行时其扬程急剧增大，功率下降的幅度也较小，当扬程增大到最大值以后，功率随负荷的降低而降低，渐近于固定的机械损耗功率。这是一种低端随负荷变而高端近似恒功率的理想特性。又例如，本发明特有的流量一效率特性更能体现其变工况适应性。在通常是欠流量运行的外部调节液流***中，现有技术离心泵低端效率陡降的特性将导致严重的能源浪费。而本发明的效率特性却是低端升高的，在釆用后述的内减摩技术后，这种低端效率不降反而上升的区域在对数坐标上甚至能再向低端平移一个指数区间。 ' 本发明之高势比叶轮的叶片形状设计方案是：叶轮叶片呈 L形，其前中部分别为直线段，呈径向走势，其肘部和尾部经恰当曲率半径过渡朝反切向弯曲，尾部具有隔离内外压差的机械强度和尖锐的末端，恰当曲率半径过渡包括内外两侧的造形变化，尾部内侧作为加速段外侧约束边与叶片肘部之间的距离满足流道加速段截面变化要求，尾部外侧满足附壁效应整理的走向角变化要求，肘部外侧曲率半径还满足不脱流条件。 The specific design also determines the design condition parameters of the impeller at the same time. When the operating conditions change, the feedback reduction ratio K changes proportionally to the flow rate, and the specific work or head has a linear decreasing function relationship with the flow rate. These relationships also show that the product of the present invention can operate under a wide range of operating conditions. Operation under variable working conditions is a broad requirement. The present invention is different from the operating characteristics of the prior art and obviously meets the actual needs of operation under variable working conditions. For example, the traffic specific to the present invention A power characteristic reflects better adaptability to variable working conditions: the increase in shaft power is small when the flow is increased, and there is no danger of overload; when the flow is reduced, the head is sharply increased, and the power is reduced. It is also small. When the head is increased to the maximum value, the power decreases with the decrease of the load and approaches the fixed mechanical power loss. This is an ideal characteristic that the low end varies with load and the high end approximates constant power. For another example, the flow-efficiency characteristic unique to the present invention can better reflect its adaptability to changing working conditions. In an externally regulated liquid flow system that is usually operated under-flow, the characteristic of the low-end efficiency of the prior art centrifugal pumps, which causes a steep drop in efficiency, will result in serious energy waste. However, the efficiency characteristics of the present invention are increased at the low end. After using the internal friction reduction technology described below, the area where such low end efficiency does not decrease but rises can even be shifted to the low end by one more on the logarithmic coordinates. Index interval. '' The blade shape design scheme of the high potential ratio impeller of the present invention is: the impeller blades are L-shaped, the front and middle portions are straight line segments, and they are in a radial direction, and the elbow and the tail are bent to the anti-tangential direction with a proper curvature radius transition, and the tail is It has the mechanical strength and sharp end to isolate the internal and external pressure difference. The transition of the proper curvature radius includes the shape change on both the inside and outside. The distance between the inner side of the tail as the outer restraint edge of the acceleration section and the blade elbow meets the change requirements of the cross section of the acceleration section of the flow channel. The outer side of the tail meets the requirements for the change in strike angle of the Coanda effect finishing, and the outer radius of curvature of the elbow also meets the condition of no flow.

上述叶片形状方案给出了实现轮沿约束和叶槽尾部加速的具体结构。轮沿约束是通过 The above-mentioned blade shape scheme gives a specific structure for realizing wheel edge restraint and blade groove tail acceleration. The rim constraint is passed

L形叶片尾部的近圆周向走势实现的，其内侧构成叶槽尾部加速段外侧约束壁面，其外侧构成出口外的渐开轮廓线柱面或槽面，用来约束整理口外流场。叶片的内外侧边际曲线用数值算法来构造是很方便的，用这种解法从圆周向内推算，能逐点实现口外轮廓线定位、叶片厚度、叶槽截面积等功能数据，每一点都要进行作用力、强度、流体运动等相关力学计算。其中，只有尾部两侧边际线和肘部压力侧曲率是流体力学敏感的。主要要求有两点，其一是逐步减小叶槽截面积，到出口时达到设计面积；其二是具有好的力学性能。其中间过程有无限多种可能的选择，其中存在并可以寻找最优的设计，但基本要求是边际光滑性。保障边际线数学光滑是对一阶空间变化率的要求，对应的力学价值是流速的方向连续性。不脱流力学方程检验主要运用质点曲线运动的牛顿定律及其作为动力来源的压差验算，一般都能得到满足。 The near-circumferential trend of the tail of the L-shaped blade is realized. The inner side constitutes the outer restraint wall surface of the tail end acceleration section of the blade groove, and the outer side constitutes an involute contour cylinder or groove surface outside the outlet, which is used to constrain the flow field outside the mouth. It is very convenient to use the numerical algorithm to construct the inner and outer marginal curves of the blade. Using this method to calculate from the circumference to the inside, the functional data such as the positioning of the contour line outside the mouth, the thickness of the blade, and the cross-sectional area of the blade groove can be realized point by point. Perform mechanical calculations such as force, strength, and fluid motion. Among them, only the marginal line on both sides of the tail and the pressure side curvature of the elbow are hydrodynamically sensitive. There are two main requirements. One is to gradually reduce the cross-sectional area of the blade groove to reach the design area by the exit; the other is to have good mechanical properties. The intermediate process has infinitely many possible choices. Among them, the optimal design exists and can be found, but the basic requirement is marginal smoothness. Guaranteeing the mathematical smoothness of the margin line is a requirement for the first-order spatial change rate, and the corresponding mechanical value is the directional continuity of the velocity. The test of non-drifting mechanics equations mainly uses Newton's law of particle curve motion and pressure difference check as a source of power, which can generally be satisfied.

上述详细方案与现有技术对比差异很大，但却合理。第一，有限叶片数叶轮的叶槽宽度是几何受限的，与叶片走向角的正弦成正比，叶片前中部设计成直线段和大曲率半径段并且呈径向走势，其叶槽及其入口的截面积被最大化，其相对流速因而最小。第二， L形叶片是减小流道出口面积后的一种必然的和优化的选择。因为，小出口在叶轮周长尺度上分布必然彼此相离，这就需要一个轮沿上的弧形结构来构造这种相离，并用作叶槽流道与轮外出口区的隔离和承压结构，这种结构只能是弯曲的叶片尾部。 The above detailed schemes are quite different from the prior art, but they are reasonable. First, the groove width of the impeller with a finite number of blades is geometrically limited, and is proportional to the sine of the blade's heading angle. The front middle part of the blade is designed as a straight line segment and a large radius of curvature and has a radial trend. Its groove and its entrance The cross-sectional area is maximized and its relative flow rate is thus minimized. Second, the L-shaped blade is an inevitable and optimized choice after reducing the outlet area of the flow channel. Because the distribution of the small outlets on the perimeter of the impeller is necessarily separated from each other, this requires an arc structure on the rim to construct this separation, and is used as the isolation and pressure of the blade groove flow channel and the outer exit area of the wheel. Structure, this structure can only be a curved blade tail.

本发明的这种改进方案在加大叶槽截面积的同时，还减小了叶片包角，因而缩短了叶槽流程。较之现有技术后弯式叶片的设计，其叶槽加载区的截面积大约增大 1倍，叶槽加载做功区流程大约减小 50%。按此粗略估值计算，较之直径、转速和流量相同的传统离心泵叶轮，本发明方案叶槽加载区的流速将降低 50%，其单位长度上的摩擦损耗将减少 75 % , 因而其叶槽加载区的沿途摩擦损耗将减少 87.5%。 This improved solution of the present invention reduces the blade wrap angle while increasing the cross-sectional area of the blade groove, thereby shortening the blade groove flow. Compared with the prior art backward curved blade design, the cross-sectional area of the blade groove loading area is approximately doubled, and the flow process of the blade groove loading work area is reduced by approximately 50%. Based on this rough estimate, compared with traditional centrifugation with the same diameter, speed and flow For the pump impeller, the flow velocity in the blade groove loading area of the solution of the present invention will be reduced by 50%, and the friction loss per unit length thereof will be reduced by 75%, so the friction loss along the blade groove loading area will be reduced by 87.5%.

这种改进方案的叶槽尾部是加速区，其截面积以恰当的变化率较快地连续减小，流速因而迅速地连续增加，这是旋转坐标系中的能量转换过程，会发生一定的损耗。具体设计加速流道时，应从流量和出口相对速度决定的出口截面积出发，确定一个恰当的截面积变化率来反推尺寸，流速的空间变化率和叶槽形状都将被从中确定。由于该流程段很短，当左右时，水力损耗并不显著。加速段的基本方程式是：比动能增量 =比势能减量 X 效率，其中的效率因子与截面积变化率和表面质量等因素有关，参照类似的射流技术的经验数据分析，其加速效率通常可以达到 98%。因此，按势流理论分析的结果是： L形叶片流道的全部水力损耗较之现有技术将有明显的减少。实际上，更进一步的对比优势将主要来自流场稳定性方面的差异。由于大开口所造成的相对涡旋外展及二次流等因素所造成的湍流、回流以及尾迹涡旋等不稳定现象的影响，现有技术叶轮流道的水力损耗是比较大的。相比之下，本发明 L形叶片方案的流场不稳定因素少，除了叶槽内的相对涡旋影响以外，不存在出口回流和尾缘涡，其叶轮水力效率将大为提高。况且，本发明还有后续说明的技术特征能够基本遏制住叶槽内的相对涡旋，其效率将会更具优势。 The tail of this improved solution is the acceleration zone, and its cross-sectional area is continuously and rapidly reduced at an appropriate rate of change, and the flow velocity is therefore rapidly and continuously increased. This is an energy conversion process in a rotating coordinate system, and certain losses will occur. . When designing the accelerating flow path, we should start from the outlet cross-sectional area determined by the flow rate and the relative velocity of the outlet, determine an appropriate cross-sectional area change rate to infer the size, and the spatial change rate of the flow velocity and the shape of the blade groove will be determined from it. Due to the short flow section, the hydraulic loss is not significant when left and right. The basic equation of the acceleration section is: specific kinetic energy increase = specific potential energy decrease X efficiency, where the efficiency factor is related to the cross-sectional area change rate and surface quality and other factors. With reference to empirical data analysis of similar jet technologies, its acceleration efficiency can usually be Reached 98%. Therefore, according to the analysis of potential flow theory, the total hydraulic loss of the L-shaped blade flow channel will be significantly reduced compared with the prior art. In fact, the further comparative advantage will mainly come from the differences in flow field stability. Due to the effects of instability such as turbulence, backflow, and wake vortex caused by factors such as relative vortex abduction and secondary flow caused by large openings, the hydraulic loss of the prior art impeller runner is relatively large. In contrast, the L-shaped blade solution of the present invention has less instability in the flow field. Except for the relative vortex effect in the blade groove, there is no outlet return flow and trailing edge vortex, and the impeller hydraulic efficiency will be greatly improved. Moreover, the technical features described later in the present invention can basically restrain the relative vortex in the blade groove, and its efficiency will be more advantageous.

本发明改进方案中叶片前中部的径向走势对于提高抗气蚀性能也具有明显的意义。在现有技术中，气蚀危害最严重的区域是入口区叶片两侧和出口区的吸力侧。对于入口区，本发明的叶片设计间距成倍增加，在同样的设计流量下其流速将减半。如附加后述说明介绍的自适应预旋器的配合，这种叶轮将具有特别好的入口区抗气蚀特性。对于出口区，由于完备约束，尾缘涡或吸力面低压区已经不存在，在较高的正压下无气蚀可能性。 The radial trend of the front and middle part of the blade in the improved scheme of the present invention is also significant for improving the cavitation resistance. In the prior art, the areas with the most severe cavitation damage are the sides of the blades in the inlet area and the suction side in the outlet area. For the inlet area, the design pitch of the blades of the present invention is doubled, and the flow velocity will be halved at the same design flow rate. As described in the appended description of the adaptive pre-spinner, this type of impeller will have particularly good anti-cavitation characteristics in the inlet area. For the exit area, due to complete constraints, the trailing edge vortex or the low-pressure area of the suction surface no longer exists, and there is no possibility of cavitation at higher positive pressures.

本发明前中部径向走势和 90度入口角的 L形叶片设计，是一种适合于高势比离心泵的特别设计，具有叶片包角小、叶槽前中部截面积大、流程短、流速低因而摩擦损耗小的优势，对于低比转数叶轮，其优势将更为明显。这种叶轮除了输出高势动比液流的主要目标特性以外，还兼具叶轮流程水力效率高、抗气蚀特性好的优点。本发明还包括一个配套的附件设计，即：叶轮吸入室或前级导流器出口装有一个与叶轮同轴旋转的轴向或径向来流自适应预旋器，预旋器由弹性帆式叶片、轮圈和刚性肋条组成，其叶片数少于叶轮叶片数，叶片由复合材料制成，具有由前端到根部逐渐增大的拉伸弹性系数，被径向固定于轮圈之等角度分布的装配位置上，轮圈自由地套在转轴或叶轮轴套上，叶片前端悬挂于入口处的刚性肋条上，叶片之间构成预旋流道。其中，轴向来流预旋器的刚性肋条布设于入口圆周面上的径向位置，径向来流预旋器的刚性肋条布设于入口圆柱面上与转轴平行的位置。运行中，弹性帆式叶片将随液流参数的变化而变形为自适应流道，其入口迎角及沿途倾角都是自适应变化的。 The design of the L-shaped blade in the radial direction of the front part of the present invention and a 90-degree inlet angle is a special design suitable for high-potential centrifugal pumps. The advantage of low friction loss is small. For low specific speed impellers, the advantages will be more obvious. In addition to the main target characteristics of outputting high potential-to-dynamic ratio liquid flow, this type of impeller also has the advantages of high hydraulic efficiency and good anti-cavitation characteristics of the impeller process. The invention also includes a matching accessory design, that is, an axial or radial inflow adaptive pre-spinner that rotates coaxially with the impeller is installed at the impeller suction chamber or the front stage deflector outlet. The blades, rims and rigid ribs are composed of fewer blades than impeller blades. The blades are made of composite material and have a tensile elastic coefficient that gradually increases from the front end to the root. They are radially fixed to the rim at an equal angular distribution. In the assembled position, the rim is freely sleeved on the rotating shaft or the impeller sleeve, and the front end of the blade is suspended on a rigid rib at the entrance, and a pre-spinning flow channel is formed between the blades. Among them, the rigid ribs of the axial flow pre-rotator are arranged at a radial position on the circumferential surface of the inlet, and the rigid ribs of the radial flow pre-rotator are arranged at a position parallel to the rotation axis on the cylindrical surface of the inlet. During operation, the elastic sail blade will be deformed into an adaptive flow channel with the change of the flow parameters, and the angle of attack and the inclination angle along the way are adaptively changed.

现有技术的离心泵设计观念认为应该避免正预旋，其指导思想是通过增加入口相对速度来增大比功和扬程。例如现有技术多级泵设计规范中的反导叶出口角度，就被设计成不但消除原有环量，还施加了一个反向环量，显然是出于这一目的。这样做的结果，扬程是提高了，但付出的代价是入口水力损失增大、抗气蚀特性变差、变工况运行适应性变差。本发明基于保守环量设计的观念，主张在叶轮流道入口的前承邻域内保守或者设置正预旋。自适应预旋器的设计正是这种指导思想的产物，这与传统设计相反，效果也正好相反。预旋器的作用是，以减小那部分本来就不应该额外增大的叶轮比功为代价，换取入口水力损失小、抗气蚀特性好、具有变工况运行自适应性的好处，因而是一种舍小取大的技术权衡。并且，前述 90度入口流道的特征设计，也需要预旋器来配套。 The prior art centrifugal pump design concept believes that positive pre-spin should be avoided, and its guiding idea is to increase the relative speed of the inlet Degrees to increase specific work and head. For example, the anti-lead vane exit angle in the prior art multi-stage pump design specifications is designed not only to eliminate the original loop volume, but also to apply a reverse loop volume, obviously for this purpose. As a result, the lift is increased, but the price paid is increased inlet hydraulic loss, poor cavitation resistance characteristics, and poor operating adaptability under variable operating conditions. The present invention is based on the concept of conservative loop design, and advocates that conservative or pre-spinning is set in the front bearing neighborhood of the impeller flow channel entrance. The design of the adaptive pre-rotator is the product of this guiding idea, which is the opposite of traditional design and the effect is exactly the opposite. The role of the pre-rotator is to reduce the specific work of the impeller that should not have been increased, in exchange for small inlet hydraulic losses, good anti-cavitation characteristics, and the benefits of adaptive adaptation to variable operating conditions. It is a kind of technical trade-off between small and big. In addition, the aforementioned characteristic design of the 90-degree inlet flow channel also needs a pre-spinner to be matched.

自适应预旋器是一个单独的调节性做功部件，相当于一个特殊的小叶轮，用来调整来流速度的大小和方向，使之符合叶轮吸入的需要。当来流旋转能量不足时，预旋器输出比功予以增加。当来流旋转速度过大时，预旋器也能在速度场整理中吸收掉多余部分，自身则转变为水轮机工作状态。能量调整是对来流进行速度场整理的一种宏观统计效果，速度场整理的含义是：通过弹性螺桨形流道进行分布式能量交换，连续改变来流速度的大小和方向的空间分布，使之在叶槽入口处与整体工况决定的速度分布相适应。 The adaptive pre-spinner is a separate regulating work component, which is equivalent to a special small impeller, which is used to adjust the magnitude and direction of the flow velocity to meet the needs of the impeller suction. When the incoming rotation energy is insufficient, the pre-rotator output specific power is increased. When the rotation speed of the incoming flow is too large, the pre-spinner can also absorb the excess part in the speed field arrangement, and it itself changes to the working state of the water turbine. Energy adjustment is a macro statistical effect of the velocity field arrangement of the incoming flow. The meaning of the velocity field arrangement is: distributed energy exchange through the elastic propeller-shaped flow channel, and the spatial distribution of the magnitude and direction of the incoming flow is continuously changed. It is adapted to the velocity distribution determined by the overall operating conditions at the entrance of the blade groove.

预旋器的这些特性功能主要是为了与 L形叶片的前部径向走势配套，同时使叶轮适应变工况运行的需要。实现这些功能的机理是：当工况参数变动时，吸入室区域的变化体现为流量变化以及由流量变化引起的速度大小和方向的变化。由于预旋器与叶轮同轴旋转，因而其入口处的刚性肋条及悬挂的帆式叶片是匀速转动的，它们切入液流的速度会随着流量的变化而变化。在切入线的一个空间邻域内，液流的惯性力和柔软叶片入口部位的张力的分布会在叶片上的每一个点都达成一种平衡，这种力平衡点汇集的几何效果是帆式叶片之始端将自适应地随来流速度的变化而改变迎角，从而自动保持与来流流线相切的状态。这种机制解决了传统叶轮在流量变动时速度的大小和方向的变化将导致与角度固定的叶片发生撞击而产生入口湍流等工况变动不适应的问题。 These characteristics of the prespinner are mainly to match the radial direction of the front of the L-shaped blade, and at the same time to adapt the impeller to the needs of variable operating conditions. The mechanism to achieve these functions is: When the working condition parameters change, the changes in the suction chamber area are reflected as changes in flow and changes in speed and direction caused by changes in flow. Because the pre-spinner and the impeller rotate coaxially, the rigid ribs at the entrance and the hanging sail blades rotate at a constant speed. The speed at which they cut into the flow will change with the change of the flow. In a spatial neighborhood of the cut-in line, the inertial force of the liquid flow and the distribution of the tension at the entrance of the soft blade will reach a balance at each point on the blade. The geometric effect of this force balance point is the sail blade The beginning will adaptively change the angle of attack as the incoming flow speed changes, thereby automatically maintaining a state tangent to the incoming flow line. This mechanism solves the problem that the changes in the speed and direction of the traditional impeller when the flow rate changes will cause collision with the blade with a fixed angle, resulting in turbulence at the inlet and other conditions.

来流在入口区无撞击相切进入以后，在后续的预旋流道区域更能保持相切流动的状态，其力学原理仍然是液流的惯性力和叶片张力以及抗弯力的平衡。其中，越来越大的叶片径向抗弯强度将逐步增加法向约束强度，直到与叶轮流道连接的出口，其出口方向将基本上是叶轮入口方向。来流在这种柔性逐步减小的螺桨形流道中受叶片约束力作用连续改变速度的大小和方向，到出口处时就具有了被预设的方向，而流道各处的速度大小则可以随流量变化而变化，同一流量下各处速度的变化则是叶片约束和因约束进行能量交换的结果。 After the incoming flow enters without impact and tangent in the inlet area, the tangential flow state can be maintained in the subsequent pre-spinning channel area. Its mechanical principle is still the balance of the inertial force of the flow, the blade tension, and the bending resistance. Among them, the radial bending strength of larger and larger blades will gradually increase the normal restraint strength until the exit connected to the impeller flow channel, and the exit direction will basically be the impeller inlet direction. The incoming flow is continuously changed in speed and direction by the blade restraining force in this flexible and gradually decreasing propeller-shaped flow channel. When it arrives at the exit, it has a preset direction, and the speed of the flow channel is It can change with the change of the flow rate, and the change of the speed of each place under the same flow rate is the result of the blade constraint and the energy exchange due to the constraint.

预旋器使叶轮在变流量工作时入口区流线均匀而平稳，不产生撞击、湍流和脱流损耗。这使入口区水力损耗保持低水平，并且气蚀特性也大为改善。本发明的系列设计还包括另一项更为重要的特征，那就是：叶轮叶槽中布设遏制相对涡旋的均速岔道。每个叶槽流道被 1〜3片均速梳叶纵向分割，形成 2〜4个岔道。岔道入口接近而未达到叶槽入口，其截面积均匀分配。岔道出口接近而未达叶槽出口，截面积依据所叠加的相对涡旋的动力分布和给定的速度分布确定的、或通过优选试验优化的经验数据分配。均速梳叶对相对涡旋施加抗性遏制力，形成均匀的叶槽速度分布，并产生所需的入口压力梯度和出口速度梯度。 The pre-spinner makes the impeller flow line in the inlet area uniform and stable during variable flow operation, without impact, turbulence and outflow loss. This keeps the hydraulic loss in the inlet area low and greatly improves cavitation characteristics. The series design of the present invention also includes another more important feature, which is: Vortex bifurcation. Each blade groove flow channel is longitudinally divided by 1 to 3 uniform-speed combing leaves to form 2 to 4 bifurcations. The entrance of the fork is close to the entrance of the slot, and its cross-sectional area is evenly distributed. The exit of the bifurcation is close to the exit of the vane slot, and the cross-sectional area is determined based on the superimposed relative vortex dynamic distribution and a given speed distribution, or by empirical data optimization optimized by preferred experiments. The uniform-speed combing blade exerts resistance and restraining force on the relative vortex, forms a uniform groove velocity distribution, and generates the required inlet pressure gradient and outlet velocity gradient.

本发明的叶槽均速岔道是为解决相对涡旋这一影响叶轮水力效率的关键问题而专门设计的特别结构。相对涡旋是有限叶片数叶轮内部自由流体的惯性运动形态，这种运动会产生与无限叶片数叶轮不同的速度场结构而改变其比功值，使泵的理论扬程降低 15 %〜25 %。另外，相对涡旋还直接产生严重的损耗，其速度和压力是不均匀分布的，它叠加于叶槽流场，形成回流、湍流和低压脱流区，产生较大的损耗，使实际扬程进一步降低。液流叠加相对涡旋会产生压力面与吸力面之间的附加压差，直接形成附加阻力矩和附加功率损耗，使无效比功的比例增加，这也是实际扬程进一步降低的原因之一。 The blade groove average speed bifurcation of the present invention is a special structure specially designed to solve the relative vortex, a key problem affecting the hydraulic efficiency of the impeller. Relative vortex is the inertial motion of free fluid inside a finite-blade number of impellers. This motion will produce a different velocity field structure than the infinite-blade number of impellers and change its specific work value, reducing the theoretical head of the pump by 15% to 25%. In addition, the relative vortex also directly generates serious losses, and its velocity and pressure are unevenly distributed. It superimposes on the flow field of the lobes, forming recirculation, turbulence, and low-pressure deflow regions, resulting in greater losses and further actual lift. reduce. The superimposed relative vortex of the liquid flow will generate an additional pressure difference between the pressure surface and the suction surface, which will directly form an additional drag torque and additional power loss, which will increase the proportion of the invalid specific work, which is one of the reasons for the further reduction of the actual head.

从离心泵的压力系数法设计实践中也可以看出问题的严重性。没有相对涡旋的无限叶片数叶轮的理论压力系数等于 2，其中比势能和比动能分压力系数分别为 1。但传统离心泵的设计压力系数却通常只能达到 1左右，最高的只有 1.1。压力系数的减少值在 0.9以上，其主要原因有三个：有限叶片使输送比功减小和理论扬程降低；叶轮流程损耗使实际扬程下降；导流流程损耗使实际扬程进一步下降。三大原因中的前两大原因都是相对涡旋作祟，由此可见遏制相对涡旋在技术上的重要性。 The seriousness of the problem can also be seen in the design practice of the pressure coefficient method of the centrifugal pump. The theoretical pressure coefficient of an impeller with an infinite number of vanes without relative vortex is equal to 2, where the specific potential energy and specific kinetic energy partial pressure coefficients are 1 respectively. However, the design pressure coefficient of traditional centrifugal pumps usually can only reach about 1, and the highest is only 1.1. The decrease of the pressure coefficient is above 0.9. There are three main reasons for this: The finite blade reduces the specific work and the theoretical head; the impeller flow loss reduces the actual head; and the diversion flow loss further reduces the actual head. The first two of the three major causes are relative vortexes, which shows the technical importance of curbing relative vortexes.

相对涡旋的强度随着叶片数的减少而单调增大。对于叶片数等于 6〜8 这样的常规选择的比尺度，相对涡旋理论角速度的绝对值几乎和叶轮角速度相等，其理论线速度的最大值约为叶轮圆周速度的 1/3左右，在数值上可能达到每秒十几米。这样大的涡旋速度和较小的相对速度进行矢量合成，对于液流出口角较大的传统叶轮来说，将产生绝对值比边沿涡旋速度高 1倍相对流速的吸力面髙速正向流，产生绝对值比边沿涡旋速度低 1倍相对流速但仍属高速的压力面回流。尽管边际摩擦和内部粘滞力会遏制这种高速流，能使其降到一个较低的平衡值，但损耗却随之产生。相对涡旋产生的回流、湍流和脱流问题严重时，叶轮的设计出口.将被挤占一部分，成为徒增损耗的有害空间，并且还可能生成叶频压力波而产生百赫兹级的径向振动。当然，对于本发明来说，出口回流已经完全消灭，上述问题已经解决了大部分，但是，叶槽流道内部的相对涡旋却仍然存在。因此，釆用一种抗性而非阻性的遏制相对涡旋的方法，用来施加有针对性的剪力矩，使叶片吸力面减速和使压力面加速，同时吸收和转化剩余的涡旋能量，就成为本发明的一种必要的改进设计。本发明的均速岔道正是上述设计思想的产物。按照所述的设计要求，均速岔道布设在叶槽流道之前中部截面宽阔处，对流道截面积的挤占系数并不大。由前述分析可知，叶槽宽阔处的流速本来较低，如果将相对涡旋遏制住，则涡旋速度对吸力面的正叠加和对压力面的负叠加将被消除，叶槽将恢复为正常的低速流态。本发明遏制相对涡旋的原理是： 1)、大体径向走势的岔道之压力面和吸力面约束力是不均匀分布的，它们会对每一岔道之涡旋中心形成一个圆周面上的反向剪力矩，其作用相当于增加叶片数； 2)、 L形叶片与岔道结构的弯曲配合使岔道的内外壁不等长，内外岔道不等长且相差较大，其沿途阻力的差别与遏阻涡旋动力的需求相一致； 3) 、更重要的是，岔道出口截面积的不均匀分配控制着各岔道的内外流速，使近主叶片吸力面之岔道有较高的出口速度而近压力面之岔道有较低的出口速度，其反作用抗力的差别将在圆周面上产生相对于整个叶槽涡旋中心的遏制力矩，或者说，其反作用抗力的差别正好等于岔道牵连运动的涡旋动力差别，从而实现所希望的速度均匀分布。 The intensity of the relative vortex increases monotonically as the number of blades decreases. For a conventionally selected ratio scale such as the number of blades is 6 to 8, the absolute value of the relative vortex theoretical angular velocity is almost equal to the impeller angular velocity, and the maximum value of the theoretical linear velocity is about 1/3 of the peripheral velocity of the impeller. May reach a dozen meters per second. Such a large vortex speed and a small relative speed perform vector synthesis. For a traditional impeller with a large liquid flow exit angle, it will produce a suction surface forward velocity with an absolute value that is 1 times higher than the edge vortex speed. , Which produces a pressure surface with an absolute value that is 1 times lower than the relative speed of the edge vortex, but still at a high speed. Although marginal friction and internal viscous forces will curb this high-speed flow and reduce it to a lower equilibrium value, losses will occur. When the problems of backflow, turbulence and deflow caused by relative vortex are serious, the impeller's design exit will be squeezed up and become a harmful space with excessive loss. It may also generate blade-frequency pressure waves and generate a hundred-hertz-level radial vibration. . Of course, for the present invention, the outlet backflow has been completely eliminated, and most of the above-mentioned problems have been solved, but the relative vortex inside the channel of the blade groove still exists. Therefore, I used a method of resisting rather than resisting the relative vortex to apply a targeted shear moment to decelerate the suction surface of the blade and accelerate the pressure surface, while absorbing and transforming the remaining vortex energy. , It becomes a necessary improved design of the present invention. The uniform speed bifurcation of the present invention is the product of the above design idea. According to the design requirements, the uniform speed bifurcation is arranged at a wide cross section in the middle of the front of the channel of the blade groove, and the crowding coefficient of the cross-sectional area of the convection channel is not large. It can be known from the foregoing analysis that the flow velocity in the wide part of the blade groove is originally low. If the relative vortex is restrained, the vortex velocity is positively superimposed on the suction surface and pressure. The negative superposition of the surface will be eliminated, and the leaf groove will return to the normal low-speed flow state. The principle of curbing relative vortexes of the present invention is: 1) The binding forces of the pressure surface and the suction surface of a branch road in a generally radial direction are unevenly distributed, and they form a counter-surface on the circumferential surface of the vortex center of each branch road. The shearing moment is equivalent to increasing the number of blades. 2) The bending cooperation between the L-shaped blade and the fork structure makes the internal and external walls of the fork unequal in length, and the internal and external forks are unequal in length and have a large difference. The requirements of the vortex resistance are consistent; 3), more importantly, the uneven distribution of the cross-sectional area of the branch exit controls the internal and external flow velocity of each branch, so that the branch near the suction surface of the main blade has a higher exit velocity and near pressure The branch road has a relatively low exit velocity. The difference in the reaction resistance will produce a restraining moment on the circumferential surface relative to the center of the entire vortex vortex. Or, the difference in the reaction resistance is exactly equal to the vortex power of the branch road involved motion. Difference, so as to achieve the desired uniform speed distribution.

由于岔道分布于叶槽的非进出口区域，那么余下的进出口区域还会存在较小的相对涡旋倾向。所述方案要求，均速岔道的出口截面积之比应该产生恰当的入口压力梯度，用以生成遏制入口区涡旋的剪力矩，还应该产生恰当的出口速度梯度，用以改变岔道出口的压力分布，引射近压力面岔道，并减小叶槽出口区外的轮周摩擦。详细准确的动力学计算或者渐近试验均能做到所述的恰当，其结果将落实为岔道结构的具体比尺寸并使之优化。需要说明的是，大部分涡旋动力在近吸力面岔道中形成加速压力时被反作用抗力抵消了，在旋转坐标系中不存在正的涡旋能量积累的问题，受到涡旋动力影响的将只有沿正方向流出的液流，其比能增量形成了所述的速度梯度。 Because the bifurcation is distributed in the non-import and export areas of the blade grooves, the remaining import and export areas will still have a relatively small vortex tendency. The solution requires that the ratio of the cross-sectional area of the exit of the average speed fork should generate an appropriate inlet pressure gradient to generate the shear moment that curbs the vortex in the entrance zone. It should also generate an appropriate exit velocity gradient to change the pressure at the outlet of the fork Distribution, injecting a bifurcation near the pressure surface, and reducing wheel friction around the exit area of the blade groove. Detailed and accurate dynamic calculations or asymptotic tests can achieve the appropriateness as described, and the results will be implemented into the specific specific size of the branch structure and optimized. It should be noted that most of the vortex power is offset by the reaction resistance when the acceleration pressure is formed in the near-suction bifurcation. There is no problem of positive vortex energy accumulation in the rotating coordinate system, and only the vortex power will be affected. The specific energy increase of the liquid flow flowing in the positive direction forms the speed gradient.

均速岔道是一项非常重要的革新。恰当的岔道出口面积比能够在叶槽内的两个维度上实现抗性均衡，几乎可以将叶轮流道内的相对涡旋完全遏制住，叶轮流道的水力效率将因此而大幅度提髙，其气蚀特性也将大为改善。均速岔道对相对涡旋的有效遏制将使叶轮的各项性能均接近于无限叶片数叶轮之性能，其中最重要的贡献包括理论扬程的恢复，也包括因叶轮流程水力损失的减少而使理论扬程与实际扬程的差值减少。由于带均速岔道的 L形叶片叶轮之理论比功和理论扬程非常接近于无限叶片数欧拉方程规律，因而可以启用该方程来讨论有限叶片数髙势比叶轮的性能。 The average speed fork is a very important innovation. The proper exit area ratio of the bifurcation can achieve resistance balance in two dimensions in the blade groove, which can almost completely restrain the relative vortex in the impeller flow channel, and the hydraulic efficiency of the impeller flow channel will be greatly improved because of this. Cavitation characteristics will also be greatly improved. The effective containment of the relative vortex by the average speed bifurcation will make the performance of the impeller close to that of the infinite number of impellers. The most important contribution includes the recovery of the theoretical head, and the theoretical reduction due to the reduction of the hydraulic loss of the impeller flow. The difference between the head and the actual head is reduced. Because the theoretical specific work and theoretical head of an L-shaped blade impeller with a uniform speed bifurcation are very close to the law of the Euler equation of infinite blade number, this equation can be used to discuss the performance of a finite blade number pseudopotential ratio impeller.

在 L形叶片叶轮流道之入口角（相对液流角）等于 90度和出口角约等于 0度的条件下，根据入口和出口速度三角形，有^²= ²+^¥ 和 v₂ ²= (u₂—w₂)²。再引进叶轮入口牵连速度系数 x ut/ 和入口相对速度系数 Wi/Ws两参数，则有 _Ul ²=u₂ ²x²， w,²=u₂^ ²K²， w₂ ²=u₂ ²K², v₂ ²=u₂ ²(l— K)^f!_Vl ²=u₂ ² (χ²+μ²Κ²), 利用这些关系式将欧拉氏比功方程的所有各项对 u₂归一化，得方程的设定参数形式如（3) 式，其中包含具有重要意义的理论压力系数 Ψ_Τ，其表达式如（4) 式。 Under the condition that the inlet angle (relative flow angle) of the L-shaped blade impeller flow channel is equal to 90 degrees and the outlet angle is approximately equal to 0 degrees, according to the inlet and outlet speed triangles, there are ^ ² = ² + ^ ¥ and v ₂ ² = (u ₂ —w ₂ ) ² . Introducing the impeller inlet implication speed coefficient x ut / and the relative inlet speed coefficient Wi / Ws, there are _Ul ² = u ₂ ² x ² , w, ² = u ₂ ^ ² K ² , and w ₂ ² = u ₂ ² K ² , v ₂ ² = u ₂ ² (l— K) ^ f! _Vl ² = u ₂ ² (χ ² + μ ² Κ ² ), and use these relations to pair all terms of the Euler's specific work equation U _{2 is} normalized, and the set parameter form of the equation is as in formula (3), which contains the theoretical pressure coefficient _{Τ τ} which has significant meaning, and its expression is as in formula (4).

Y_T=0.5 ²R₂ ²((l-x²-K²(l-u²))+(l -χ²-2Κ+Κ²(1-μ²)) Y _T = 0.5 ² R ₂ ² ((lx ² -K ² (lu ² )) + (l -χ ² -2Κ + Κ ² (1-μ ² ))

= ²R₂ ²(l-x²-K) (3)= ² R ₂ ² (lx ² -K) (3)

Ψχ=(1- ²-Κ²(1- μ ²))+( 1 - Χ²-2Κ+ ²(1-μ ²)) =2(1— x ²— K) (4) 两式中，（1— Χ ²—Κ²(1— μ ² ))是比势能增量压力系数，（1— Χ ²—2Κ +Κ²(1— μ ² ))是比动能增量压力系数， Κ为反馈减速比， ω为叶轮角速度， R₂为叶轮半径。由于入口牵连速度系数 x =Ui/u₂的值等于叶轮入出口半径之比是一个固定不变的几何参数。又根据不可压缩流体的特性，入口相对速度系数 μ =_Wl/w₂的值等于叶轮流道入出口截面积之反比也是一个固定不变的几何参数。经参数变换后，方程只包含叶轮的圆周速度和 3个归一化系数，这就大大地方便了对新型叶轮特性的分析讨论。 Ψχ = (1- ² -Κ ² (1- μ ² )) + (1-χ ² -2Κ + ² (1-μ ² )) ^{= 2 (1- x 2 - K} ) (4) wherein ^{^{two, (1- Χ 2 -Κ 2 (}} 1- μ 2)) than the potential incremental pressure ^{coefficient, (1- Χ 2 -2Κ + Κ} 2 (1— μ ² )) is the specific kinetic energy incremental pressure coefficient, κ is the feedback reduction ratio, ω is the impeller angular velocity, and R ₂ is the impeller radius. Since the value of the inlet implication speed coefficient x = Ui / u ₂ is equal to the ratio of the impeller inlet and outlet radius, it is a fixed geometric parameter. According to the characteristics of the incompressible fluid, the value of the relative velocity coefficient μ = _Wl / w ₂ at the inlet is equal to the inverse ratio of the cross-sectional area of the inlet and outlet of the impeller flow path, which is also a fixed geometric parameter. After the parameter transformation, the equation only includes the peripheral speed of the impeller and three normalized coefficients, which greatly facilitates the analysis and discussion of the characteristics of the new impeller.

在方程式（3) 和理论压力系数表达式（4) 中保留比势能增量和比动能增量分压力系数的表达式有多种需要，两种能量生产的理论分析、理论和实际势动比的因变分析都需要用到它们。显然，两个表达式的组项构成凸显了比势能增量分压力和比动能增量分压力的力学来源及其比例关系。其中，比势能增量压力系数是由离心力功压力系数 1一 X ²和用于加速相对运动的势能消耗压力系数减量项一 K²(l— μ ² )的代数和组成的，而比动能增量压力系数则是由与离心力功压力系数等量的叶片剩余加速力功压力系数 1一 x ²、动能反馈于转轴使其减功的压力系数减量项一 2Κ和因相对运动加速而增加的压力系数增量项 K²(l— μ ² )的代数和组成的。 — Κ²(1— μ ² )和 Κ²(1— μ ² )项的存在表示叶槽流道尾部液流加速时势能转换为动能的过程存在，转换量的归一化比例系数分别与 Κ正相关而与 μ负相关锐变化，但它们在总的理论压力系数中互相抵消而不产生影响。 J人上面的分析可知，离心力功压力系数 1一 X ²和叶片剩余加速力功压力系数 1一 X ²两者等量，这是离心泵叶轮比功分配和扬程生成的普遍规律。当不进行技术处理时，离心泵叶轮的理论压力系数将为 2 ( 1— X ²)，其理论势动比等于 1。显然，本发明中同样产生了两个 1一 X ²项，在动能反馈技术的处理机制作用下，叶轮向转轴反馈了归一化系数为一 2K的比动能，理论压力系数减小为 2 ( l - x ²-K) , 理论势动比则因此而获得大幅度的增大。由于势能和动能的生产具有不同的实际转换效率，在计及损耗时需要分别按照各自流程的水力效率来计算实际的压力系数，这时，比势能增量和比动能增量的理论压力系数是必须使用的中间参数。 In equation (3) and theoretical pressure coefficient expression (4), there are many needs for retaining the expressions of specific potential energy increment and specific kinetic energy increment and partial pressure coefficient. There are two kinds of theoretical analysis, theoretical and actual potential kinetic energy production ratios. They are all used in the dependent analysis. Obviously, the composition of the two terms of the two expressions highlights the mechanical sources of the specific potential energy incremental partial pressure and the specific kinetic energy incremental partial pressure and their proportional relationship. Among them, the specific potential energy incremental pressure coefficient is composed of the algebraic sum of the centrifugal force work pressure coefficient 1-X ² and the potential energy consumption pressure coefficient decrement term K ² (l- μ ² ) for accelerating relative motion, and the specific kinetic energy increase in pressure by the remaining factor is the accelerating force function coefficient blade centrifugal pressure coefficient equal amount of work pressure a 1 x ^2, the kinetic energy of the rotating shaft so as to reduce power feedback pressure reduction coefficient term and a 2Κ increases due to relative motion acceleration Algebra and composition of the pressure coefficient incremental term K ² (l— μ ² ). — The existence of the terms κ ² (1-μ ² ) and κ ² (1- μ ² ) indicates that there is a process of converting potential energy to kinetic energy when the fluid flow at the tail of the channel is accelerated. Positive correlation and sharp negative correlation with μ, but they cancel each other out in the overall theoretical pressure coefficient without affecting. From the above analysis by J, it can be seen that the centrifugal force work pressure coefficient 1-X ² and the blade remaining acceleration force work pressure coefficient 1-X ² are both equal, which is a general law of centrifugal pump impeller specific work distribution and head generation. When no technological processing, the theoretical pressure coefficient of the impeller for a centrifugal pump ² (1- X 2), which is equal to a ratio of the theoretical potential movable. Obviously, two 1-X ² terms are also generated in the present invention. Under the action mechanism of the kinetic energy feedback technology, the impeller feeds back the specific kinetic energy with a normalization coefficient of 2K to the rotating shaft, and the theoretical pressure coefficient is reduced to 2 ( l-x ² -K), the theoretical momentum ratio is greatly increased. Because the potential and kinetic energy production have different actual conversion efficiencies, the actual pressure coefficients need to be calculated according to the hydraulic efficiency of the respective processes when accounting for losses. At this time, the theoretical pressure coefficients of specific potential energy increase and specific kinetic energy increase are An intermediate parameter that must be used.

认真分析理论压力系数的因变规律，就可以从理论上看清本发明的这种叶片结构方案在提高效率和改善运行特性上的优势，进而可以发现其比功输出控制上的巨大潜力，这种发现将成为设计可调节性离心泵和可自控性智能离心泵的理论基础。 By carefully analyzing the dependent law of the theoretical pressure coefficient, you can theoretically see the advantages of the blade structure scheme of the present invention in improving efficiency and improving operating characteristics, and then you can find its great potential in controlling specific power output. This discovery will become the theoretical basis for designing adjustable centrifugal pumps and self-controlling intelligent centrifugal pumps.

方程式（3) 表明，在本发明的理论压力系数的构成中，比势能增量压力系数占绝大部分，而比动能压力系数的数值是比较小的，并且，由于绝对速度的大幅度降低而使导流流程的水力效率大幅度提高，因而泵的实际压力系数非常接近于理论压力系数。基于这两方面的原因，在进行叶轮设计时，基本上可以用后者代替前者。如需精确计算，则可应用导流效率公式或者进一步地使用全程水力效率公式进行修正。高势比离心泵理论压力系数随 X和 Κ变动的情况列于表 4。高势比离心泵理论压力系数 Ψ =2(1— x²—K)变动情况表 Equation (3) shows that in the composition of the theoretical pressure coefficient of the present invention, the specific potential energy incremental pressure coefficient accounts for the majority, and the value of the specific kinetic energy pressure coefficient is relatively small, and due to the large decrease in absolute speed The hydraulic efficiency of the diversion process is greatly improved, so the actual pressure coefficient of the pump is very close to the theoretical pressure coefficient. Based on these two reasons, the latter can basically be used instead of the former when designing the impeller. If accurate calculation is needed, the diversion efficiency formula can be applied or further modified using the full-range hydraulic efficiency formula. The variation of the theoretical pressure coefficient of the high potential ratio centrifugal pump with X and K is shown in Table 4. Table of theoretical pressure coefficient of high potential ratio centrifugal pump (= 2 (1— x ² —K)

参照表 4，理论压力系数随着牵连速度系数 X的增加成平方关系地减小，随着反馈减功系数 Κ的增加而线性地减小。两者都是真小数，因而后者具有更髙的敏感性，它使高势比离心泵具有自适应调功的近似恒功率特性和良好的线性节流特性。 X是一个设计几何参数，受制于流量、入口流速和轴径，其值通常为 0.2〜0.3左右，对于理论压力系数的影响不大。 Referring to Table 4, the theoretical pressure coefficient decreases in a square relationship with the increase of the implication speed coefficient X, and decreases linearly with the increase of the feedback reduction coefficient K. Both are true decimals, so the latter has more 髙 sensitivity, which makes the high potential ratio centrifugal pump have approximately constant power characteristics and good linear throttling characteristics of adaptive power adjustment. X is a design geometric parameter, which is limited by the flow rate, inlet velocity and shaft diameter, and its value is usually about 0.2 ~ 0.3, which has little effect on the theoretical pressure coefficient.

具有本发明前述技术特征之叶轮的理论势动比为： The theoretical momentum ratio of the impeller having the foregoing technical features of the present invention is:

λ_τ=(1- χ²-Κ²(1-μ²))/(1 -χ²-2Κ+Κ²(1-μ²)) ' (5) 由于本发明叶轮流程段的水力效率很高，因而实际的输出势动比会非常接近理论势动比。两者的差别主要来自入口和加速段损耗的影响，入口损耗影响输出比势能，加速段损耗两者都影响，由于这类损耗已经降得很低，通常可以忽略。在 Κ、 μ、 X的实际取值范围内， λ_τ能够达到的数值范围约为 3〜9。其物理意义是，高势比叶轮生产的压力势能增量将为以液流绝对速度体现的动能增量的 3〜9倍。可见，本发明的高势比特性是十分显著的。 λ _τ = (1- χ ² -Κ ² (1-μ ² )) / (1 -χ ² -2Κ + Κ ² (1-μ ² )) '(5) Because the hydraulic efficiency of the impeller process section of the present invention is very High, so the actual output momentum ratio will be very close to the theoretical momentum ratio. The difference between the two is mainly due to the effects of the loss at the entrance and the acceleration stage. The entrance loss affects the specific potential energy of the output, and both of the acceleration stage losses are affected. Since such losses have been reduced very low, they can usually be ignored. Within the actual values of K, μ, and X, the range of values that λ _τ can reach is about 3 to 9. The physical meaning is that the pressure potential energy increase produced by the high potential ratio impeller will be 3 to 9 times the kinetic energy increase reflected by the absolute velocity of the liquid flow. It can be seen that the high potential ratio characteristic of the present invention is very significant.

比动能增量和比动能不是同一概念。当考察对象为叶轮时，诸如预旋器、入管液流的外源驱动速度等外界能量介入要求这两个概念区别使用。当考察对象为整个离心泵时，除存在外源驱动的入管速度以外，这两个概念可视为同一。另外，当关注导流负荷时，要求考察比动能增量，当关注导流损耗时，要求考察比动能。其实，两者的归一化系数差别只在高阶小量项 μ²Κ²，其数值显然是很小的，在一般的分析中完全可以忽略不计。 Specific kinetic energy increase and specific kinetic energy are not the same concept. When the object under investigation is an impeller, the intervention of external energy such as the pre-spinner and the external driving speed of the inlet flow requires the two concepts to be used differently. When the object to be investigated is the entire centrifugal pump, the two concepts can be regarded as the same except that there is an externally driven pipe inlet speed. In addition, when the diversion load is concerned, it is required to examine the specific kinetic energy increase, and when the diversion loss is concerned, the specific kinetic energy is required to be examined. In fact, the difference between the normalization coefficients of the two is only in the high-order small-quantity term μ ² κ ² , and its value is obviously very small, which can be ignored in general analysis.

当取典型参数 μ²=0.1时，比动能压力系数 Ψ₂，=(1—Κ)²，比势能增量压力系数 Ψ₁=(l— x²—0.9K²)，比动能增量压力系数 Ψ₂=(1— x²—2K + 0.9K²)，势动比 λ τ ι^/ ι^, 它们的变动情况列于表 5。表 5 比动能压力系数、比势能增量压力系数、比动能增量压力系数和势动比变动表 When taking the typical parameter μ ² = 0.1, the specific kinetic energy pressure coefficient Ψ ₂ , = (1—Κ) ² , the specific potential energy incremental pressure coefficient Ψ ₁ = (l— x ² —0.9K ² ), the specific kinetic energy incremental pressure The coefficient Ψ ₂ = (1— x ² —2K + 0.9K ² ), the potential ratio λ τ ι ^ / ι ^, and their changes are listed in Table 5. Table 5 Specific kinetic energy pressure coefficient, specific potential energy incremental pressure coefficient, specific kinetic energy incremental pressure coefficient, and potential-to-kinetic ratio change table

从表 5中可以.看到，两个分压力系数均随着 X和 Κ的增大而减小，但变化率有明显的差异，这种差异导致势动比随着 X和 κ的增大而增大，随 X增大的变化较为缓慢，随 κ增大的变化却非常敏感，这正是实际设计所需要的。 Κ作为与 X²等价的调节量显然应该具有较高的灵敏度，并且， Κ也不同于作为几何参数受结构制约的 X，可以享有比较大的设置独立性和灵活性。 Κ的取值范围通常在 0.5左右比较适宜。 From Table 5, it can be seen that the two partial pressure coefficients decrease with the increase of X and κ, but there is a significant difference in the rate of change. This difference causes the momentum ratio to increase with X and κ. While increasing, the change with X increases slowly, but the change with κ increases is very sensitive, which is exactly what the actual design needs. It is obvious that κ as an adjustment amount equivalent to X ² should have high sensitivity, and κ is also different from X, whose geometric parameters are structurally restricted, and can enjoy relatively large setting independence and flexibility. The range of K is usually about 0.5.

在理论压力系数 Ψ=2(1— X²— Κ)、比势能增量压力系数¾^ = 1— x²—K²(l— μ²)和比动能增量压力系数 Ψ₂=1― χ²-2Κ+Κ²(1-μ ²)中， ( 1_ X²)作为离心力功或叶片剩余加速力功压力系数项，它们分别是两个分压力系数的唯一或第一源泉，其大小变动如表 6。 The theoretical pressure coefficient Ψ = 2 (1—X ² — Κ), the specific potential energy incremental pressure coefficient ¾ ^ = 1— x ² —K ² (l— μ ² ), and the specific kinetic energy incremental pressure coefficient Ψ ₂ = 1― In χ ² -2Κ + Κ ² (1-μ ² ), (1_ X ² ) is used as the centrifugal force work or the remaining acceleration force work pressure coefficient term. They are the sole or first source of the two partial pressure coefficients, respectively. Changes are shown in Table 6.

离心力功压力系数和剩余加速力功压力系数等量变动表 Centrifugal force work pressure coefficient and residual acceleration work pressure coefficient

作为比势能增量压力系数的唯一源泉，表 6给出的离心力功压力系数显然是该系数的上限。作为比动能增量压力系数的第一源泉，表 6给出的剩余加速力功压力系数构成该系数的主要正值部分，在 X和 K较小时尤其如此。综合起来考虑，如前所述，表 6所给出的两个压力系数是离心泵的理论压力系数的两个等量的赋能源泉，它们的和决定了泵的理论压力系数的上限。当有典型参数 x =0.2〜0.3左右时，这个上限为 1.92〜1.82左右。考虑到现有技术的设计压力系数通常在 1.0左右。因此，采用同样轮径和同样转速的本发明之叶轮，要达到同样的设计压力系数时，也具有 0.92〜0.82左右的压力系数空间用于设置反馈减速比 K和规划大为减小了的压力系数损失。这时的势动比大约可以达到 3〜5，已经基本上满足需要了。如果需要进一步增大势动比，则可以适当降低压力系数设计值，以增加转速或适当加大轮径的办法来达到设计扬程。由于前者的轮盘摩擦损耗的相关幂次较低，通常应该优先釆用前者。但釆用本发明后述的内减摩技术特征以后，轮盘摩擦损耗将成为无需特别顾忌的问题，这时，大胆地降低压力系数和提高势动比，可以获得更髙的水力效率和总效率。综上所述，本发明对现有技术离心泵之叶轮进行了较为彻底的改进，主要技术特征包括：As the only source of the specific potential energy incremental pressure coefficient, the pressure coefficient of centrifugal force given in Table 6 is obviously the coefficient Ceiling. As the first source of the specific kinetic energy incremental pressure coefficient, the residual acceleration work pressure coefficient given in Table 6 constitutes the main positive part of this coefficient, especially when X and K are small. Taken together, as mentioned above, the two pressure coefficients given in Table 6 are two equal energy energizing springs of the theoretical pressure coefficient of the centrifugal pump, and their sum determines the upper limit of the theoretical pressure coefficient of the pump. When there are typical parameters x = about 0.2 to 0.3, this upper limit is about 1.92 to 1.82. Considering that the design pressure coefficient of the prior art is usually around 1.0. Therefore, when the impeller of the present invention with the same wheel diameter and the same speed is required to achieve the same design pressure coefficient, it also has a pressure coefficient space of about 0.92 to 0.82 for setting the feedback reduction ratio K and the greatly reduced pressure. Coefficient loss. At this time, the momentum ratio can reach about 3 ~ 5, which has basically met the needs. If it is necessary to further increase the potential-to-dynamic ratio, the design value of the pressure coefficient can be appropriately reduced, and the design lift can be achieved by increasing the rotational speed or appropriately increasing the wheel diameter. Since the power of the former's friction loss is relatively low, the former should usually be used first. However, after applying the internal friction reduction technical features described later in the present invention, the friction loss of the disk will become a problem that does not require special consideration. At this time, boldly reducing the pressure coefficient and increasing the potential-to-dynamic ratio can obtain even greater hydraulic efficiency and total power. effectiveness. In summary, the present invention makes a relatively thorough improvement on the impeller of the prior art centrifugal pump. The main technical features include:

1 ) 、叶轮流道釆用相离分布之反切向小出口，产生动能反馈减速机制，抗性提高势动比； 1) The impeller flow channel 釆 uses the inverse tangential small exit of the separated distribution to generate a kinetic energy feedback deceleration mechanism to increase the resistance to the potential-to-dynamic ratio;

2) 、釆用 L形叶片，其前端为径向叶槽，截面积大而包角小，流速低而流程短，其尾部产生轮沿约束作用，完全消除回流和脱流现象； 2) Use L-shaped blades, whose front end is a radial groove, with a large cross-sectional area and a small wrap angle, a low flow rate and a short flow, and a tail restraint effect at the tail to completely eliminate the phenomenon of backflow and outflow;

3 ) 、叶槽中设置均速岔道抗性消除叶槽相对涡旋，使叶槽流道速度场均匀分布，消除了湍流、尾缘涡等不稳定现象以及压力面与吸力面之间的湍阻性压差。 3) The uniform speed bifurcation resistance is set in the blade groove to eliminate the relative vortex of the blade groove, so that the velocity field of the blade groove flow channel is evenly distributed, and the unstable phenomena such as turbulence, trailing edge vortex, and the turbulence between the pressure surface and the suction surface Resistive pressure difference.

这些改进措施可以实现下列功能或性能特征： These improvements can achieve the following functional or performance characteristics:

1 ) 、降低入导速度，减小导流损耗，基本消除叶轮损耗，大幅度提高全程水力效率； 1) Reduce the inlet speed, reduce the flow loss, basically eliminate the impeller loss, and greatly improve the hydraulic efficiency of the whole process;

2) 、具备变工况运行的适应性，小流量运行的水力效率不是下降而是提髙； 2) With the adaptability for variable operating conditions, the hydraulic efficiency of small flow operation is not reduced but improved;

3 ) 、增大叶轮之理论比功和理论扬程，使之接近于无限叶片数欧拉方程规律； 3) Increase the theoretical specific work and theoretical head of the impeller to make it closer to the law of Euler's equation of infinite blade number;

4) 、使叶轮流程和导流流程的压力系数损失减到很小，使实际扬程接近于理论扬程；4), reduce the pressure coefficient loss of the impeller process and the diversion process to a small, so that the actual head is close to the theoretical head;

5)、在基本方程中***可灵活设定的反馈减功系数 K，使理论扬程、实际扬程和水力效率皆随反馈减功系数 Κ单调锐变化，从而奠定了可调节性和可自控性离心泵的技术基础。本发明对于造成离心泵内机械效率主要损失的轮盘摩擦损耗问题和大而不稳定的轴向推力问题也给予了重点的关注，设计了达到第二个发明目的技术方案：将闭式叶轮轮盘之两侧端腔或半开式叶轮的后盖侧端腔置于气体循环或气液二相流循环流程中，端腔充盈不溶性气体，叶轮轮盘在气相介质中旋转，其摩擦损耗很小，端腔气体的压力在循环中动态地保持与端腔边沿旋转液流表面压力的平衡，并且等于或者小于叶轮输出静压力，当前后端腔均充气时，两者的比压相等或相近，气体对叶轮施加的轴向力等于气体压力与叶轮端面面积的乘积，与泄漏间隙的大小和泄漏流量无关。 5) Insert flexible feedback reduction coefficient K into the basic equation, so that the theoretical lift, actual lift and hydraulic efficiency all monotonously change with the feedback reduction coefficient K, thereby establishing the adjustable and self-controlling centrifugation. Technical basis of the pump. The present invention also pays great attention to the problem of disc friction loss and large and unstable axial thrust that cause the main loss of mechanical efficiency in the centrifugal pump. A technical solution to achieve the second purpose of the invention is designed: a closed impeller The end cavities on both sides of the disc or the rear cover side end cavities of the semi-open impeller are placed in the gas circulation or gas-liquid two-phase flow circulation process. The end cavity is filled with insoluble gas. The impeller disc rotates in the gas phase medium, and its friction loss is very high. The pressure of the end cavity gas is dynamically maintained in the circulation in equilibrium with the pressure of the surface of the rotating liquid flow along the edge of the end cavity, and is equal to or less than the static pressure of the impeller output. When the front end cavity is inflated, the specific pressure of the two is equal or similar. The axial force exerted by the gas on the impeller is equal to the gas pressure and the impeller The product of the end face area is independent of the size of the leakage gap and the leakage flow.

轮盘摩擦是一种与扬程和流量无直接关联的固定性损耗，其大小与叶轮直径的 5次方成正比，与转速的 3次方成正比，所造成的效率损失不容忽视。对于低比转数、髙扬程、以及偏离设计工况小流量运行等情况，轮盘摩擦的相对影响尤其严重。数值分析表明，该种损耗是造成低比转数离心泵特别是转速较低而叶轮较大的高扬程离心泵的设计效率较低的主要原因之一。另外，该种损耗也是造成离心泵偏离设计工况小流量运行时效率严重下降的决定性原因，因为，水力效率下降对总效率的影响还有一个由势动比决定的渐近下限，而轮盘摩擦损耗与有效轴功之比则可以倒过来大于 1甚至远大于 1而没有限制。 Disk friction is a fixed loss that is not directly related to head and flow. Its magnitude is proportional to the 5th power of the impeller diameter and proportional to the 3rd power of the speed. The loss of efficiency caused by it cannot be ignored. The relative impact of wheel friction is particularly serious for low specific speeds, head lift, and small flow operations that deviate from design conditions. Numerical analysis shows that this loss is one of the main reasons for the low design efficiency of low-specific-speed centrifugal pumps, especially high-lift centrifugal pumps with lower speeds and larger impellers. In addition, this kind of loss is also the decisive reason for the serious decrease in efficiency when the centrifugal pump deviates from the design condition at low flow rate operation, because the impact of the decrease in hydraulic efficiency on the overall efficiency has an asymptotic lower limit determined by the momentum ratio, and the wheel disk The ratio of friction loss to effective shaft work can be reversed to greater than 1 or even greater than 1 without restriction.

就轴向推力问题而言，传统叶轮形成压力侧轴向推力的机制主要是由于输出压力对两侧端腔的作用不均衡，而吸入侧液流动量改变的反作用力的补偿作用则相对太小，并且随流量变化而变化。造成端腔压力差别的原因是，吸入侧端腔的平均比压较压力侧低而其面积又较小。两侧比压差别是由间隙宽度差别、泄漏流方向及其携带动量矩的不同所造成的角速度差别以及离心力场的尺度差别等因素引起的。除面积及泄漏流方向外，这些因素都是非定常的，并且变化比例较大。因此，传统叶轮会产生数值很大且非平稳的轴向推力，这种推力会导致轴承损耗增加和效率下降，甚至还可能产生机械故障。轴向力平衡问题增加了离心泵设计和制造的难度。专门设计的平衡盘装置增加了结构复杂性和轴系精度要求，因而增加了泵的成本，并且平衡盘的分流作用会导致容积效率和总效率下降。 As far as the axial thrust is concerned, the mechanism of the traditional axial impeller forming the thrust on the pressure side is mainly due to the uneven effect of the output pressure on the end cavities on both sides, while the compensation of the reaction force for the change in the fluid flow on the suction side is relatively small. , And changes with flow. The reason for the difference in end-cavity pressure is that the average specific pressure of the end-cavity on the suction side is lower than the pressure side and its area is smaller. The specific pressure difference on both sides is caused by factors such as the difference in gap width, the direction of the leakage flow and the difference in the momentum moment carried by it, and the difference in the size of the centrifugal force field. Except for the area and the direction of the leakage flow, these factors are unsteady and have a large proportion of change. Therefore, the traditional impeller will generate a large amount of non-smooth axial thrust. This thrust will lead to increased bearing losses and reduced efficiency, and may even cause mechanical failure. Axial force balance issues increase the difficulty of designing and manufacturing centrifugal pumps. The specially designed balance plate device increases the complexity of the structure and the requirements of the shafting accuracy, thus increasing the cost of the pump, and the shunting effect of the balance plate will cause the volumetric efficiency and the total efficiency to decrease.

本发明的内减摩方案的作用是双重的——既能消除绝大部分的轮盘摩擦损耗，提高泵的内机械效率，同时又能减小和稳定轴向推力。其减摩原理容易理解，由于气体的粘滞系数较之液体小两个数量级，因而轮盘端面与气体摩擦时，其摩擦损耗也相应减小两个数量级。但在实际应用中，由于充气端腔的气液分界面（液位）存在随机扰动，在扰动波的波谷处会发生气泡逃逸现象，因而气体不可能完全充满整个端腔。在端腔外沿存在环形液相区的情况下，轮盘摩擦损耗将难于真正地减小两个数量级。有基于此，本发明用充气时存在残余环形液相区的轮盘摩擦损耗与不充气时轮盘摩擦损耗之比（简称摩擦损耗比）来描述减摩效果，忽略充气区的气相摩擦，该比值由（6) 式给出。 The effect of the internal friction reduction scheme of the present invention is twofold-it can eliminate most of the friction loss of the disk, improve the internal mechanical efficiency of the pump, and at the same time reduce and stabilize the axial thrust. The principle of friction reduction is easy to understand. Because the viscous coefficient of gas is two orders of magnitude smaller than that of liquid, the friction loss of the disc end face when it rubs against the gas also reduces the friction loss by two orders of magnitude. However, in practical applications, due to the random perturbation of the gas-liquid interface (liquid level) of the gas-filled end cavity, the bubble escape phenomenon will occur at the trough of the perturbed wave, so the gas cannot completely fill the entire end cavity. In the presence of a ring-shaped liquid phase zone along the outer edge of the end cavity, it will be difficult to reduce the disc friction loss by two orders of magnitude. Based on this, in the present invention, the ratio of the friction loss of the disc with a residual annular liquid phase region when inflated to the friction loss of the disc when not inflated (abbreviated as friction loss ratio) is used to describe the friction reduction effect, and the gas phase friction in the inflation region is ignored. The ratio is given by (6).

Z 1 /Z₂ ⁵ (6)

Z 1 / Z ₂ ⁵ (6)

摩擦损耗比 Zi/Z₂是端腔充气直径比（山/(1₂)的函数，前者是有扰动时对减摩效果的测度，后者是有扰动时对充气效果的直接测度，按（6) 式计算的摩擦损耗比数值见表 7。端腔不完全充气时轮盘摩擦损耗比数据表充气直径比 /cb 0.90 0.92 0.94 0.95 0.96 0.97 0.98 0.99 摩擦损耗比 Zi/Z₂ 0.41 0.34 0.27 0.23 0.18 0.14 0.10 0.05 从表 7中可以看出，当充气直径比达到 96%以上时，轮盘摩擦损耗比将减少到 18 % 以下，当充气直径比达到 99%时，轮盘摩擦损耗比将减少为 5 %。可以看出，实际的减摩效果是摩擦损耗减小一个数量级，而不是两个数量级。下面具体分析本发明的内减摩设计所降低的损耗与离心泵效率指标之间的数量关系。包含经典概念的离心泵效率公式如（7) 式。， The friction loss ratio Zi / Z ₂ is a function of the end-cavity inflation diameter ratio (Mountain / (1 ₂ ), the former is a measure of the friction reduction effect when there is a disturbance, and the latter is a direct measure of the inflation effect when there is a disturbance. 6) The friction loss ratio calculated by the formula is shown in Table 7. Data of the friction loss ratio of the wheel and disc when the end cavity is not fully inflated / cb 0.90 0.92 0.94 0.95 0.96 0.97 0.98 0.99 Friction loss ratio Zi / Z ₂ 0.41 0.34 0.27 0.23 0.18 0.14 0.10 0.05 It can be seen from Table 7 that when the inflation diameter ratio reaches 96% or more, the wheel friction loss ratio will be reduced to less than 18%, and when the inflation diameter ratio reaches 99%, the wheel friction loss ratio will be reduced to 5%. It can be seen that the actual friction reduction effect is that the friction loss is reduced by an order of magnitude instead of two orders of magnitude. The following specifically analyzes the quantitative relationship between the loss reduced by the internal friction reduction design of the present invention and the efficiency index of the centrifugal pump. The efficiency formula of the centrifugal pump containing the classic concept is shown in (7). ,

n = _m i= n_mn_hn_v ( Ι -Ρ_Γ ΡΪ ) (7) 式中 n、 n_h、 η_ν分别为总效率、水力效率和容积效率，（1— p_r /Pi) 为内机械效率， ri

二 n _h n_v ( i-Pr/Pi )为内效率， Ρ、 Ρ_γ 分别为轴功率、内机械损耗功率和内功率。本发明的内减摩方案使轮盘摩擦损耗降低一个数量级，因而内机械损耗功率 Pj>也等比例地降低为（z z^ P 并使内功率也变为一n = _m i = n _m n _h n _v (Ι -Ρ _Γ ΡΪ) (7) where n, n _h and η _ν are total efficiency, hydraulic efficiency and volumetric efficiency, respectively, (1-p _r / Pi) is Internal mechanical efficiency, ri

Two n _h n _v (i-Pr / Pi) are internal efficiency, and P and P _γ are respectively shaft power, internal mechanical loss power, and internal power. The internal friction reduction scheme of the present invention reduces the friction loss of the disc by an order of magnitude, so the internal mechanical loss power Pj> is also reduced to (zz ^ P) in proportion to the internal power.

(Ζ!/Ζ₂ ) Ρ_Γ, 内机械效率、内效率及总效率因而都有相应幅度的提高。 (Z! / Z ₂ ) ρ _Γ , the internal mechanical efficiency, internal efficiency, and overall efficiency have correspondingly improved.

在外机械效率、水力效率和容积效率未知并假设它们都保持不变的前提下，经过稍繁的推导和计算，可得在假定运行条件下的内减摩技术之效率增益数据如表 8、表 9。由于轮盘摩擦损耗造成的效率损失有较大差别，因而必须分别讨论和计算。表 8和表 9分别给出了小型或低比转数离心泵和大型离心泵内减摩后的效率提高数据。 Under the premise that the external mechanical efficiency, hydraulic efficiency, and volumetric efficiency are unknown and it is assumed that they remain unchanged, after a little more derivation and calculation, the efficiency gain data of the internal friction reduction technology under the assumed operating conditions can be obtained as shown in Table 8. 9. Because the efficiency loss caused by disc friction loss is quite different, it must be discussed and calculated separately. Tables 8 and 9 show the efficiency improvement data of friction reduction in small or low specific speed centrifugal pumps and large centrifugal pumps, respectively.

小型、低比转数离心泵内减摩后效率提高数据表 Data sheet for efficiency improvement after friction reduction in small, low specific speed centrifugal pumps

参照表 8，表中第 1行和第 2行假设减摩条件，在几种效率可能性下轮盘摩擦导致 10 %的标称效率下降。后 4行表示摩擦损耗比为 0.18和 0.10时的减摩增效数据。在现有技术中，小型、低比转数离心泵的轮盘摩擦损耗相对严重，可能造成 10%左右的标称效率下降，小流量运行时，效率下降的幅度可能达到 20%以上。釆用内减摩方案后，设这类泵的充气直径比能达到 96%〜98%，依据表 7，其轮盘摩擦损耗比将在 0.18〜0.1之间。如表 8 所示，其标称效率将提高 8〜9%，效率高时增幅大，效率低时增幅略微减小。大中型离心泵内减摩后效率提高数据表无轮盘摩擦时总效率 90% 80% 70% 60% 50% 有轮盘摩擦，总效率降 6% 84% 74% 64% 54% 44% 减摩 90% 总效率 ' 89.4% 79.4% 69.3 % 59.3 % 49.3 % Referring to Table 8, the first and second rows in the table assume friction reduction conditions. Under several efficiency possibilities, wheel friction causes a 10% reduction in nominal efficiency. The last 4 rows show the friction reduction efficiency data when the friction loss ratio is 0.18 and 0.10. In the prior art, the friction loss of the disk of a small, low specific speed centrifugal pump is relatively serious, which may cause a nominal efficiency drop of about 10%. When running at a low flow rate, the efficiency drop may reach more than 20%. (4) After using the internal friction reduction scheme, the pump's inflation diameter ratio can reach 96% ~ 98%. According to Table 7, its wheel friction loss ratio will be between 0.18 ~ 0.1. As shown in Table 8, its nominal efficiency will increase by 8-9%. When the efficiency is high, the increase will be large, and when the efficiency is low, the increase will be slightly reduced. Efficiency increase after reducing friction in large and medium-sized centrifugal pumps Data sheet Total efficiency without wheel friction 90% 80% 70% 60% 50% With wheel friction, total efficiency decreased by 6% 84% 74% 64% 54% 44% Reduce friction by 90% Total efficiency '89.4% 79.4% 69.3% 59.3% 49.3%

总效率增量 +5.4% + 5.4% + 5.3 % +5.3 % +5.3 % 总效率 89.7% 79.7% 69.7% 59.7% 49.7% 减摩 95% Total efficiency increase + 5.4% + 5.4% + 5.3% +5.3% +5.3% Total efficiency 89.7% 79.7% 69.7% 59.7% 49.7% Friction reduction 95%

总效率增量 + 5.7% + 5.7% +5.7% +5.7% +5.7% 参照表 9，表中第 1行和第 2行假设减摩条件，在几种效率可能性下轮盘摩擦导致 6 %的标称效率下降。后 4行表示摩擦损耗比为 0.10和 0.05时的减摩增效数据。在现有技术中，大中型离心泵的轮盘摩擦损耗数值很大，但造成的效率损失一般能控制在 6%或以下。小流量运行时，效率下降的幅度会超过该值。采用内减摩方案后，设这类泵的充气直径比能达到 98 %〜99%，依据表 7，其轮盘摩擦损耗比将在 0.10〜0.05之间。如表 9所示，其标称效率将提高 5.3 %〜5.7%，增幅与效率正相关，但差别很小。内减摩技术在平衡和稳定轴向力方面也具有明显的优越性。对于闭式叶轮之两侧内减摩方案，由于气相离心力场的压力差别极小，因而两侧端腔可以认为具有相同的比压，其压力差别只在承压面积的大小。考虑到叶轮入口直径通常为叶轮直径的 1/3左右，扣除转轴截面积，泵的吸入侧端腔的承压面积将只比压力侧小 5 %〜9%，加上吸入侧承受的液流转向动反力的补偿作用，在正常运转时，叶轮两侧所受的轴向力之差将可能下降到施压侧压力的 2〜5 %的水平。并且，这种压力差将只随流量的改变而略有改变，没有其他不确定因素的扰动影响，因而容易平衡和控制。对于半开式叶轮，其压力侧内减摩后，产生的轴向推力将不再受间隙泄漏流的影响而趋于恒定，虽然吸入侧的相关变动因素仍然较多，其平衡效果要差一些，但轴向力的稳定性将明显优于不充气的叶轮。内减摩方法及其装置是本发明全面提升离心泵效率的发明设计的重要组成部分，既可组合其他发明特征一道使用，又可单独实施，因而具有独立发明的属性。 Total efficiency increase + 5.7% + 5.7% + 5.7% + 5.7% + 5.7% Referring to Table 9, the first and second rows in the table assume friction reduction conditions, and the disk friction causes 6% under several efficiency possibilities The nominal efficiency is reduced. The last 4 rows show the friction reduction efficiency data when the friction loss ratio is 0.10 and 0.05. In the prior art, the friction loss of the discs of large and medium-sized centrifugal pumps is very large, but the efficiency loss caused can generally be controlled at 6% or less. When running at low flow rates, the efficiency drop will exceed this value. After the internal friction reduction scheme is adopted, the inflation diameter ratio of such pumps can reach 98% ~ 99%. According to Table 7, the friction loss ratio of the disk will be between 0.10 ~ 0.05. As shown in Table 9, its nominal efficiency will increase by 5.3% to 5.7%, and the increase is positively related to efficiency, but the difference is small. Internal friction reduction technology also has obvious advantages in balancing and stabilizing axial forces. For the internal friction reduction scheme on both sides of the closed impeller, the pressure difference in the gas-phase centrifugal force field is extremely small, so the end cavities on both sides can be considered to have the same specific pressure, and the pressure difference is only in the area of the pressure bearing area. Considering that the impeller inlet diameter is usually about 1/3 of the impeller diameter, excluding the shaft cross-sectional area, the pressure-bearing area of the end cavity on the suction side of the pump will be only 5% to 9% smaller than the pressure side, plus the fluid flow on the suction side. The compensation of the steering dynamic reaction force, during normal operation, the difference between the axial forces on both sides of the impeller may drop to a level of 2 to 5% of the pressure on the pressure side. In addition, this pressure difference will only slightly change with the change of the flow rate, without the disturbance of other uncertain factors, so it is easy to balance and control. For a semi-open impeller, the axial thrust generated by reducing friction in the pressure side will no longer be affected by the gap leakage flow and will become constant. Although there are still many related changes on the suction side, the balance effect is worse. However, the stability of the axial force will be significantly better than the non-aerated impeller. The internal friction reduction method and its device are important components of the invention design for comprehensively improving the efficiency of the centrifugal pump in the present invention, which can be used in combination with other invention features or can be implemented separately, so it has the property of an independent invention.

将这种设计应用于现有技术离心泵时，相当于首先攻克制约效率的第三大瓶颈，如表 8、表 9所示，能有 5〜9个百分点的效率提髙，这已经是很可观的效益，而实施成本却很低。由于现有技术离心泵没有这种结构规划，其中许多端腔是开放的大开口，这就难以充气和保持气包的稳定。只有在端腔开口缩小到成为一个小的间隙时，现有技术离心泵才能方便地安装充气装置，本发明的实施例说明中将提供这种设计。将内减摩技术应用于高势比离心泵时，由于制约效率的第一大瓶颈导流损耗和第二大瓶颈叶轮损耗问题均已解决，离心泵的水力效率和总效率基础已经大幅度提高。轮盘摩擦损耗问题因而成为制约效率的主要因素而上升为第大瓶颈，这时釆用充气减摩技术，其效率提高的幅度还略有增加。 When this design is applied to the centrifugal pump of the prior art, it is equivalent to first overcome the third major bottleneck that restricts efficiency. As shown in Tables 8 and 9, it can improve the efficiency by 5-9 percentage points. Considerable benefits, but implementation costs are low. Since the prior art centrifugal pumps do not have such a structural plan, many of the end cavities are large open openings, which makes it difficult to inflate and maintain the stability of the airbag. Only when the opening of the end cavity is reduced to a small gap can the prior art centrifugal pump be conveniently installed with an inflation device, which will be provided in the description of the embodiment of the present invention. When internal friction reduction technology is applied to centrifugal pumps with high potential ratios, the problems of the first major bottleneck diversion loss and the second largest bottleneck impeller loss that have limited efficiency have been resolved, and the hydraulic efficiency and total efficiency basis of centrifugal pumps have been greatly improved. . As a result, the problem of wheel friction loss has become the main factor restricting efficiency and has risen to become the largest bottleneck. At this time, the use of inflatable friction reduction technology, the efficiency improvement has increased slightly.

本发明内减摩的具体设计包括气体种类选择、端腔压力降低和充气直径比增大方法、循环驱动及流量调节的解决方案。气体种类的挑选应该满足与被泵送液体不发生有害理化反应和容易获得的要求，例如当被泵送液^:是水时，使用空气就是最简单的选择，现有技术就已经有使用空气来调节比功或者改善启动和停车过渡特性的应用先例。端腔压力和液位扰动幅度当然是越低越好，它们与叶轮出口静压力、出口流速及其出口部位的几何设计相关，也与端腔间隙有关，应该通过专门试验来优化设计，本发明将提供与之相关的一种具体方案。至于循环驱动方式，则应根据端腔压力、气源压力以及成本等经济因素来综合考虑，可以在压力气瓶、气泵、气液二相流泵等方案中选择。虽然气体循环是必要的，但循环流量并没有严格的数量要求，可在实施实践中以不影响减摩效果为前提调整到最小值。压力液体的循环也是必要的，这是冷却轴封和产生泄漏间隙压差的需要，或者还可能是驱动二相流的能源，循环流量应该依据所有这些需要中之最大流量来确定。实际上，就内减摩的循环驱动及其流量控制而言，存在着许多可用的方案供选择。本发明内减摩的一个具体方案是：包括给减摩端腔充气的射流器，射流器的驱动压力液体由泵之出口分流，其引射口通过调节阀接气源或通大气，其出口输出压力略高于端腔的气液二相流，从静止壁面近轴处接入减摩端腔，二相流在腔中分离，气体被离心力场之向心浮力约束于腔中，液体和多余的气体从轮沿侧隙中排入导流器。前端腔减摩时，通吸入室的间隙改成防止气体逃逸的阻气间隙，通过在入口加装分离分流二相流的阻气 V形环槽、或者加装二相流封浸润滑的有机材料挡圈、或者另接压力液体直接封堵间隙实现。轮盘端面或者还作过粗糙化处理以提高介质圆周速度，叶轮出口处的腔壁母线或者还设计成具有引射减压作用的形状，以使出口液流产生射流作用将端腔压力降到出口静压力以下，实时调整驱动液流流量和被引射气体流量，端腔气液分界面将稳定在轮沿附近。 The specific design of the internal friction reduction of the present invention includes a solution for selecting a gas type, reducing a pressure in an end cavity, and increasing an inflation diameter ratio, a circulation drive, and a flow rate adjustment. The selection of the gas type should meet the requirements of no harmful physical and chemical reactions with the pumped liquid and easy availability. For example, when the pumped liquid is water, using air is the simplest choice. There are already precedents for applications that use air to regulate specific work or to improve start and stop transition characteristics. End-cavity pressure and liquid level perturbations are of course as low as possible. They are related to the static design of the impeller outlet, the outlet flow velocity, and the geometric design of the exit part. They are also related to the end-cavity clearance. The design should be optimized through special experiments. The present invention A specific scenario related to this will be provided. As for the cycle driving method, it should be comprehensively considered according to economic factors such as end-cavity pressure, gas source pressure, and cost. It can be selected from the schemes of pressure gas cylinders, gas pumps, and gas-liquid two-phase flow pumps. Although gas circulation is necessary, there is no strict quantity requirement for the circulating flow rate, and it can be adjusted to the minimum value in the premise of not affecting the friction reduction effect. The circulation of pressurized liquid is also necessary. This is the need to cool the shaft seal and create a pressure difference between the leakage gaps, or it may be the energy source driving the two-phase flow. The circulation flow rate should be determined based on the maximum flow rate of all these needs. In fact, in terms of cyclic drive for internal friction reduction and its flow control, there are many options available. A specific solution for reducing friction in the present invention is as follows: a jet device for inflating the friction reducing end cavity is included, and the driving pressure liquid of the jet device is divided by the outlet of the pump; its injection port is connected to the air source or the atmosphere through a regulating valve; The output pressure is slightly higher than that of the end-cavity gas-liquid two-phase flow, which is connected to the anti-friction end-cavity from the stationary wall near the axis. The two-phase flow is separated in the cavity. The gas is confined in the cavity by the centripetal buoyancy of the centrifugal force field. Excess gas is expelled from the wheel gap into the deflector. When reducing the friction in the front cavity, the gap through the suction chamber is changed to a gas-blocking gap to prevent gas from escaping, and a gas-blocking V-ring groove that separates and splits the two-phase flow is installed at the inlet, or a two-phase flow is sealed and lubricated organically. A material retaining ring or another pressure liquid is used to directly seal the gap. The end face of the disc is either roughened to increase the peripheral speed of the medium. The cavity wall generatrix at the exit of the impeller is also designed to have an ejection decompression effect, so that the ejection effect of the outlet liquid flow reduces the end cavity pressure to Below the outlet static pressure, the driving liquid flow rate and the induced gas flow rate are adjusted in real time, and the end-cavity gas-liquid interface will stabilize near the wheel edge.

射流器依靠动量交换原理工作，虽然本身的效率不髙但成本很低，体积很小，已经广泛应用于小流量流体的变压操作。由于压力液体及其前后流程都是现成于主设备，因而用射流器来驱动气体实现离心泵的内减摩是一种恰到好处的设计。实践表明，当驱动液流压力比目标压力高 0.05MPa以上时，射流器就有足够的引射动能而产生明显的引射增压作用。检验射流效果并影响效率的参数是工作压头比 ε，该参数决定于（8 ) 式。 The ejector works on the principle of momentum exchange. Although its efficiency is not bad, its cost is very low and its volume is very small. It has been widely used in pressure-transforming operations of small flow fluids. Since the pressure liquid and its front and back processes are all ready-made in the main equipment, it is a perfect design to use a jet to drive the gas to achieve the internal friction reduction of the centrifugal pump. Practice has shown that when the pressure of the driving liquid flow is higher than the target pressure by more than 0.05 MPa, the ejector has sufficient ejection kinetic energy to produce a significant ejection boosting effect. The parameter that tests the jet effect and affects the efficiency is the working head ratio ε, which is determined by the formula (8).

ε = (Ρ₄-Ρ₂) / (Ρ!-Ρ₂) ( 8 ) 式中 Pi、 P₂、 P₄分别是输入流体压力、引射流体压力和输出压力，按照所述的连接方案则分别为离心泵出口压力、气源压力和目标端腔压力。射流器的特性是：工作压头比越低，所需压力液体的流量就越小。由（8 ) 式可知，降低 P₄和在 Pi的限度内提高？₂都是减小射流器压头比的措施，其中考虑和包括了（P₄— P₂) 为负值的情况。因此，降低 P₄和在 Pi的限度内提高 P₂都能减小压力液体的流量。 ε = (P ₄ -P ₂ ) / (Ρ! -P ₂ ) (8) where Pi, P ₂ , and P ₄ are the input fluid pressure, the ejection fluid pressure, and the output pressure, respectively. According to the connection scheme, They are the outlet pressure of the centrifugal pump, the pressure of the air source and the pressure of the target end cavity. The characteristics of the ejector are: The lower the working head ratio, the smaller the required fluid flow rate. From the formula (8), it can be seen that reducing P ₄ and increasing within the limits of Pi? ₂ are measures to reduce the head ratio of the ejector, which considers and includes the case where (P ₄ -P ₂ ) is negative. Therefore, both reducing P ₄ and increasing P ₂ within the limits of Pi can reduce the flow of pressurized liquid.

将叶轮出口处腔壁母线设计成具有引射减压作用的形状时，叶轮及其容纳腔体就成了一个大的静压调控射流器，其引射作用能将减摩端腔压力 P₄降低到叶轮出口静压力以下，从而起到帮助射流器降低目标压力的作用，这是不消耗功率的静压调节。如果要在单级泵及多级泵的末级实施所述方案，利用叶轮的射流效应降低压头比是降低端腔压力和减小反馈压力液体流量的重要措施。降低端腔压力还有另一个重要的作用，那就是减小轴向推力，因为该推力是与端腔压力成正比的。 When the cavity wall busbar at the exit of the impeller is designed to have the effect of ejecting decompression, the impeller and its containing cavity become a large static pressure regulating ejector, and its ejecting effect can reduce the pressure at the frictional end cavity P ₄ Reduced to below the impeller outlet static pressure, so as to help the ejector reduce the target pressure. This is a static pressure adjustment that does not consume power. If the solution is to be implemented in the last stage of a single-stage pump and a multi-stage pump, using the jet effect of the impeller to reduce the head ratio is to reduce the end cavity pressure and reduce the reaction An important measure for feeding pressure fluid flow. There is another important effect of reducing the end cavity pressure, which is to reduce the axial thrust, because this thrust is proportional to the end cavity pressure.

端腔充气时，保持液位（气液分界面的径向坐标）和压力的稳定是重要的，这需要排除或减小各种扰动因素的影响。上述方案要求，轮盘的端腔侧应具有粗糙的表面，其作用相当于叶轮外侧装设了无数微小的副叶片，可以增大对腔中流体的驱动力，能使端腔轮沿区附近的液体具有较高的圆周速度，并使输入端腔的二相流也增加圆周面速度。如果二相流中的液体不经这种加速而直接落入气液分界面，将造成圆周向速度冲击而影响液位的稳定性。在上述方案中，略为控制二相流进入端腔的流道面积和方向，便可获得一个喷向叶轮端面的二相流速度。喷出的液体将***成小液珠附着于叶轮的粗糙端面，在径向相对运动中依靠粘滞力带动而增加圆周速度。液珠加速可以减小液位扰动幅度，防止气体逃逸，从而减小气体和压力液体的流量，达到提高容积效率的目的。 When the end cavity is inflated, it is important to maintain the liquid level (radial coordinates of the gas-liquid interface) and the stability of the pressure, which needs to eliminate or reduce the influence of various disturbance factors. The above scheme requires that the end cavity side of the wheel disc should have a rough surface, and its role is equivalent to the installation of countless tiny auxiliary blades on the outer side of the impeller, which can increase the driving force for the fluid in the cavity and enable the vicinity of the edge of the end cavity wheel. The liquid has a higher peripheral velocity, and the two-phase flow into the input cavity also increases the peripheral surface velocity. If the liquid in the two-phase flow falls directly into the gas-liquid interface without such acceleration, it will cause a circumferential velocity impact and affect the stability of the liquid level. In the above scheme, by slightly controlling the area and direction of the two-phase flow entering the end cavity, a two-phase flow velocity sprayed to the end face of the impeller can be obtained. The ejected liquid will be split into small liquid beads and adhere to the rough end surface of the impeller. In the relative radial movement, the viscous force will be used to increase the peripheral speed. Liquid bead acceleration can reduce the amplitude of the liquid level disturbance and prevent gas from escaping, thereby reducing the flow of gas and pressure liquid to achieve the purpose of improving volumetric efficiency.

闭式叶轮的前端腔与吸入室之间存在一个环形泄漏间隙，从近轴部位通入二相流时，该间隙成为一个并联泄漏支路，因而必须将其改成防止气体逃逸的阻气间隙。在二相流入口加装分离分流二相流的阻气 V形环槽，或者加装二相流封浸润滑的有机材料挡圈，或者另接压力液体直接封堵该间隙，均可以提高入口的绝对压力，起到防止气体逃逸的作用。 There is an annular leakage gap between the front end cavity of the closed impeller and the suction chamber. When a two-phase flow is passed from the paraxial portion, the gap becomes a parallel leakage branch, so it must be changed to a gas blocking gap to prevent gas escape. . Adding a gas-blocking V-ring groove that separates and splits the two-phase flow at the inlet of the two-phase flow, or installs a two-phase flow to seal and lubricate the organic material retaining ring, or another pressure liquid directly seals the gap, which can improve the inlet. Absolute pressure to prevent gas from escaping.

由闭式或半幵式叶轮组装的多级泵，每一级都需要一个单独的射流器及其二相流循环流程来维持其端腔的气相压力，驱动压力液体可以从后级取得，这能提高射流器的工作压头比和降低压力液体的流量。当然，末级不能采用此法。 A multi-stage pump assembled by a closed or semi-pumped impeller requires a separate ejector and its two-phase flow cycle for each stage to maintain the gas phase pressure in its end cavity. The driving pressure liquid can be obtained from the subsequent stage. Can increase the working head ratio of the ejector and reduce the flow of pressure liquid. Of course, this method cannot be used in the final stage.

半开式叶轮无前盖和前端腔，二相流驱动射流器只需驱动后端腔之一路循环，其驱动流量可以减少一半以上。 The semi-open impeller has no front cover and front cavity. The two-phase flow driven ejector only needs to drive one cycle of the rear cavity, and its driving flow can be reduced by more than half.

内减摩充气二相流循环也可以由齿轮泵加压的液流驱动，或者由齿轮泵对离心泵输出液流再加压，此类驱动之射流器工作压头比高，压力液体流量小。充气减摩方案也可以不采用二相流循环方式，而采用压力罐装气体经减压阀降压和调节阔调节流量后，直接从减摩端腔静止壁注入，并从泵出口分流一小流量液体直接注入机械密封腔及前端腔泄漏间隙，分别冷却和封堵泄漏间隙，或者，将压力罐装气体经减压阀降压和调节阀调节流量后的气流直接注入泵之出口引出的回流管中构成二相流，分别连接到后端腔静止壁面和前端腔静止壁面近轴阻气间隙处，分别密封进入，也能达到同样的效果。这时，不再需要射流器来产生二相流，气体和液体的流量是分别调节的，其中液体流量调节阀串接在泵出口分流管中。 The internal friction reducing two-phase gas circulation can also be driven by the gear pump pressurized liquid flow, or the gear pump re-pressurizes the output liquid of the centrifugal pump. The ejector of this type of drive has a high working head ratio and a small pressure liquid flow. . Inflatable antifriction scheme can also not use the two-phase flow circulation method. Instead, the pressure canned gas can be injected directly from the static wall of the antifriction end cavity after pressure reduction and adjustment of the pressure regulating valve to reduce the flow. The flow liquid is directly injected into the leakage gap of the mechanical seal cavity and the front end cavity to cool and seal the leakage gap, respectively, or the pressured gas is depressurized by the pressure reducing valve and the flow rate adjusted by the regulating valve is directly injected into the backflow of the pump. A two-phase flow is formed in the tube, which is respectively connected to the stationary wall surface of the rear cavity and the parison gas-blocking gap of the stationary wall surface of the front cavity. At this time, the ejector is no longer needed to generate two-phase flow, and the gas and liquid flow rates are adjusted separately. The liquid flow adjustment valve is connected in series in the pump outlet shunt pipe.

压力罐装气体或者其他压力源气体的引入可以使内减摩方案的驱动装置得到简化，其工作也更稳定可靠。对于绝大多数的水泵，可以使用罐装压缩空气作为压力气源，对于泵送可燃性液体的泵，可以使用廉价的罐装氮气作为压力气源，气体还可以在安装于输出管路中的气液分离容腔中通过简单的重力分离予以清除。设计精良的内减摩装置可以达到较高的充气直径比，在运行中若干个百分点的效率提高可以节约大量的能源费用，而气源的消耗量却是很少的其费用微不足道。例如，对于一台轴功率为 100KW左右的中型水泵，当效率由 60%提高到 64%时，节约的电功率为 10.42KW, 每昼夜可以节约电能 250度。而其内减摩装置的驱动循环所消耗的气体流量大约只需 0.1标准状态升 /秒即可满足要求。换算成能量效益，当端腔压力为 0.4MPa时， 0.1标准状态升 /秒的压缩空气流量相当于 0.1 Χ 101.3 Χ 1η (400/101.3) = 13.9W的有效功率消耗，考虑 30%的气源压缩效率，也只相当于 46.4W左右的功率消耗，能量的投入产出效益比为 225倍。 The introduction of pressure tank gas or other pressure source gas can simplify the driving device of the internal friction reduction scheme, and its work is more stable and reliable. For most water pumps, canned compressed air can be used as the pressure gas source. For pumps that pump flammable liquids, cheap canned nitrogen can be used as the pressure gas source. The gas can also be installed in the output pipeline. The gas-liquid separation chamber is removed by simple gravity separation. A well-designed internal friction reduction device can achieve With a high inflation diameter ratio, the efficiency improvement of several percentage points in operation can save a lot of energy costs, but the consumption of air sources is very small and its cost is insignificant. For example, for a medium-sized water pump with a shaft power of about 100KW, when the efficiency is increased from 60% to 64%, the saved electric power is 10.42KW, which can save 250 degrees of electricity every day and night. The gas flow consumed by the drive cycle of the friction reducing device only needs 0.1 standard state liters / second to meet the requirements. Converted into energy efficiency, when the end cavity pressure is 0.4 MPa, the compressed air flow rate of 0.1 standard state liters per second is equivalent to an effective power consumption of 0.1 × 101.3 × 1η (400 / 101.3) = 13.9W, considering 30% of the air source The compression efficiency is only equivalent to a power consumption of about 46.4W, and the energy input-output benefit ratio is 225 times.

驱动循环所消耗的压缩空气流量之所以这么小，是因为除了气液分界面之峰峰值很小的随机扰动以外，端腔离心力场进行气液分离和气体保存的力学机制是超稳定的和非消耗性的，保持一个小的循环流量仅仅是为了完成初始化过程和在稳态运行中进一步增大受到扰动的液封环的内径。实际上，循环流量的设计并没有太严格的数量要求，甚至可以变动数量级。当设计循环流量较小时，其影响仅仅是初始化过程时间加长和液封环深度可能增加，前者的影响在稳态时间长度上可以忽略不计并且不影响稳态运行工况，后者在概率上影响稳态工况，但液封深度受限于本来就很小的扰动峰值幅度，因而影响甚微。本发明达到第三个发明目的的解决方案是：导流器为向心导轮，液流从外沿流入，至近轴环形腔汇合流出。流道呈内向涡旋形，曲率半径逐渐减小而截面积渐扩，其入口或出口截面积之和分别等于设计流量除以入出口设计流速。各流道旋转对称分布，分转移段和增压段。转移段前接叶轮流道出口，增压段连续扩张截面积，汇合于中心环腔，转 90度后轴向输出。流道由导叶隔开，导叶安装或一体化制造在基板上，成半开式结构，或者加盖板成闭式结构。基板中心有与转轴动配合的轴套。 The reason why the compressed air flow consumed by the driving cycle is so small is because the mechanical mechanism of the end-cavity centrifugal force field for gas-liquid separation and gas preservation is super stable and non-except for the small random disturbance of the peak-to-peak value of the gas-liquid interface. Consumption, maintaining a small circulating flow is only to complete the initialization process and to further increase the inner diameter of the disturbed liquid seal ring during steady state operation. In fact, the design of the circulation flow does not have too strict a quantity requirement, and can even vary by an order of magnitude. When the design circulation flow is small, the impact is only the lengthening of the initialization process time and the depth of the liquid seal ring may increase. The former effect can be ignored in the steady state time and does not affect the steady-state operating conditions. The latter has a probability effect. Steady-state conditions, but the liquid seal depth is limited by the small amplitude of the disturbance peak, which has little effect. The solution to achieve the third object of the present invention is: The deflector is a centripetal guide wheel, and the liquid flow flows from the outer edge to the confluent outflow of the paraxial annular cavity. The flow channel is inwardly swirling, the radius of curvature gradually decreases and the cross-sectional area gradually expands. The sum of the cross-sectional areas at the inlet or outlet is equal to the design flow rate divided by the design flow velocity at the inlet and outlet. The flow channels are distributed symmetrically in rotation and are divided into a transfer section and a boosting section. The transfer section is connected to the exit of the impeller flow path, and the pressurized section continuously expands the cross-sectional area, converges in the central ring cavity, and rotates 90 degrees to output axially. The runners are separated by guide vanes. The guide vanes are installed or integrated on the base plate to form a semi-open structure or a cover plate to form a closed structure. The center of the base plate is provided with a shaft sleeve which is dynamically matched with the rotating shaft.

现有技术釆用蜗道或导轮、导环直接在外环空间导流增压。当釆用蜗道时，速度分布不同的汇流与增压过程合用一个非完备约束的流道。汇流与增压的速度分布冲突、叶轮大开口对蜗道产生涡旋外展等不利因素，会导致流场不稳定，并产生局部激励损耗，因而蜗道的导流效率最低。当釆用导轮、导环时，汇流与增压过程仍然并存于大开口的连通空间，两者处于贯通并联的欠约束状态。大开口导致叶轮的相对涡旋和其他不稳定流态区域外展，其回流区甚至深入导轮导环内部深处，其尾缘涡干扰分界面流场分布。叶导论双方的欠约束状态均导致局部激励损耗，其导流效率也不高。 In the prior art, a worm or a guide wheel and a guide ring are used to directly guide and pressurize the outer ring space. When a worm is used, the confluence of different speed distributions and the supercharging process use a non-completely constrained flow channel. Disadvantages such as the conflict of the speed distribution of the confluence and the supercharging, the vortex abduction of the volute by the large opening of the impeller, will cause the flow field to be unstable and generate local excitation losses, so the worm's flow guidance efficiency is the lowest. When guide wheels and guide rings are used, the process of confluence and pressurization still coexists in the large open communication space, and the two are under-constrained in a parallel and parallel connection. The large opening causes the relative vortex of the impeller and other unstable flow regimes to ablate. Its return flow area even penetrates deep inside the guide ring guide ring, and its trailing edge vortex interferes with the interface flow field distribution. The under-constrained state of both sides of the introduction to Ye leads to local excitation loss, and its diversion efficiency is not high.

当需要级联过流时，现有技术导轮以轴面速度分量为主的转向机制需要消除大部分环量，然后迅速转向 180度进入反导流程。反导流道在去环量和反预旋过程中速度变化很大，其流道截面积随半径的减小而减小，反导加速过程形成向心降压分布。其过减速后再加速的不合理现象增大了导流负荷，也是降低效率的因素之一。 When cascading overcurrent is required, the steering mechanism of the prior art guide wheel, which is mainly composed of the axial surface speed component, needs to eliminate most of the loop volume, and then quickly turn 180 degrees to enter the anti-missile process. The speed of the anti-missile flow channel changes greatly during the loop removal and anti-pre-rotation. The cross-sectional area of the anti-flow channel decreases with decreasing radius, and the anti-missile acceleration process forms a centripetal pressure reduction distribution. The unreasonable phenomenon of excessive acceleration and deceleration increases the diversion load and is one of the factors that reduce the efficiency.

两种传统导流器都没有变工况适应性，当流量减小时，局部激励现象加重，导流效率下降幅度较大。在空间利用上，传统单级或多级泵的导流器均是环套于叶轮之外的，这使泵的径向尺寸增加了许多因而体积庞大。其中，多级泵的反导轮还占据了另一段相邻的轴向空间而增加了泵的轴向尺寸。体积庞大的蜗道、导轮和反导轮浪费了空间，增大了制造成本。本发明按照全程保守环量设计原则构造的向心导轮是一种内向涡旋型导流器，其增压流道是完备约束的，并按优化扩张率渐增截面积和渐减中线曲率半径，体积小而导流效率高。向心导轮的压力分布特征与传统导流器正好相反，其流道压力随中心线极半径的减小而单调增加。这种导轮与叶轮有着最佳的配合关系，其内向涡旋形流道及其与叶轮的轴向并列布设从根本上改变了传统导流器的结构和空间位置，较之具有外向涡旋流道和与叶轮径向环套的传统导流器，该导轮具有效率和成本两方面的突出优势。 Both types of traditional deflectors do not have adaptability to changing operating conditions. When the flow rate is reduced, the local excitation phenomenon is aggravated, and the diversion efficiency is greatly reduced. In terms of space utilization, the deflectors of traditional single-stage or multi-stage pumps are looped outside the impeller, which makes The radial dimension of the pump increases a lot and is therefore bulky. Among them, the anti-guide wheel of the multi-stage pump also occupies another adjacent axial space and increases the axial size of the pump. The voluminous worm, the guide wheel, and the anti-guide wheel waste space and increase manufacturing costs. The centrifugal guide wheel constructed in accordance with the principle of the whole-cycle conservative loop design of the present invention is an inward scroll type deflector. The booster flow path is fully constrained, and the sectional area is gradually increased and the center line curvature is gradually reduced according to the optimized expansion rate. Radius, small volume and high diversion efficiency. The pressure distribution characteristic of a centripetal guide wheel is exactly the opposite of that of a traditional deflector. The pressure of the flow channel increases monotonically with the decrease of the centerline pole radius. This guide wheel has the best matching relationship with the impeller. Its inwardly swirling flow path and its parallel arrangement with the axial direction of the impeller fundamentally change the structure and spatial position of the traditional deflector, compared with the outward scroll. The flow channel and the traditional deflector that is radially encircled with the impeller. The guide wheel has outstanding advantages in terms of efficiency and cost.

本发明设计对于提高效率特别有利，其原因有三：第一，叶轮流程和导流流程是真正几何串联的，其汇流过程和增压过程因而是分开的，不管叶轮流场如何，导流流程因串联而完全隔离，并具有完备的约束，因而不存在任何局部激励损耗，此害消除以后，剩下的仅仅是可以控制的沿途损耗。第二，增压流道的截面积扩张率可以独立改变和进行最优化设计，其截面形状也可以进行优化，因而沿途损耗将降到很低的水平，其增压效率最高可到达 98 %。第三，完备约束使液流方向与流量无关，因而具有最好的变工况适应性，并且其沿途损耗与流量的 3次方成正比，小流量时处于极低损耗状态。这三大增效机制，对比传统的外环蜗道或导轮的三个缺点：汇流增压过程几何并联或贯通、增压流道非完备约束且扩张率不能优化、无变工况适应性小流量损耗剧增，其差异之显著是毋庸赘言的。 The design of the present invention is particularly advantageous for improving efficiency for three reasons: First, the impeller flow and the diversion flow are truly geometrically connected, and thus the confluence process and the pressurization process are separated. Regardless of the impeller flow field, the diversion flow is caused by It is completely isolated in series and has complete constraints, so there is no local excitation loss. After the damage is eliminated, what remains is only controllable loss along the way. Second, the cross-sectional area expansion rate of the pressurized runner can be independently changed and optimized, and its cross-sectional shape can also be optimized. Therefore, the loss along the way will be reduced to a very low level, and its maximum pressurization efficiency can reach 98%. Third, the complete constraint makes the flow direction independent of the flow rate, so it has the best adaptability to changing conditions, and its loss along the way is proportional to the third power of the flow rate, and it is in a very low loss state at small flow rates. These three efficiency enhancement mechanisms are compared with the three shortcomings of the traditional outer ring worm or guide wheel: the geometry of the combined booster process is parallel or continuous, the booster runner is not fully constrained and the expansion rate cannot be optimized, and it has no adaptability to changing conditions. The small flow loss increases sharply, and the difference is self-evident.

对于多级泵的级联，本发明方案更能体现其优越性。否定去环量加载反预旋增功的不利设计，转而保守正预旋级联，正好发挥了保守环量设计在***优化方面的潜力。这种级联除了上述三大优势以外，还增加了大幅减小导流负荷和省去 180度换向环节两项优势。其中，前者包含因保守输出环量而降低减速幅度和消除过减速过程两项因素，如前所述，降低导流负荷一般具有 3次幂函数的减耗敏感性。后者是指保持圆周速度过流省去了 180 度的轴面分量换向环节，其影响是多方面的，除了省去 2次幂函数型的局部阻力损耗以外，更主要的是因此而省去反导流程和过减速过程两项好处，这是影响基本流程规划和结构布局的关键性改进，对空'间利用率有重大影响。需要说明的是，本发明方案的轴面分量换向过程不是不存在了，而是分散化了。从容地安排一个数值相对很小的轴面速度增量矢在较长的路程中和较长的时间里产生，其空间变化率和时间变化率都很小，因而不具有急转向的几何与力学特征，其局部阻力损耗因而消除，这正是保守环量设计的目标效益。 For the cascade of multi-stage pumps, the scheme of the present invention can better reflect its superiority. The negative design of anti-loop preload and power increase was removed, and the positive pre-rotation cascade was conserved instead, which fully utilized the potential of conservative loop design in system optimization. In addition to the above-mentioned three advantages, this cascade also adds two advantages of greatly reducing the diversion load and eliminating the 180-degree commutation link. Among them, the former includes the two factors of reducing the deceleration amplitude and eliminating the over-deceleration process due to the conservative output loop quantity. As mentioned above, reducing the diversion load generally has a sensitivity of reducing power by a third power function. The latter means that the 180 ° axial surface component commutation link is omitted in maintaining the peripheral velocity overcurrent. The impact is multifaceted. In addition to eliminating the local power loss of the second power function type, it is more important to save The two benefits of the anti-missile process and the over-deceleration process are key improvements that affect the basic process planning and structural layout, and have a significant impact on space utilization. It should be noted that the process of reversing the axial component of the solution of the present invention is no longer existing, but is decentralized. It is easy to arrange a relatively small value of the axial speed increase vector over a long distance and a long time, and its spatial change rate and time change rate are small, so it does not have the geometry and mechanics of sharp turning Characteristic, its local resistance loss is thus eliminated, which is the goal benefit of conservative loop design.

减小导流负荷及其空间开销，不产生过减速现象而实现速度单调减的增压过程，均为使导流流程大为缩短的技术因素。因此，在同样的入导速度下，因为沿途损失的减少、转向局部损失的消除、连续减速增压过程的实现等多项因素，导流水力损耗将有较大幅度的降低。如前所述，本发明高势动比叶轮将大幅度降低入导速度，将其与向心导轮结合时，上述降低损耗的优势将更加突出，在数量关系上，将表现为 3次幂函数型剧减。 Reducing the diversion load and its space overhead, and the supercharging process that achieves a monotonous reduction in speed without causing excessive deceleration, are all technical factors that greatly shorten the diversion process. Therefore, at the same speed, due to a number of factors, such as reduction of loss along the way, elimination of local steering losses, and implementation of a continuous deceleration and pressure increase process, the hydraulic loss of diversion will be greatly reduced. As mentioned above, the high potential-to-dynamic-ratio impeller of the present invention will greatly reduce the speed of guide. When it is combined with the centripetal guide wheel, The above-mentioned advantages of reducing losses will be more prominent. In terms of quantity relationship, it will appear as a third power function type drastic reduction.

本发明的这种配套部件及其与向心导轮的组合，既可以配套于高势比离心泵，又可以应用于现有技术离心泵的简单改造，其导流效率均适用（2) 式。本发明更为明显的一项优势是：导流器的空间开销将因为这种结构的优势而大为减小。向心导轮及其叶导轮组合结构紧凑，在降低制造成本和方便使用等方面效果突出。向心导轮是一种按照离心泵尤其是多级泵的空间规划的合理性概念而专门设计的优化方案。较之现有技术，该方案节省了叶轮的外环空间以及多级结构中的反导空间，而代之以仅相当于反导空间中与叶轮直径相等的那一部分来安装导轮。因此，向心导轮的径向尺寸将和叶轮相等，这使得整个泵的直径设计只需以叶轮直径为基准来考虑，其导流空间利用率大约提髙 2倍，即空间需求将减少 2/3，泵的制造成本无疑将大大降低。如果与高势比叶轮配合使用，由于导流负荷减小为若干分之一，其体积将会再减小 50%左右。 The matching component and the combination with the centrifugal guide wheel of the present invention can be used not only for high-potential ratio centrifugal pumps, but also for simple retrofitting of centrifugal pumps of the prior art, and the diversion efficiency is applicable to the formula (2) . A more obvious advantage of the present invention is that the space overhead of the deflector will be greatly reduced due to the advantages of this structure. The combined structure of the centrifugal guide wheel and the impeller guide wheel is compact, and the effect is outstanding in reducing manufacturing costs and facilitating use. The centrifugal guide wheel is an optimized solution specially designed according to the rationality concept of the spatial planning of the centrifugal pump, especially the multi-stage pump. Compared with the prior art, this solution saves the outer ring space of the impeller and the anti-missile space in the multi-stage structure, and instead installs the guide wheel only in the portion of the anti-missile space that is equal to the diameter of the impeller. Therefore, the radial dimension of the centrifugal guide wheel will be equal to the impeller, which makes the diameter design of the entire pump only need to consider the impeller diameter as a reference, and its guide space utilization rate will be approximately doubled, that is, the space requirement will be reduced by 2 / 3, the manufacturing cost of the pump will undoubtedly be greatly reduced. If it is used with a high potential ratio impeller, its volume will be reduced by about 50% because the diversion load is reduced to a fraction.

向心导轮的这些优越性，对于后续说明中将要公开的单级泵和多级泵的同构概念，以及模块化组合的方法的建立，均具有决定性的作用。本发明关于向心导轮的一项重要的附加设计是：导轮流道转移段由叶轮出口柱面、叶轮腔前壁曲面和导轮前底面外沿曲面围成，其截面分为叶轮腔部分和导轮部分，两部分装配吻接合一。其合成截面的位置周期性地向导轮方向转移，其截面积随导流圆心角的增大而周期性地线性增大。其周期等于一个导流流道对应的圆心角，其增大比例系数等于叶轮转过单位角度的体积排量设计值与液流出口绝对速度设计值之比，或者还乘以一个大于 1 而小于导轮增压流道最小扩张率的扩张系数。 . These advantages of the centrifugal guide wheel are decisive for the homogeneous concept of the single-stage pump and the multi-stage pump to be disclosed in the subsequent description, and the establishment of a modular combination method. An important additional design of the centrifugal guide wheel of the present invention is: The guide wheel flow passage transfer section is surrounded by the impeller exit cylinder surface, the curved surface of the front wall of the impeller cavity and the curved surface of the front bottom surface of the impeller, and the cross section is divided into the impeller cavity portion. And the guide wheel part, the two parts are assembled and joined together. The position of its composite section is periodically shifted in the direction of the guide wheel, and its cross-sectional area increases linearly with the increase of the diversion center angle. Its period is equal to the center angle of a diversion channel, and its increasing proportionality factor is equal to the ratio of the design value of the volumetric displacement of the impeller through a unit angle to the design value of the absolute velocity of the liquid outlet, or it is multiplied by a value greater than 1 and less Expansion coefficient of the minimum expansion rate of the guide wheel booster runner. .

转移段流道承接叶轮出口液流，属于高速流道，其设计对于离心泵的全程水力效率有重要影响，设计不良还可能产生水锤震颤效应或空化气蚀效应，因而需要较为仔细的设计。其一般性的设计原则是：流道的长度及其截面的周长应该尽可能地缩短，因而圆形截面最理想；当必须使用矩形截面时，其长宽比应该尽量接近于 1，最好作内圆倒角；当必须使用其他功能截面时，应尽量缩小摩擦边际线的长度。除了这些控制摩擦面积的一般性原则外，还必须控制截面积的变化率，使之符合汇流的要求，同时还必须控制截面边际坐标的变化率，它们是完成过流转移动力学过程的关键变量。为避免冗繁叙述，关于截面形状优化及其边际坐标控制问题，将在后续实施例设计中结合附图予以说明。 The transfer channel of the transfer section receives the impeller outlet liquid flow, which belongs to the high-speed flow channel. Its design has an important influence on the overall hydraulic efficiency of the centrifugal pump. Poor design may also produce water hammer chatter effect or cavitation cavitation effect, so more careful design is required. . Its general design principles are: The length of the flow channel and the perimeter of its cross section should be as short as possible, so a circular cross section is the most ideal; when a rectangular cross section must be used, its aspect ratio should be as close to 1 as possible, the best Make internal chamfers; when other functional sections must be used, the length of the frictional margin line should be minimized. In addition to these general principles for controlling the friction area, the rate of change of the cross-sectional area must be controlled to meet the requirements of the confluence, and the rate of change of the marginal coordinates of the cross-section must also be controlled. These are the key variables to complete the dynamic process of the overcurrent transfer. To avoid redundant descriptions, the optimization of the cross-sectional shape and the control of its marginal coordinates will be described in the design of subsequent embodiments with reference to the drawings.

本发明的上述附加设计的目标在于满足高效率地保持速度或者还包括连续减速增压的过流要求。理论上，利用不可压缩流体的特性，依据牛顿方程和伯努利方程，通过控制流道截面积的变化，同时控制截面之两个部分的面积分配和形状，是可以实现具有任何力学特征的过流转移的。本发明从稳定液流的平均流速的目的出发，设计了一个匀速等压或者降速增压的势流过程。其基本方法是，从最小截面积开始，用汇流截面的连续变形伴随面积线性增大致最大值后两腔平稳分割的周期性过程方法来构造流道。在每一个流道对应的圆心角周期内实现流道的转移和截面的合理化控制，包括满足流速的连续性条件和加速度最小化的原则，这是基于动量定理的思考。其中，汇流过程的圆周速度是保持不变的或者是尽量尊重的，目的在于避免在同一个贯通空间里出现大的梯度分布而引起动量交换型损耗，更不允许出现局部激励。边际摩擦损耗则通过边际线长度最小化的摩擦面积控制来减小。所述的周期性过程的实现本身实际上也包含了对流速的轴面分量的周期性控制。在上述设计中，改善流道的效率特性、抗气蚀特性和变工况运行的自适应特性，是关注的重点。 The objective of the above-mentioned additional design of the present invention is to meet the over-current requirements of maintaining the speed efficiently or further including continuous deceleration and boosting. Theoretically, by using the characteristics of incompressible fluid, according to Newton's equation and Bernoulli's equation, by controlling the change of the cross-sectional area of the flow channel, and simultaneously controlling the area distribution and shape of the two parts of the cross-section, it is possible to achieve a process with any mechanical characteristics. Stream transfer. Starting from the purpose of stabilizing the average flow velocity of the liquid flow, the present invention designs a potential flow process of constant pressure, constant pressure, or deceleration. The basic method is to start with the smallest cross-sectional area, Periodic process method of smooth division of the two cavities after the area increases linearly to the maximum to construct the flow channel. The transition of the flow channel and the rationalized control of the cross-section during the central angle period corresponding to each flow channel, including the principle of satisfying the continuity condition of the flow velocity and the acceleration minimization, are based on the thinking of the momentum theorem. Among them, the peripheral speed of the confluence process is kept constant or respected as much as possible, the purpose is to avoid a large gradient distribution in the same penetrating space and cause momentum exchange loss, and local excitation is not allowed. Marginal friction loss is reduced by friction area control that minimizes the length of the margin line. The realization of the periodic process itself actually includes the periodic control of the axial component of the flow velocity. In the above design, the improvement of the flow channel's efficiency characteristics, anti-cavitation characteristics and adaptive characteristics of variable operating conditions is the focus of attention.

本发明的转移段流道方案仅仅体现为导轮底面及叶轮盖板或叶轮腔盖板外沿部位的一种功能曲面的形状设计，并没有形成独立的零部件，因而在制造过程仅相当于一种工艺造型。当所涉及零件采用模成型工艺批量制造时，其实现成本非常低。本发明与向心导轮配套的封装结构体设计是：采用中心涡道汇流变角度出管对称端盖作前后轴向封装。该端盖由带装配止口的承压盖板和与盖板一体化制造的中心结构及连通管道组成。其中心结构包括轴套、轴套***的中心蜗道、蜗道围护结构支撑的轴承腔和轴孔。承压盖板的承压面为平面或与向心导轮开口面吻合的旋转曲面，其近轴部位有一个与蜗道连通的环形开口。中心蜗道是一种径向渐开轴向平移的三维蜗道，其始端是环形开口平面上的隔舌，其末端在增加了径向和轴向坐标的隔舌下方。蜗道截面积与圆心角成正比，比例系数等于叶轮转过单位角度的体积排量与液流平均速度之比。以开口圆平面为基准，随着截面积的线性增加，蜗道底部中心线的径向坐标和轴向坐标逐渐增加，形成一个蜗底斜坡，转过 360度后进入隔舌下方，随后与管道吻接。蜗道截面形状亦随圆心角改变，从隔舌直线段开始，首先为长轴在开口平面上的变短半轴长半椭圆，成为半圆后逐渐下沉并沿一足以绕开轴承腔支承结构的曲率变化率适当的渐开弧线延伸，成为曲边四边形加半圆形状，直到进入隔舌下方，然后保持截面积地变形为圆截面与管道吻接。该对称端盖作后盖时，带环量的轴向来流从环形开口进入蜗道，在旋转和平移中汇流于涡道，沿蜗道旋转 0〜360度不等，到达蜗道终点后从吻接的出管流出。作前盖时，来管中直线运动液流接受蜗道法向力作用转作三维涡旋运动，最后从环形开口带环量地分流进入叶轮吸入室，运动过程与后盖端相反。前后盖蜗道中的涡旋运动在水力规范速度下是低损耗的，装配时将前后盖沿止口转动可以各自独立地改变入管和出管的角度。 The flow channel scheme of the transfer section of the present invention is only embodied in the shape design of a functional curved surface on the bottom surface of the guide wheel and the outer edge of the impeller cover plate or impeller cavity cover plate, and does not form independent parts. Therefore, the manufacturing process is only equivalent to A craft shape. When the parts involved are mass-produced using a molding process, their implementation costs are very low. The design of the packaging structure matching the centripetal guide wheel according to the present invention is as follows: a symmetrical end cap with a central vortex confluence angle outlet tube is used for front and rear axial packaging. The end cap is composed of a pressure-bearing cover plate with an assembly stop, a central structure integrated with the cover plate, and a connecting pipe. Its central structure includes a shaft sleeve, a central volute around the shaft sleeve, a bearing cavity supported by the wormway envelope structure, and a shaft hole. The pressure-bearing surface of the pressure-bearing cover plate is a flat surface or a rotating curved surface that coincides with the opening surface of the centrifugal guide wheel. The paraxial part has an annular opening communicating with the worm channel. The central worm is a kind of three-dimensional worm with radial involute axial translation. The beginning end is the tongue on the plane of the annular opening, and the end is below the tongue with increased radial and axial coordinates. The cross-sectional area of the worm is proportional to the center angle, and the proportionality factor is equal to the ratio of the volumetric displacement of the impeller over a unit angle to the average speed of the liquid flow. Based on the open circular plane, as the cross-sectional area increases linearly, the radial and axial coordinates of the centerline of the bottom of the worm gradually increase, forming a snail bottom slope. After 360 degrees, it enters the lower part of the tongue, and then communicates with the pipe. Kiss. The shape of the cross section of the worm also changes with the center angle. Starting from the straight segment of the tongue, the first is the shortened semi-axis and semi-ellipse with the long axis in the plane of the opening. The involute curve with a suitable curvature change rate extends into a curved quadrilateral plus a semi-circular shape, until it enters the lower part of the tongue, and then maintains a cross-sectional area to deform into a circular cross-section to meet the pipe. When the symmetrical end cap is used as the back cover, the axial incoming flow with a circular amount enters the volute from the annular opening, converges on the vortex during rotation and translation, and rotates along the worm ranging from 0 to 360 degrees. After reaching the end of the worm Flow out from the kissing tube. When the front cover is used, the linear flow in the incoming tube receives the normal force of the worm and converts it into a three-dimensional vortex motion. Finally, it is diverted from the annular opening into the suction chamber of the impeller. The movement process is opposite to the end of the rear cover. The vortex motion in the volute of the front and rear covers is low loss at the hydraulic standard speed. When the front and rear covers are rotated along the stop during assembly, the angles of the inlet and outlet pipes can be changed independently.

中心蜗道分汇流变角度出管对称端盖是本发明的一种重要配套部件。应用向心导轮与该部件配套，可以使离心泵的体积大为缩小，其变角度出管的功能在应用中可以满足难以预料的用户临场需要，可以节约场地和管道，可以减少弯头和提高管路效率。这种设计甚至可能使离心泵的进出口角度分型号的划分成为不必要，显然，站在用户的角度，这种划分是不方便的。本发明的这种设计目标包括多重的通用性：在一台泵中，它是前后盖通用的；在单级泵和多级泵之间，它也是可通用互换的。在单级泵中使用时，这种封装结构的整体优势更是特别明显。端盖的对称性所带来的多重通用性，以及简化进出口角度分型号的潜在优势，可以简化离心泵的设计和制造过程，从而降低制造成本。 The symmetric end cap of the central volute branching and merging angle outlet pipe is an important supporting component of the present invention. The application of centripetal guide wheels with this component can greatly reduce the volume of the centrifugal pump, and its variable angle outlet function can meet the unpredictable user's on-site needs in the application, can save space and pipes, can reduce elbows and Improve pipeline efficiency. This design may even make the division of the inlet and outlet angles of centrifugal pumps into different types unnecessary. Obviously, from the user's perspective, this division is inconvenient. This design goal of the invention includes multiple versatility: in a pump, it is universal It is universally interchangeable between single-stage and multi-stage pumps. When used in single-stage pumps, the overall advantages of this package structure are even more obvious. The multiple versatility brought by the symmetry of the end caps and the potential advantages of simplifying the model of the inlet and outlet angles can simplify the design and manufacturing process of the centrifugal pump, thereby reducing manufacturing costs.

本发明的这种配套部件及其与向心导轮的组合，既可以配套于髙势比离心泵，又可以应用于现有技术离心泵的简单改造。将其应用于常势比和高势比离心泵时，蜗道的局部阻力系数是很小的，因而可以将其流道合并到导流流道中一并计算损耗，合并后的导流效率均适用公式（2 ) 。向心导轮及其转移段流道加上对称端盖的动能损耗率 ξ ₂将显著低于传统导流器。在变工况运行时，由于恒切向入导避免撞击损耗的特点，其损耗不但不增加反而会减少，因而会产生效率曲线在小流量区不但不降反而上升的优良特性。又由于减小尺寸和方便用户安装的优势也具有特别的竞争力。因此，向心导轮和对称端盖的组合也是一项不依赖于高势比叶轮的独立发明。这项技术与高势比叶轮、内减摩等发明特征组合使用时，将使各项优势特征相得益彰。 The matching component and the combination with the centrifugal guide wheel of the present invention can be used not only for centrifugal pumps with pseudopotential ratio, but also for simple modification of the centrifugal pump in the prior art. When it is applied to the constant potential ratio and high potential ratio centrifugal pumps, the local resistance coefficient of the volute is very small, so the flow channel can be combined into the diversion flow channel to calculate the loss, and the combined diversion efficiency is uniform. Formula (2) applies. The kinetic energy loss rate ξ ₂ of the centrifugal guide wheel and its transfer section flow channel plus the symmetrical end cap will be significantly lower than that of the traditional deflector. When running under variable operating conditions, due to the characteristics of constant tangential conduction to avoid impact losses, the losses will not only increase but will decrease, so the excellent characteristic of the efficiency curve will not only decrease but increase in the small flow area. It is also particularly competitive due to the advantages of reduced size and easy installation. Therefore, the combination of the centrifugal guide wheel and the symmetrical end cap is also an independent invention that does not depend on the high potential ratio impeller. When this technology is used in combination with inventive features such as high potential ratio impellers and internal friction reduction, the various advantageous features will complement each other.

当向心导轮和对称端盖用于改造现有技术离心泵时，其向心增压、变角度出管和体积大幅度减小等功能和性能，是一种突出的实质性特点，能够产生显著的进步。例如，据初步估算，仅减小导流器体积和前后端盖及其轴承座与出管一体化并且对称通用两项，就可能使离心泵的制造成本降低 30%以上，用户还能得到场地节约、管路节省、效率提高等方面的效益。显然，这种设计具有多方面的技术经济优势。基于向心导轮、对称端盖的特点和优势，本发明据以设计了一种模块化组合离心泵的方法，依据该方法可以组合出许多种新型的离心泵。这种方法不仅用来构造多级泵，还用来构造单级泵，不仅用来实施一种技术，还用来组合实施多种技术。 When the centrifugal guide wheel and the symmetrical end cover are used to transform the prior art centrifugal pump, its functions and performances such as centripetal pressure increase, variable angle outlet pipe and greatly reduced volume are a prominent substantive feature, which can Produces significant progress. For example, according to preliminary estimates, only reducing the volume of the deflector and integrating the front and rear end caps and their bearing housings with the outlet pipe are symmetrical and universal, which may reduce the manufacturing cost of the centrifugal pump by more than 30%, and users can also obtain the site. Benefits such as savings, piping savings, and efficiency improvements. Obviously, this design has many technical and economic advantages. Based on the characteristics and advantages of the centrifugal guide wheel and the symmetric end cover, the present invention has designed a modular modular centrifugal pump method according to which many new types of centrifugal pumps can be combined. This method is used not only to construct multi-stage pumps, but also to construct single-stage pumps, not only to implement one technology, but also to implement multiple technologies in combination.

基于向心导轮的向心增压原理，将导轮流程作为与叶轮速度场及其动能分布的反向处理过程与之轴向并列，可以形成最简捷的流程空间周期性。根据该周期性可以建立最紧凑的模块化结构的空间概念，其中隐含"液流从近轴环形口带环量流入和流出"的连接模式。从近轴环形口入出是必要设计，之所以要求带环量，是出于对离心泵全程流速变化率最小化的力学考虑提出的要求。这种最小化好处很多，包括变工况运行适应性和入出口气蚀特性的改善、导流负荷的减轻、入出口动能的利用、以及最关键的从叶轮出口后高效入导等等。这都属于叶轮流道的边界条件优化问题，可见，保守环量是边界条件优化的核心问题。 Based on the principle of centripetal supercharging of the centrifugal guide wheel, the process of the guide wheel is axially juxtaposed with the impeller speed field and its kinetic energy distribution to form the simplest periodicity of the process space. According to this periodicity, the space concept of the most compact modular structure can be established, in which the connection mode of "liquid flow flowing in and out from the paraxial annular mouth with annular flow" is implicit. It is necessary to design the entry and exit from the paraxial annular port. The reason for the requirement of the loop quantity is the requirement of mechanical considerations to minimize the change rate of the flow rate of the centrifugal pump. There are many benefits to this minimization, including improved adaptability under varying operating conditions and improved cavitation characteristics at the inlet and outlet, reduction of the diversion load, utilization of the kinetic energy at the inlet and outlet, and the most critical efficiency of the guide from the impeller exit. This all belongs to the optimization of the boundary conditions of the impeller flow path. It can be seen that the conservative loop is the core problem of the optimization of the boundary conditions.

从前述说明可知，对称端盖的近轴环形开口和三维蜗道是保守环量设计的，具有造就弥补所需边界条件的能力，能够适应上述连接模式。因此，以该原理、该周期性、该模块概念和该连接模式为基础，就能设计出一种对于具有任何技术特性的叶轮都可以进行模块化组合的方法。该方法要求叶轮的外部形状和尺寸标准化，以标准化的叶轮外部形状和尺寸为基准，展开离心泵的轴向空间，就可以设计出轴向连接的模块化拼装结构。该结构包含一个水力流态周期中的全部结构件，实际上就是叶轮和导轮及其附件的轴向组合。它们的结构及其功能具有几何及运动学和动力学特征的周期性，而其流场中的势函数——静压力则是沿途累加和在连通器原理下传递的，不具有也不需要这种周期性。这样设计的模块化组合方法与级数无关，因而肯定是普适于单级泵和多级泵的新型设计方法。 It can be known from the foregoing description that the paraxial annular opening of the symmetrical end cap and the three-dimensional volute are designed with conservative quantities, have the ability to make up the required boundary conditions, and can adapt to the above connection mode. Therefore, based on the principle, the periodicity, the module concept, and the connection mode, a method for modularly combining impellers with any technical characteristics can be designed. This method requires the external shape and size of the impeller to be standardized. Based on the standardized external shape and size of the impeller, the axial space of the centrifugal pump is expanded to design a modular assembly structure for axial connection. This structure contains all the structural elements in a hydraulic flow regime, which is actually the axial combination of the impeller, the guide wheel and its accessories. They The structure and its function have the periodicity of geometric and kinematic and dynamic characteristics, while the potential function in the flow field, the static pressure, is accumulated along the way and transmitted under the principle of the connector. It does not have or is not required. Periodic. The modular combination method designed in this way has nothing to do with the number of stages, so it must be a new design method that is generally suitable for single-stage and multi-stage pumps.

模块化技术组合方法及其组合产品的准确描述是：基于向心导轮的结构和特性，将其流程作为与叶轮流程动能分布的反向处理过程轴向并列，形成简捷的空间周期性，据以构造带环量近轴口连接的叶导轮轴向组合向心增压赋能模块，简称向心增压模块，并将其标准化。基于对称端盖的结构和特性，将其作为带环量近轴环形口连接的流场边界及端封结构模块并将其标准化。标准化产生互相对应的两个包含子规格的规格系列，其中同一种父规格的模块装配尺寸和基本接口参数（例如流量、转速）相同而具有査表检验互换性，父规格下的同一种子规格模块装配尺寸和所有接口参数（包括泛函意义下的参数，例如耐压 The accurate description of the modular technology combination method and its combined products is: Based on the structure and characteristics of the centrifugal guide wheel, its process is axially juxtaposed with the reverse process of the kinetic energy distribution of the impeller process to form a simple spatial periodicity. An axially combined centrifugal booster energizing module is constructed by using an impeller with a ring-shaped near-axis connection, which is referred to as a centripetal booster module, and standardized. Based on the structure and characteristics of the symmetric end cap, it is used as a flow field boundary and end seal structure module with a ring-shaped paraxial ring mouth connection and standardized. Standardization produces two specifications series that contain child specifications. The parent module has the same assembly dimensions and basic interface parameters (such as flow rate and speed). It has the same lookup table to check interchangeability. The same seed specification module under the parent specification Assembly dimensions and all interface parameters (including parameters in the functional sense, such as withstand voltage

2MPa, 耐腐蚀材料制成等）相同而具有完全互换性，两种互换性定义在单级泵、多级泵、各种型号和不同内含技术包括使用高势比或常势比叶轮的离心泵的大集合上，在规划和设计过程中定义互换性域，在设计之后的生产过程中和在生产之后的使用过程中互换性在定义域内成立。按照 "液流从近轴环形口带环量流入和流出"的连接模式，将 1个或最多 64 个串联（传统多级泵一般不超过 20级，本发明级数可增多，但一般不超过 64级）的多个向心增压模块与 2个对称端盖模块组合，即构成模块化组合单级泵或多级泵。向心增压模块无外壳者配用中开式外壳，带外壳者为级段式结构。在现有技术中，除了轴承、轴封、紧固件等少数跨型号使用的辅助性零件以外，没有不同类型的离心泵使用相同的主要功能模块的规划，也没有包含不同技术和具有不同性能的主要功能模块在同一种离心泵上组合和替换的设计。如所周知，现有技术的每一种单级泵都是根据选定的水力模型个别设计的，不同水力模型的叶轮和导流器没有互换性，水力模型相同的叶轮和导流器因型号规格的不同而具有不同的尺寸，也没有互换性。现有技术的级段式多级泵通常使用相同的赋能部件或组件，用它们可以组装同一流量规格的不同扬程离心泵，但使用的模型和技术是固定的和不能改变的，并且，其支承围护结构及轴系部件仍然是单独设计的。由于这些问题的存在，致使离心泵的产品型系非常庞杂，离心泵的新技术推广也在众多规范壁垒的阻隔下被延缓。 2MPa, made of corrosion-resistant materials, etc.) Same and fully interchangeable. The two interchangeability are defined in single-stage pumps, multi-stage pumps, various models and different built-in technologies, including the use of high-potential or constant-potential impellers. On the large set of centrifugal pumps, interchangeability domains are defined during the planning and design process, and interchangeability is established within the definition domain during the production process after design and during the use process after production. According to the connection mode of "fluid flow in and out from the paraxial annular mouth with annular flow", one or a maximum of 64 are connected in series (traditional multi-stage pumps generally do not exceed 20 stages, the number of stages of the present invention can increase, but generally does not exceed 64-stage) multiple centripetal booster modules combined with 2 symmetrical end cap modules, which form a modular combination single-stage or multi-stage pump. Centrifugal booster modules without shells are equipped with a mid-open shell, and those with shells are stepped structures. In the prior art, there are no plans for different types of centrifugal pumps to use the same main functional modules, except for a few auxiliary parts such as bearings, shaft seals, and fasteners that are used across models. They also do not include different technologies and have different performance. The design of the main function modules is combined and replaced on the same centrifugal pump. As is well known, each single-stage pump in the prior art is individually designed according to the selected hydraulic model. The impellers and deflectors of different hydraulic models are not interchangeable. Different models have different sizes and are not interchangeable. The prior art stage multistage pumps usually use the same energized parts or components, and they can be used to assemble different lift centrifugal pumps of the same flow specification, but the models and technologies used are fixed and cannot be changed, and their Support envelopes and shafting components are still individually designed. Due to the existence of these problems, the product types of centrifugal pumps are very complicated, and the promotion of new technologies for centrifugal pumps has also been delayed by many regulatory barriers.

本发明将多级泵釆用相同赋能组件拼装的传统方法扩充为模块化组合方法，使在单级泵和多级泵之间，在围护和支承结构体的设计上，进而在不同技术的组合代数域内，都能够广泛地采用具有优势的模块化组件，具体化以后，新的设计方法就形成了。在设计这种方法的核心思想中，发挥组合和模块化的工艺效益和打破新技术面临的规范壁垒只是目的的一部分，借机融入数学规划方法来提升离心泵的设计性价比则是另一个更为迫切的想法。之所以更为迫切，是因为模块化组合方法及其结构设计还可能只是一个仅应用于局部的方法。如果依据该方 ¾随意地选取参数构造模块，将造成流量一压力平面上的杂乱的空间占用，这对行的***性资源优化和成本降低不利或没有大的补益。要想从全局得益，应该改变在流量一压力平面上依据社会需求调査数据直接规划离心泵产品的型谱覆盖的传统做法，改而将模块化组合的结构设计考虑进去，这能大大简化离心泵的型谱， ***性地降低泵行业的平均生产成本。模块化组合的参数选择的依据则应该来源于经过最优化规划的规范。 The invention extends the traditional method of assembling multi-stage pumps with the same energizing components to a modular combination method, so that between the single-stage pump and the multi-stage pump, in the design of the envelope and support structure, and then in different technologies In the combinatorial algebra domain, the modular components with advantages can be widely used. After the concrete design, a new design method is formed. In the core idea of designing this method, the use of combined and modular process benefits and breaking the regulatory barriers faced by new technologies are only part of the purpose. Taking the opportunity to incorporate mathematical planning methods to improve the cost-effectiveness of centrifugal pump design is another Urgent idea. It is even more urgent because the modular combination method and its structural design may be just a partial application method. If the parameter construction module is randomly selected according to this method, it will cause a messy void on the flow-pressure plane. Occupy time, which is unfavorable or not of great benefit to the systematic resource optimization and cost reduction of the bank. In order to benefit from the overall situation, the traditional method of directly planning the pattern coverage of centrifugal pump products based on social demand survey data on the flow-pressure plane should be changed, and the modular and combined structural design should be taken into account, which can greatly simplify The profile of centrifugal pumps systematically reduces the average production cost of the pump industry. The basis for parameter selection of the modular combination should be derived from the optimized planning specification.

本发明将向心增压模块作为离心泵的一种低成本积木组件，据以建立离心泵的多级拼装规范，并且在该规范中还特别地将单级泵也包括于其中，以使耗时糜费的单级泵的设计和制造不再成为必要，这是最原始的想法。但发明人在研究多级泵的性能方程并将其与髙势比技术进行比较时，产生了新的技术推演。如所周知，离心泵做成多级有利于提高效率，因为，对于同样的扬程需求，多级泵的级扬程与级数成反比，相同转速下其叶轮直径和入导速度与级数的平方根成反比，因而泵的 2次幂型导流损耗也将与级数成反比。比较本发明所述高势比叶轮的技术特性与多级泵特性之间的关系，从对水力损耗的影响来说，高势比叶轮的设计参数——反馈减速比给出线性减函数关系，这与多级泵的级参数调节方向相同，因而可以将两者看成是分区间等价的调节参数，其差别在于后者是离散的并且应用空间较大，而前者 '却是连续的但应用空间受限。这种等价性揭示了提高离心泵效率的另一条重要途径，其差别展示了两大途径互补组合的良好前景。 In the present invention, a centripetal booster module is used as a low-cost building block component of a centrifugal pump to establish a multi-stage assembly specification for a centrifugal pump, and a single-stage pump is also specifically included in the specification to make consumption The design and manufacture of time-consuming single-stage pumps is no longer necessary. This is the original idea. However, when the inventors studied the performance equation of the multi-stage pump and compared it with the pseudo-potential ratio technique, a new technical deduction was produced. As is well known, making a multi-stage centrifugal pump is beneficial to improve efficiency, because, for the same head requirement, the multi-stage pump's stage head is inversely proportional to the number of stages, and its impeller diameter and inlet speed and the square root of the number of stages at the same speed It is inversely proportional, so the second power type guide loss of the pump will also be inversely proportional to the number of stages. Compare the relationship between the technical characteristics of the high potential ratio impeller and the characteristics of the multi-stage pump according to the present invention. From the impact on the hydraulic loss, the design parameter of the high potential ratio impeller, the feedback reduction ratio, gives a linear reduction function relationship. This is the same direction as the adjustment of the stage parameters of the multi-stage pump. Therefore, the two can be regarded as equivalent adjustment parameters between zones. The difference is that the latter is discrete and has a large application space, while the former is continuous but Limited application space. This equivalence reveals another important way to improve the efficiency of centrifugal pumps. The difference shows the good prospect of the complementary combination of the two approaches.

本发明主张将两种高效途径结合，并在考虑模块化组合方法的型谱规划中具体结合进去，这能产生巨大的经济和社会效益。这种结合，实际上是将离心泵在流量一扬程平面上的型系规划转换成级模块规划的组合，因而将问题转化为级模块在流量一扬程平面上的规划。本发明设计了对级模块参数进行数学规划的方法。 The present invention proposes to combine the two high-efficiency approaches and specifically integrate them in the spectrum planning considering the modular combination method, which can generate huge economic and social benefits. This combination is actually a combination of transforming the centrifugal pump's type plan on the flow-lift level into a level module plan, thus turning the problem into a plan for the level module on the flow-lift level. The invention designs a method for mathematically planning the parameters of the stage module.

该数学规划方法是：将级数和比转数作为以流量和扬程为独立宗量的二元函数进行规划，将反馈减速比作为在效率等值面上与级函数分区间等价的连续可调独立变量也参与规划，形成前二元分区间等价的三元规划函数组 ((级数,反馈减速比)，比转数)。通过社会调査产生以效率等因素构造的运行成本函数和以结构、尺寸、材料、工艺等因素构造的制造成本函数，将两者之可比单位函数值相加作为目标函数，或者还增加产品美学设计要求等附加不等式组的约束，釆用经典数学规划方法或数值算法获得使目标函数取最小值的三元规划函数组的优化值域，据以建立水力模型和级模块系列规范。设计时，以扬程和流量为宗量，依据规范确定级数、比转数和反馈减速比，即可确定优化的离心泵级模块参数。当级模块釆用现有技术的后弯式叶轮时，其反馈减速比定义为出口相对速度的圆周分量与轮沿线速度之比，其值接近于 0，可忽略。 The mathematical programming method is: planning the series and specific revolutions as a binary function with flow and head as independent variables, and using the feedback reduction ratio as a continuous Tuning independent variables also participate in planning, forming an equivalent ternary programming function group ((stage number, feedback reduction ratio), specific revolution number) between the previous binary partitions. Through social surveys, an operating cost function constructed with factors such as efficiency and a manufacturing cost function constructed with factors such as structure, size, material, and process are added. The values of the comparable unit functions are added as the objective function, or product aesthetics are also increased. Constraints such as design requirements add additional inequalities. 釆 Use classical mathematical programming methods or numerical algorithms to obtain the optimal range of the ternary programming function group that minimizes the objective function. Based on this, a hydraulic model and a series of module specifications are established. When designing, the head and flow are taken as the parameters, and the number of stages, specific revolutions and feedback reduction ratio are determined according to the specifications, and the optimized centrifugal pump stage module parameters can be determined. When the stage module uses the backward curved impeller of the prior art, its feedback reduction ratio is defined as the ratio of the circumferential component of the relative exit speed to the line speed along the wheel. Its value is close to 0 and can be ignored.

在上述方法中，由于级数和反馈减速比在效率调节上的分区间等价性，因而在同一个等效率曲面上提供了一种可以互换互补的接续关系，级函数和比转数规划后的优化值域将因此而稀疏化。这种方法为离心泵的型谱规划和产品设计开辟了新的思维空间，在理论研究和设计实践中均具有重要意义。这种方法规划的级数和比转数的型谱系列最少，据以设计的离心泵不但效率高，而且空间利用率高、尺寸小、用材省，因而具有效率和成本的双重价值优势。理论上，其技术经济指标将是最高的。 In the above method, due to the equivalence between the partitions of the series and the feedback reduction ratio in the efficiency adjustment, a complementary connection relationship is provided on the same surface of equal efficiency. The resulting optimized range will be thinned accordingly. This method opens up a new thinking space for the centrifugal pump's spectrum planning and product design, which is of great significance in both theoretical research and design practice. This method plans the least number of series and specific rotations. The designed centrifugal pumps not only have high efficiency, but also have high space utilization, small size, and low material consumption, so they have the dual value advantages of efficiency and cost. In theory, its technical and economic indicators will be the highest.

需要特别指出.的是，泵效率和泵成本还不是最后的评价指标，最后的指标应该是机组的相应指标，再实际点应该是实际液流***的相应指标。从泵指标到最后的应用指标具有网状拓扑关系，必须运用矩阵运算来分析。例如，站在制造厂商的角度，如其产品是电机一离心泵机组，则作为一个乘性因子的泵效率的提高，显然是成正比地提高了机组效率。但这不是唯一的结果，因为还有另一个设计泛函对厂家的利益产生影响，那就是泵效率一电机功率一电机成本一机组成本的关系。因此，由泵成本、电机成本、二者联结成本之和构成的机组成本将同时受泵效率和泵成本两项指标的双重影响。考虑到电机成本在离心泵机组成本中的比重，大幅度提高泵效率对机组成本影响的幅度并不算小。由此可见，在技术经济评估中，泵指标只是一个宗矢量，在求解与实际经济利益相关的目标指标的系数矩阵中，存在着并应计及交叉作用因子的影响。对于最终用户来说，这种影响将从购买开支和运行费用两个方面攸关于其总拥有成本。对于生产厂商来说，同时获得性能提高和成本降低两项好处的设计无疑将提髙其产品的性价比而增大其市场竞争力。基于这种考虑，应该改造上述规划方法中的目标函数，将方法修订为：通过调查统计得到一个关联矩阵函数，将泵效率和泵成本换算成机组效和机组成本，据以构造机组的运行成本和制造成本，将两者的可比单位函数值相加作为目标函数进行规划来优化模块参数和产品设计。 It is important to point out that pump efficiency and pump cost are not the final evaluation indexes. The final index should be the corresponding index of the unit, and the actual point should be the corresponding index of the actual liquid flow system. From the pump index to the final application index, there is a network topology relationship, which must be analyzed using matrix operations. For example, from the perspective of a manufacturer, if its product is a motor-centrifugal pump unit, the increase in pump efficiency as a multiplicative factor obviously increases the unit efficiency in proportion. But this is not the only result, because there is another design function that affects the interests of manufacturers, that is, the relationship between pump efficiency-motor power-motor cost-unit cost. Therefore, the unit cost consisting of the sum of the cost of the pump, the cost of the motor, and the cost of the two will be affected by both the pump efficiency and the cost of the pump. Considering the proportion of the motor cost in the cost of the centrifugal pump unit, the magnitude of the significant increase in pump efficiency on the unit cost is not small. It can be seen that in the technical and economic evaluation, the pump index is just a piece of vector. In the coefficient matrix for solving the target index related to the actual economic benefits, the influence of cross-effect factors exists and should be taken into account. For end users, this impact will be related to their total cost of ownership in terms of both purchase and operating expenses. For manufacturers, a design that simultaneously benefits both performance and cost will undoubtedly increase the price / performance ratio of their products and increase their market competitiveness. Based on this consideration, the objective function in the above planning method should be transformed, and the method should be revised to obtain a correlation matrix function through survey statistics, convert the pump efficiency and pump cost into unit efficiency and unit cost, and construct the unit operation cost. And manufacturing costs, the values of the comparable unit functions of the two are added as an objective function to plan to optimize module parameters and product design.

本发明推崇多级结构和模块化组合的思想考虑了一个工艺前提，那就是精密模成型技术和其他现代制造技术所提供的新工艺，例如粉末冶金、压力精密铸造、压塑和注塑等。这些工艺较之传统工艺，可以在增加结构的空间复杂性的同时，还能大幅度提高生产效率和降低生产成本。例如，级段式叶导组合模块中的半开式叶轮、闭式叶轮盖、带外壳和叶轮腔的导轮、叶轮腔盖等零件，全部为开式或半开式工件，具有总体上能够釆用两合模成型的工艺优势，因 ffij能采用上述新工艺制造。本发明的系列流体力学上的特征设计，可能会增加模具的复杂性和模具成本，却棊本上不致于增加加工成本。.考虑到大批量生产时模具成本的分摊值实际上很低，因而釆用新工艺实施本发明的系列技术不但是发明人的愿望，而且是一种隐含的基本假设。如果采用传统工艺，本发明的一些设计将难以实施或成本反而升高。这不会影响本发明的实用性，因为社会迫切需求廉价而高效的离心泵产品，本发明的设计和适当先进的工艺相结合，就可以满足这种需求。 The invention respects the idea of multi-level structure and modular combination considering a process premise, that is, the new technology provided by precision molding technology and other modern manufacturing technologies, such as powder metallurgy, pressure precision casting, compression molding and injection molding. Compared with traditional processes, these processes can not only increase the spatial complexity of the structure, but also greatly improve production efficiency and reduce production costs. For example, the semi-open impeller, closed impeller cover, guide wheel with casing and impeller cavity, impeller cavity cover and other parts in the step-type impeller combination module are all open or semi-open workpieces, which have a general ability to优势 The advantages of using the two-clamp molding process, because ffij can use the new process described above. The series of fluid mechanics feature designs of the present invention may increase the complexity of the mold and the cost of the mold, but it will not increase the processing cost. Considering that the cost value of the mold is actually low in mass production, it is not only the inventor's wish, but also an implicit basic assumption that the new technology is used to implement the series of technology of the present invention. If traditional processes are used, some designs of the present invention will be difficult to implement or the cost will increase. This will not affect the practicability of the present invention, because society urgently needs cheap and efficient centrifugal pump products. The combination of the design of the present invention and appropriate advanced technology can meet this demand.

釆用本发明的模块化组合方法，可以将前述各类产品发明特征组合到模块中，还可以将其中的一些产品的发明特征与现有技术组合，这将形成许多种离心泵的新类型。仅仅使用模块化组合方法对现有技术的产品设计进行改造，也能够产生多种积极效果。关于这些组合的详细设计和组合效果的叙述，以及组合方法的应用方式，将包含或体现在结合附图的实施例说明中。附图说明釆 Using the modular combination method of the present invention, the aforementioned features of various types of products can be combined into a module, and the features of some of these products can also be combined with the existing technology, which will form many new types of centrifugal pumps. Modification of existing product designs using only a modular combination approach can also produce a variety of positive effects. The detailed design and description of the combination effect and the application method of the combination method will be included or embodied in the description of the embodiments with reference to the drawings. BRIEF DESCRIPTION OF THE DRAWINGS

下面结合附图对本发明所述的离心泵及其技术组合方法作进一步的详细说明。图 1是一种半开式高势比叶轮结构示意图。 The centrifugal pump and its technical combination method according to the present invention will be further described in detail below with reference to the drawings. Figure 1 is a schematic diagram of a semi-open type high potential ratio impeller.

图 2是一种闭式高势比叶轮结构示意图。 Figure 2 is a schematic diagram of a closed high potential ratio impeller.

图 3是一种锯齿形轮盘半开式高势比叶轮结构示意图。 FIG. 3 is a schematic diagram of a structure of a zigzag disc semi-open high potential ratio impeller.

图 4是一种锯齿形轮盘闭式高势比叶轮结构示意图。 FIG. 4 is a schematic diagram of a structure of a closed-type high potential ratio impeller with a sawtooth-shaped disc.

图 5是一种轴向入流预旋器结构示意图。 Fig. 5 is a schematic structural view of an axial inflow pre-spinner.

图 6是一种径向入流预旋器结构示意图。 Fig. 6 is a schematic structural diagram of a radial inflow pre-spinner.

图 7是一种带预旋器的半开式高势比叶轮结构示意图。 Figure 7 is a schematic diagram of a semi-open type high potential ratio impeller with a pre-spinner.

图 8是一种带均速岔道的半开式高势比叶轮结构示意图。 Figure 8 is a schematic diagram of a semi-open type high potential ratio impeller with a uniform speed bifurcation.

图 9是一种带均速岔道和预旋器的半开式髙势比叶轮结构示意图。 Figure 9 is a schematic diagram of a semi-open impeller ratio impeller with a uniform speed bifurcation and a pre-rotator.

图 10是一种带均速岔道和预旋器的高势比悬臂泵结构示意图。 Figure 10 is a schematic diagram of a high potential ratio cantilever pump with a uniform speed bifurcation and a pre-rotator.

图 11是一种出轴端内减摩驱动二相流冷却轴封流道结构示意图。 Fig. 11 is a schematic structural diagram of a two-phase flow cooling shaft seal flow channel with antifriction driving in the output shaft end.

图 12是一种前端腔内减摩驱动二相流 V形槽阻气间隙结构示意图。 FIG. 12 is a schematic diagram of the structure of a two-phase flow V-shaped air-blocking gap in the front end cavity to reduce friction.

图 13是一种半开式叶轮悬臂泵充气驱动装置及其连接示意图。 Fig. 13 is a schematic diagram of a semi-open impeller cantilever pump inflatable driving device and its connection.

图 14是一种闭式叶轮悬臂泵充气驱动装置及其连接示意图。 Fig. 14 is a schematic diagram of a closed impeller cantilever pump inflatable driving device and its connection.

图 15是一种向心导轮结构示意图。 FIG. 15 is a schematic structural diagram of a centripetal guide wheel.

图 16是一种高势比叶轮腔与向心导轮组合之转移段流道结构示意图。 FIG. 16 is a schematic diagram of a flow passage structure of a transfer section in which a high potential ratio impeller cavity and a centripetal guide wheel are combined.

图 17是一种闭式叶轮超减摩和导轮控制转移段流道之结构示意图。 FIG. 17 is a schematic structural diagram of a flow path of a closed impeller super friction reduction and guide wheel control transfer section.

图 18是一种中心蜗道分汇流变角度出管对称端盖结构示意图。 FIG. 18 is a schematic structural diagram of a symmetric end cap of a central volute branching and merging angle outlet pipe.

图 19是一种半开式叶轮与向心导轮组合之级段式模块结构示意图。 FIG. 19 is a schematic diagram of a stepped module structure of a combination of a semi-open impeller and a centrifugal guide wheel.

图 20是一种闭式叶轮与向心导轮组合之级段式模块结构示意图。 20 is a schematic diagram of a stepped module structure of a closed impeller and a centrifugal guide wheel.

图 21是一种减摩闭式叶轮与向心导轮组合之级段式模块结构示意图。 FIG. 21 is a schematic diagram of a stepped module structure of a friction reducing closed impeller and a centrifugal guide wheel.

图 22是一种半开式高势比叶轮与向心导轮组合之级段式模块结构示意图。 Fig. 22 is a schematic diagram of a stepped module structure of a combination of a semi-open type high potential ratio impeller and a centrifugal guide wheel.

图 23是一种闭式高势比叶轮与向心导轮组合之级段式模块结构示意图。 FIG. 23 is a schematic diagram of a stepped module structure of a combination of a closed high potential ratio impeller and a centripetal guide wheel.

图 24是一种预旋闭式高势比叶轮与向心导轮组合之级段式模块结构示意图。 FIG. 24 is a schematic diagram of a stepped module structure of a combination of a pre-spin closed high potential ratio impeller and a centrifugal guide wheel.

图 25是一种减摩闭式高势比叶轮与向心导轮组合之级段式模块结构示意图。 FIG. 25 is a schematic diagram of a stepped module structure of a combination of a friction reducing closed high potential ratio impeller and a centrifugal guide wheel.

图 26是一种减摩预旋闭式高势比叶轮与向心导轮组合之级段式模块结构示意图。图 27是一种超减摩预旋闭式高势比叶轮与向心导轮组合之级段式模块结构示意图。图 28是一种对称盖变角出管半开式轮向心增压离心泵结构示意图。 FIG. 26 is a schematic diagram of a stepped modular structure of a combination of a friction reduction pre-spinning type high potential ratio impeller and a centrifugal guide wheel. FIG. 27 is a schematic diagram of a stepped module structure of a combination of a super-friction reducing pre-spinning high potential ratio impeller and a centripetal guide wheel. FIG. 28 is a schematic structural diagram of a semi-open wheel centrifugal booster centrifugal pump with a symmetrical cover and variable angle outlet pipe.

图 29是一种对称盖变角出管闭式轮向心增压离心泵结构示意图。 FIG. 29 is a schematic structural diagram of a closed-type centrifugal centrifugal centrifugal pump with a symmetric cover and variable angle outlet tube.

图 30是一种对称盖变角出管减摩闭式轮向心增压离心泵结构示意图。 FIG. 30 is a schematic structural diagram of a symmetric cover variable angle outlet tube anti-friction closed-wheel centrifugal booster centrifugal pump.

图 31是一种对称盖变角出管高势比半幵式轮向心增压离心泵结构示意图。 FIG. 31 is a schematic structural diagram of a semi-concentric wheel centrifugal booster centrifugal pump with a high potential ratio of a symmetric cover variable angle outlet pipe.

图 32是一种对称盖变角出管高势比闭式轮向心增压离心泵结构示意图。图 33是一种对称盖变角出管预旋高势比闭式轮向心增压离心泵结构示意图。 FIG. 32 is a schematic structural diagram of a closed-wheel centrifugal booster centrifugal pump with a high potential ratio of a symmetric cover variable angle outlet pipe. FIG. 33 is a schematic structural diagram of a closed-type centrifugal centrifugal centrifugal pump with a pre-spinning and high-potential ratio of a symmetric cover with variable angle outlet pipe.

图 34是一种对称盖变角出管减摩高势比闭式轮向心增压离心泵结构示意图。 FIG. 34 is a schematic structural diagram of a closed-wheel centrifugal centrifugal centrifugal pump with a symmetric cover and variable angle outlet tube for reducing friction and high potential ratio.

图 35是一种对称盖变角出管减摩预旋高势比闭式轮向心增压离心泵结构示意图。图 36是一种对称盖变角出管超减摩预旋高势比闭式轮向心增压离心泵结构示意图。图 37是一种对称盖变角出管半开式轮向心增压多级离心泵结构示意图。 FIG. 35 is a structural schematic diagram of a closed-end centrifugal pump with a symmetrical cover and a variable angle outlet pipe for reducing friction and pre-spinning with high potential ratio. FIG. 36 is a schematic structural diagram of a closed-type centrifugal pump with a closed cover and a centrifugal pump with a superimposed anti-friction pre-spinning and high-potential ratio. FIG. 37 is a schematic structural diagram of a semi-open wheel centrifugal booster multistage centrifugal pump with a symmetrical cover and variable angle outlet pipe.

图 38是一种对称盖变角出管闭式轮向心增压多级离心泵结构示意图。 FIG. 38 is a schematic structural diagram of a closed-wheel centrifugal multi-stage centrifugal pump with a symmetrical cover and variable angle outlet pipe.

图 39是一种对称盖变角出管减摩闭式轮向心增压多级离心泵结构示意图。 Figure 39 is a schematic structural diagram of a symmetric cover variable angle outlet tube anti-friction closed-wheel centrifugal booster multistage centrifugal pump.

图 40是一种对称盖变角出管高势比半开式轮向心增压多级离心泵结构示意图。 FIG. 40 is a schematic structural diagram of a semi-open type centrifugal booster pump with a high potential ratio of a symmetrical cover and variable angle outlet pipe.

图 41是一种对称盖变角出管高势比闭式轮向心增压多级离心泵结构示意图。 FIG. 41 is a schematic structural diagram of a closed-wheel centrifugal multi-stage centrifugal pump with a high potential ratio of a symmetric cover variable angle outlet pipe.

图 42是一种对称盖变角出管预旋高势比闭式轮向心增压多级离心泵结构示意图。图 43是一种对称盖变角出管减摩高势比闭式轮向心增压多级离心泵结构示意图。图 44是一种对称盖变角出管减摩预旋高势比闭式轮向心增压多级离心泵结构示意图。图 45 是一种对称盖变角出管超减摩预旋高势比闭式轮向心增压多级离心泵结构示意图 46 是一种对称盖变角出管预旋高势比半开式叶导轮向心增压多级离心泵结构示意 Fig. 42 is a structural schematic diagram of a closed-end centrifugal booster pump with a high-potential ratio and a pre-rotation of a symmetrical cover with variable angle outlet pipe. FIG. 43 is a schematic structural diagram of a closed-wheel centrifugal multistage centrifugal pump with a symmetric cover and variable angle outlet pipe for reducing friction and high potential ratio. Fig. 44 is a structural schematic diagram of a closed-end centrifugal pump with a centrifugal pump with a symmetrical cover and variable angle outlet pipe for reducing friction and pre-spinning with high potential ratio. Figure 45 is a schematic diagram of the structure of a symmetrical cover variable angle outlet pipe with super friction reducing pre-spinning high potential ratio closed wheel centripetal booster multistage centrifugal pump 46 The structure of the centrifugal pump

发明实施例 Invention Examples

图 1、图 2、图 3、图 4分别表示高势比叶轮的 4种主要类型及其结构。 Figure 1, Figure 2, Figure 3, and Figure 4 show the four main types of high potential ratio impellers and their structures, respectively.

参照图 1，图中给出了半开式高势动比叶轮的一种结构。其中， 1是叶轮轮盘， 2是叶轮轴孔， 3是叶轮轴套， 4是吸入室， 5是叶片， 6是叶槽流道中部， 7是流道入口， 8是流道出口。 Referring to FIG. 1, a structure of a semi-open type high potential impeller is shown. Among them, 1 is the impeller disc, 2 is the impeller shaft hole, 3 is the impeller shaft sleeve, 4 is the suction chamber, 5 is the blade, 6 is the middle of the flow channel of the blade groove, 7 is the flow channel inlet, and 8 is the flow channel outlet.

半开式高势比叶轮是一个圆盘形零件，釆用模成型工艺一体化制造。其中心有轴孔 2 和轴套 3，用于与转轴装配（可设置键槽）。轴套外面是环形吸入室 4，其底面或者是使液流连续转向的旋转曲面，当或者装入预旋器时，该曲面将由造形相同的预旋器轮圈表面代替。叶片 5为 L形，前中部呈径向走势，尾部朝反切向弯曲，尾部外侧为光滑的渐开弧线柱面或槽面。 6〜12片完全相同的 L形叶片在轮盘上均匀分布，叶片间形成均布的叶槽流道。该流道的入口 7和中部 6较为宽阔，在到达出口 8之前截面积逐渐减小并转向，流体被加速和改变方向，最后以较大的相对速度和很小的出口角流出叶轮，液流出口绝对速度因而大幅度减小，势动比显著提高。液流出口后，受到内侧柱面或槽面附壁效应约束，在出口间隔区形成向内弯曲的均布流线，具有均匀的径向分量与切向分量，其比值不随圆心角改变。这等效于连续开口的效果，但完全没有回流。 The semi-open type high potential ratio impeller is a disc-shaped part. It has a shaft hole 2 and a shaft sleeve 3 in the center for assembly with the shaft (key slot can be set). The outer surface of the sleeve is the annular suction chamber 4. The bottom surface is a rotating curved surface that continuously turns the liquid flow. When the pre-spinner is installed, the curved surface will be replaced by the pre-spinner rim surface of the same shape. The blade 5 is L-shaped, with a radial direction at the front and middle, a tail curved in the opposite direction, and a smooth involute arc cylindrical or grooved surface outside the tail. Six to twelve identical L-shaped blades are evenly distributed on the wheel disc, and uniformly distributed groove channels are formed between the blades. The inlet 7 and the middle 6 of the flow channel are relatively wide, and the cross-sectional area gradually decreases and turns before reaching the outlet 8. The fluid is accelerated and changed direction, and finally flows out of the impeller at a relatively large speed and a small outlet angle. As a result, the absolute speed of exports has been greatly reduced, and the momentum ratio has increased significantly. After the liquid flow exits, it is constrained by the inner wall or groove surface Coanda effect, forming inwardly curved uniformly distributed flow lines in the exit space, with uniform radial and tangential components, and its ratio does not change with the center angle. This is equivalent to the effect of a continuous opening, but there is no backflow at all.

叶轮各流道的出口面积与设计流量成正比，与设计出口相对速度和叶片数成反比，设计相对速度等于叶轮出口处的圆周速度与反馈减速比参数 K的乘积。用这种方法确定的设计参数与实测值吻合性好，因为其中没有回流干扰。 The exit area of each impeller flow channel is proportional to the design flow, and is inversely proportional to the design exit relative speed and the number of blades. The design relative speed is equal to the product of the peripheral speed at the exit of the impeller and the feedback reduction ratio parameter K. The equipment determined in this way The measured parameters are in good agreement with the measured values, because there is no backflow interference.

按照前述讨论确定参数 K, 离心泵将具有良好的调节特性、效率特性和抗气蚀特性。参照图 2，图中给出了闭式高势比叶轮的一种结构。其中 9是固定盖板的铆钉， 10是叶轮前盖。在半开式高势比叶轮的基础上加装前盖 10将叶轮封闭，就构成闭式高势比叶轮。闭式高势比叶轮流道弯曲度大，出口处狭窄，难于用传统的铸造工艺制造，采用半开式叶轮底盘铆接前盖的工艺方法却简单易行。该方法要求，在每片 L形叶片之肘部宽阔处开 2〜3个铆钉孔，用沉头或扁平头铆钉 9将前盖板与半开式轮盘零件铆接。前盖板采用模压成型工艺制造，具有与半开式轮盘密配合的内表面和符合精度要求的旋转曲面外表面。为保障动平衡，处于同一相对位置的铆钉孔应该在一个同心圆上，并处于叶片中线位置。可以将铆钉孔改为螺孔，用防松螺钉紧固前盖板。也可以釆用点焊工艺连接前盖板。闭式叶轮的半开式底盘的技术特征和设计要求与半开式叶轮相同，两者使用特性也基本相同。闭式叶轮的优越性在于，其叶槽流道没有开放面的涉外摩擦和湍流干扰，因而更接近理论特性。并且，闭式叶轮装入叶轮腔后，能形成两个对叶轮流道封闭的端腔，采用双端腔内减摩技术后，其轮盘摩擦的绝大部分将被消除，具有很高的内机械效率。参照图 3，图中给出了锯齿形轮盘半开式高势比叶轮的一种结构。 11是轮盘的齿沿轮廓线。将半开式高势比叶轮圆形轮盘的叶片之外的部分去掉，轮盘即成为锯齿形。图中线段 11 是一个叶片尾尖到后一个叶片外沿的齿形轮廓线段，为出口法平面上的一条直线。该线段处的底盘被减薄，形成尖锐的齿尖，以产生整流效果。为了保持齿尖和叶片尾尖的强度，这种叶轮需要高强材料制造。 Determine the parameter K according to the foregoing discussion. The centrifugal pump will have good regulation characteristics, efficiency characteristics and anti-cavitation characteristics. Referring to Figure 2, a structure of a closed high potential ratio impeller is shown. Among them, 9 are rivets for fixing the cover plate, and 10 is the front cover of the impeller. On the basis of the semi-open type high potential ratio impeller, a front cover 10 is added to close the impeller to form a closed type high potential ratio impeller. The closed high potential is more curved than the impeller flow channel, and the exit is narrow, which is difficult to manufacture by traditional casting process. The process of riveting the front cover with the semi-open impeller chassis is simple and easy. This method requires that 2 to 3 rivet holes are opened in the wide elbow of each L-shaped blade, and the front cover plate and the semi-open type roulette part are riveted with a countersunk or flat head rivet 9. The front cover is manufactured by a compression molding process. It has an inner surface that closely fits the half-open wheel and an outer surface of the rotating curved surface that meets the accuracy requirements. To ensure dynamic balance, the rivet holes in the same relative position should be on a concentric circle and at the center line of the blade. The rivet hole can be changed to a screw hole, and the front cover is fastened with a lock screw. The front cover can also be connected using spot welding. The technical characteristics and design requirements of the semi-open chassis of the closed impeller are the same as those of the semi-open impeller, and the operating characteristics of the two are basically the same. The advantage of the closed impeller is that its channel has no external friction and turbulence interference from the open surface, so it is closer to the theoretical characteristics. In addition, after the closed impeller is installed in the impeller cavity, two end cavities that are closed to the impeller flow channel can be formed. After the double-end cavity anti-friction technology is adopted, most of the disc friction will be eliminated, which has a very high Within mechanical efficiency. Referring to FIG. 3, a structure of a zigzag disc half-open high potential ratio impeller is shown. 11 is the contour of the teeth of the wheel. After removing the part of the blade of the semi-open type high potential impeller circular wheel disc, the wheel disc becomes zigzag. The line segment 11 in the figure is a tooth-shaped contour line segment from the tip of the blade to the outer edge of the subsequent blade, which is a straight line on the exit normal plane. The chassis at this line segment is thinned to form a sharp tooth tip to produce a rectifying effect. In order to maintain the strength of the tooth tip and blade tip, this impeller requires high-strength materials.

, 锯齿形轮盘高势比叶轮具有较高的效率。在一般情况下，叶轮出口外的轴向约束功能已为叶轮腔所替代，轮盘边沿的曲边三角形小块因为两面摩擦而成为徒增损耗的赘物，其外侧以牵连速度与端腔介质摩擦，消耗叶轮比功，其内侧以出口相对速度与液流摩擦，消耗液流比能。去掉这些小块后，相应位置只存在液流与腔壁的摩擦，只消耗液流比能，液流的绝对速度也小于牵连速度，这显然能够提高效率。 , Zigzag wheel disc has higher potential than the impeller, which has higher efficiency. In general, the axial restraint function outside the impeller outlet has been replaced by the impeller cavity. The curved triangular small pieces on the edge of the disc become frictional losses due to friction on both sides. The friction consumes the specific work of the impeller, and the inside of the friction friction with the liquid flow at the outlet relative speed consumes the specific energy of the liquid flow. After removing these small pieces, only the friction between the liquid flow and the cavity wall exists at the corresponding position, and only the specific energy of the liquid flow is consumed. The absolute speed of the liquid flow is also less than the implication speed, which can obviously improve the efficiency.

锯齿形轮盘提高效率的幅度分析如下：依据速度三角形，去掉小三角块后的摩擦速度是其一条短边，而原来两面摩擦的速度是牵连速度长边和相对速度短边，产生的损耗是两者损耗之和。考虑到损耗与速度平方成正比，以及和 β ₂ 0的条件，则单位面积上的损耗减小率为（（1²+0.5²)—（1一 0.5 ) ²) / ( 1²+0.5²) = 80%。又考虑到损耗力矩的微分与单位面积上的摩擦力、圆周长度和半径的乘积成正比，积分后是半径的 5次函数关系，因而节能的效益应该是可观的。举例来说，设出口的径向宽度为半径的 10%，则切去的这些小块面积上的摩擦损耗的降低相对于轮盘后端腔摩擦损耗的降低比为 The magnitude of the efficiency increase of the zigzag wheel is as follows: According to the speed triangle, the friction speed after removing the small triangle block is one of its short sides, and the speed of the original two-sided friction is the involved speed long side and the relative speed short side. Sum of the two losses. Considering that the loss is proportional to the square of speed and the condition of β ₂ 0, the loss reduction rate per unit area is ((1 ² +0.5 ² )-(1-0.5) ² ) / (1 ² +0.5 ² ) = 80%. Considering that the differential of the loss moment is proportional to the product of the friction force per unit area, the length of the circumference, and the radius, the integral is a fifth-order function of the radius, so the energy saving benefit should be considerable. For example, if the radial width of the outlet is 10% of the radius, the reduction ratio of the friction loss on the area of these small pieces relative to the friction loss reduction at the rear end of the disc is

0.8 (0.8190-0.7738) /0.2= 18.1 % 0.8 (0.8190-0.7738) /0.2 = 18.1%

又设后端腔轮盘摩擦大约使泵效率下降 3〜5 %，则泵效率大约提高 0.5〜1 %。锯齿形轮盘的设计目标是轮盘减摩，在没有内减摩装置时能产生上述效益。由于内减摩装置的作用更为显著，在装有该装置时不宜设计这种轮盘的叶轮，因为它会使充气直径比减小而干扰该装置的工作，所得将不偿所失。参照图 4，图中给出了锯齿形轮盘闭式高势比叶轮的一种结构。将闭式高势比叶轮的半开式圆形轮盘及其盖板的叶片之外的部分去掉，整个叶轮即成为锯齿形。图中线段 12 是一个叶片尾尖到后一个叶片外沿的齿形轮廓线段，为出口法平面上的一条直线。其齿沿削尖整流及相应的强度要求与图 3所示半开式叶轮相同。

It is also set that the friction of the rear-end cavity wheel disc reduces the pump efficiency by about 3 to 5%, and the pump efficiency is increased by about 0.5 to 1%. The design goal of the zigzag roulette is to reduce the friction of the roulette, which can produce the above-mentioned benefits when there is no internal friction reduction device. Because the effect of the internal friction reduction device is more significant, it is not suitable to design the impeller of such a disc when the device is installed, because it will reduce the inflation diameter ratio and interfere with the operation of the device, and the gain will be lost. Referring to FIG. 4, a structure of a zigzag disc closed high potential ratio impeller is shown. The closed-type high potential ratio impeller is removed from the semi-open circular disc and the blades of the cover plate, and the entire impeller becomes zigzag. Line segment 12 in the figure is a tooth-shaped contour line segment from the tip of the blade to the outer edge of the subsequent blade, which is a straight line on the exit normal plane. Its tooth-sharpened rectification and corresponding strength requirements are the same as those of the semi-open impeller shown in FIG. 3.

锯齿形轮盘闭式高势比叶轮的减摩作用是双面的，按照上述例子的开口口径比来分析，其后轮盘和前盖的摩擦损耗均能降低 18.1 %，泵效率因而大约能提高 1〜2%。基于同样的理由，这种叶轮仅限于在没有内减摩装置的离心泵中使用。参照图 5，图中给出了轴向入流预旋器的一种结构。其中， 13是叶轮吸入室边际， 14 是下轮圈， 15是上轮圈， 16是弹性帆式叶片， 17是下轮圈的轴面投影， 18是叶片上接近下轮圈下底圆的点， 19是接近上轮圈下底圆的点， 20是刚性肋条。 The anti-friction effect of the zigzag disc closed high potential ratio impeller is double-sided. According to the analysis of the aperture ratio of the above example, the friction loss of the rear wheel and the front cover can be reduced by 18.1%, so the pump efficiency can be approximately Increase by 1 ~ 2%. For the same reason, this impeller is limited to use in centrifugal pumps without internal friction reduction. Referring to Figure 5, a structure of an axial inflow pre-spinner is shown. Among them, 13 is the margin of the suction chamber of the impeller, 14 is the lower rim, 15 is the upper rim, 16 is the elastic sail blade, 17 is the axial projection of the lower rim, and 18 is the blade near the bottom circle of the lower rim. Point 19 is a point near the bottom circle of the upper rim, and 20 is a rigid rib.

轴向入流预旋器由两节轮圈和若干片弹性帆式叶片装配而成。轮圈 14和 15滑套在叶轮轴套上，能各自独立转动，其表面互相吻接成使液流连续转向的旋转曲面。帆式叶片的片数少于叶轮叶片数或者还是其约数，以对流道的约束度不致太低而摩擦面积比又不致太大为宜。帆式叶片 16成曲边三角形，其直线边前沿悬挂于刚性肋条 20上，肋条径向固定在叶轮叶片或前盖的入口处。帆式叶片的曲线边上与两轮圈之下底圆接近的两点 18 和 19分别固定在该两圆周上，形成与刚性肋条相对的拉作用点。 The axial inflow pre-spinner is assembled by two rims and several elastic sail blades. The rims 14 and 15 are sleeved on the impeller shaft sleeve, which can rotate independently, and the surfaces thereof kiss each other to form a rotating curved surface for continuously turning the liquid flow. The number of sail-type blades is less than the number of impeller blades or is still a submultiple, so that the confinement of the flow channel is not too low and the friction area ratio is not too large. The sail blade 16 forms a curved triangle, and its straight edge is suspended from the rigid rib 20, and the rib is fixed radially at the entrance of the impeller blade or the front cover. Two points 18 and 19 on the curved edge of the sail blade close to the bottom circle under the two rims are respectively fixed on the two circumferences to form a pulling action point opposite to the rigid rib.

叶片尾尖部 18 具有一定的抗弯强度，固定时使其具有指向性，以大体保持预旋器流道出口方向与叶轮流道入口方向的一致。工作时，叶轮通过刚性肋条牵动叶片和轮圈一道旋转，弹性帆式叶片自适应地变形成螺桨形，从入口到出口全程保持与流线相切的状态，这是叶片张应力、弯应力和液流反作用力及离心力自动平衡的结果。在稳态运行中，弹性帆式叶片的自由曲线边和自由直线边将变形成空间曲线，整个叶片及其边际线相对于轮圈和叶轮的邻接部位将保持静止。在工况变动等各类动态过程中，叶片将自适应改变形状和各部分的应力，与周围的相对位置也将发生变动，以与液流惯性动反力的变动相平衡，平衡后保持与流线相切状态，两个轮圈随之调整各自的角度。这里不存在配合精度的要求，因为小的缝隙并不影响对液流作用的整体效果，而小的挤压产生的移动阻滞力也会因随机扰动而得到释放，动态调整因而总是能够精确地完成。 The blade tail tip 18 has a certain bending strength, and has a directivity when fixed, so as to substantially keep the exit direction of the pre-spinner channel consistent with the entrance direction of the impeller channel. During operation, the impeller rotates the blade and the rim together through the rigid ribs, and the elastic sail-shaped blade adaptively changes into a propeller shape, and maintains a state tangent to the streamline from the entrance to the exit. This is the blade's tensile stress and bending stress. And fluid flow reaction force and centrifugal force automatically balance the result. In steady state operation, the free-curve edge and free-straight edge of the elastic sail blade will change into a space curve, and the entire blade and its marginal line will remain stationary relative to the adjacent parts of the rim and the impeller. During various dynamic processes such as working condition changes, the blade will adaptively change the shape and stress of each part, and the relative position with the surroundings will also change to balance with the fluctuation of the inertial dynamic reaction force of the liquid flow. The streamlines are tangent, and the two wheels adjust their angles accordingly. There is no requirement for matching accuracy, because the small gap does not affect the overall effect of the liquid flow, and the movement blocking force generated by the small squeeze will be released due to random disturbances, and the dynamic adjustment can always be accurate carry out.

轴向入流预旋器安装在轴向入流离心泵的吸入室中，叶轮的吸入室因而必须开具一个圆环柱形的容空，以便装入预旋器。容空的中心是叶轮轴套，其外表面为圆柱面或台阶圆柱面，用于滑套预旋器的轮圈。轮圈的旋转曲面将代替叶轮中心的旋转曲面起转向导流作用。预旋器的负荷很小，对帆式叶片的强度没有太高的要求。 The axial inflow pre-spinner is installed in the suction chamber of the axial in-flow centrifugal pump. Therefore, the suction chamber of the impeller must be provided with a circular cylindrical space to fit the pre-spinner. The center of the empty space is the impeller shaft sleeve, whose outer surface is a cylindrical surface or a step circle Cylindrical, for wheel rims of sliding sleeve prespinners. The rotating surface of the rim will replace the rotating surface in the center of the impeller to serve as a guide. The load of the pre-rotator is very small, and the strength of the sail blade is not too high.

预旋器弹性帆式叶片自适应变形的效果是：液流总是与叶片相切地进入，并在叶片法向力作用下沿程连续地改变速度大小和方向，在出口端，其速度方向总是正对着叶轮入口的。因此，叶轮入口和预旋器入口均不会发生撞击湍流，叶轮入口面积也能得到最有效的利用。当流量改变时，这些特性保持不变。参照图 6，图中给出了一种径向入流预旋器的结构。其中， 21是下轮圈， 22是上轮圈， 23是刚性肋条， 24是弹性帆式叶片， 25是肋条支架及轴套， 26是下轮圈的轴面投影， 27 是叶片上接近下轮圈上底面的点， 28 是刚性肋条的轴面投影， 29 是叶片上接近上轮圈上底面的点， 30是上轮圈的轴面投影。 The effect of self-adaptive deformation of the pre-rotor elastic sail blade is that the liquid flow always enters tangentially to the blade, and continuously changes the speed magnitude and direction along the course under the normal force of the blade. At the exit end, its speed direction It is always facing the impeller entrance. Therefore, impingement turbulence does not occur at the impeller inlet and the pre-spinner inlet, and the area of the impeller inlet can also be used most effectively. As the flow changes, these characteristics remain the same. Referring to Fig. 6, the structure of a radial inflow pre-spinner is shown. Among them, 21 is a lower rim, 22 is an upper rim, 23 is a rigid rib, 24 is an elastic sail blade, 25 is a rib bracket and a bushing, 26 is a projection of the axial surface of the lower rim, and 27 is a blade close to the bottom The point on the bottom surface of the rim, 28 is the axial plane projection of the rigid rib, 29 is the point on the blade close to the upper bottom surface of the upper rim, and 30 is the axial plane projection of the upper rim.

径向入流预旋器由带轴套的圆盘形肋条支架 25、下轮圈 21、上轮圈 22和若干条刚性肋条 23及若干片曲边三角形弹性帆式叶片 24装配而成。其叶片数的确定、叶片的变形工作原理均与轴向入流预旋器相同。所不同之处主要有三点：第一，液流是从圆柱面入口径向流入和从平面环形出口轴向流出的，曲边三角形叶片平行于转轴的直线边是入口边，该边悬挂在刚性肋条上。第二，弹性帆式叶片的曲线边与两节轮圈的上底面圆邻近的点 27、 29固定在两轮圈上，轮圈通过该两点提供平衡拉力。第三，轮圈 21、 22滑套在支架轴套上，其中心孔的孔径较叶轮轴套外径小。 The radial inflow pre-spinner is assembled by a disc-shaped rib bracket 25 with a sleeve, a lower rim 21, an upper rim 22, a plurality of rigid ribs 23, and a plurality of curved triangular elastic sail blades 24. The number of blades and the deformation principle of the blades are the same as those of the axial inflow pre-spinner. There are three main differences: First, the fluid flows radially from the cylindrical inlet and axially from the flat annular outlet. The straight edge of the curved triangular blade parallel to the axis of rotation is the inlet edge, and this edge is suspended from rigidity. On the ribs. Second, the points 27, 29 adjacent to the curved sides of the elastic sail blades and the upper and bottom surface circles of the two rims are fixed to the two rims, and the rims provide balanced tension through these two points. Third, the rims 21 and 22 are sleeved on the support sleeve, and the diameter of the central hole is smaller than the outer diameter of the impeller sleeve.

图中，弹性帆式叶片 24悬挂在刚性肋条 28之上，肋条则直接固定在带轴套的圆盘支架 25 上，其轴套静配合在转轴上，为圆盘支架和刚性肋条提供驱动力。这种结构具有部件整体性和装配独立性的优势，并且装配时其轴套与叶轮轴套是轴向压紧的，机器的整体轴向定位性能良好，转轴的密封性和刚性也因此而提高。 In the figure, the elastic sail blades 24 are suspended on a rigid rib 28, and the ribs are directly fixed on a disc bracket 25 with a sleeve, and the sleeve is statically fitted on the rotating shaft to provide a driving force for the disc bracket and the rigid rib. . This structure has the advantages of component integrity and assembly independence, and its shaft sleeve and impeller shaft sleeve are pressed axially during assembly, the overall axial positioning performance of the machine is good, and the seal and rigidity of the shaft are improved as a result. .

运转时，圆盘支架 25和刚性肋条 28与转轴同步旋转。当进入预旋器的液流速度的圆周分量不够时，帆式叶片如图中所示向后张悬，其入口角度自适应地随流线改变，使叶片入口与流线相切。叶片的法向约束力在圆周面上为液流提供圆周向加速和向心加速的分力，使液流进入同步旋转状态，并且还提供抵消或部分抵消离心力的反径向驱动，预旋器输出轴功增加液流比能。液流轴向速度分量的增加则是旋转曲面反作用力驱动的结果，理论上不存在功能转换。液流进入某个径向坐标位置以后，其圆周速度分量将连续地大于同步速度，这时，液流将输出比能对叶片做功，其作用力有助于平衡叶片前部的拉应力的切向分量，使其根部保持与转轴垂直的状态，从而保持较大的流道截面积。叶片曲线边拉力平衡点 27、 29 的位置选择有利于在负荷最大时使两节轮圈与叶轮之间以及它们彼此之间发生最大的角位移，以满足应力加大的需要。 During operation, the disc holder 25 and the rigid rib 28 rotate in synchronization with the rotation shaft. When the circumferential component of the velocity of the liquid flow entering the pre-rotator is not sufficient, the sail-type blade hangs backward as shown in the figure, and its inlet angle adaptively changes with the streamline, so that the blade inlet is tangent to the streamline. The normal binding force of the blades provides the circumferential acceleration and the centripetal acceleration component of the liquid flow on the circumferential surface, so that the liquid flow enters a synchronous rotation state, and also provides an anti-radial drive to offset or partially offset the centrifugal force. Output shaft work increases fluid flow specific energy. The increase of the axial velocity component of the liquid flow is the result of the reaction force driven by the rotating curved surface, and there is no theoretical function conversion. After the liquid flow enters a certain radial coordinate position, its peripheral velocity component will be continuously greater than the synchronous speed. At this time, the liquid flow will output specific energy to do work to the blade, and its force will help to balance the shearing of the tensile stress at the front of the blade. Direction component, keeping its root perpendicular to the axis of rotation, thereby maintaining a larger cross-sectional area of the flow channel. The choice of the position of the blade curve side tension balance points 27, 29 is conducive to the maximum angular displacement between the two rims and the impeller and between them when the load is maximum, so as to meet the needs of increased stress.

当进入预旋器的液流速度的切向分量超过牵连速度时，帆式叶片 24将向前张悬，.与图中所示的弯曲方向相反，液流输出比能对叶片做功，预旋器进入水轮机工作状态。这时的力学分析是类似的，所不同的是法向力和应力的圆周分量的方向相反。在动态过程中，叶片自适应地发生弹性变形，两节轮圈发生相对移动。这种调整运动在小的机械摩擦阻碍下也能迅速完成，因为微小的扰动和振动总是存在的，足以帮助克服摩擦力。 When the tangential component of the velocity of the liquid flow entering the pre-rotator exceeds the implication speed, the sail blade 24 will hang forward. Contrary to the bending direction shown in the figure, the liquid flow output ratio can do work on the blade, pre-spin The turbine enters the working state of the turbine. At this time The mechanical analysis is similar, except that the circumferential components of normal force and stress are in opposite directions. During the dynamic process, the blade adaptively deforms elastically, and the two rims move relative to each other. This adjustment movement can also be done quickly under the hindrance of small mechanical friction, because small disturbances and vibrations are always present enough to help overcome friction.

径向入流预旋器主要安装在半开式向心导轮的中心位置，与下一级叶轮的吸入室紧密相连。实际上，向心导轮和预旋器的组合使得后一级叶轮根本就不需要吸入室，本发明的多级泵实施例中体现了这种设计。参照图 7，在作为预旋器应用的一个例子，图中给出了一种带预旋器的半开式高势比叶轮结构，作为将轴向入流预旋器与高势比叶轮组合的一种实施例。其中， 31是半开式高势比叶轮， 32是预旋器的下轮圈， 33是预旋器的帆式叶片， 34是预旋器的刚性肋条， 35 是预旋器的上轮圈。 The radial inflow pre-rotator is mainly installed at the center position of the semi-open centrifugal guide wheel, and is closely connected with the suction chamber of the next stage impeller. In fact, the combination of the centrifugal guide wheel and the pre-rotator makes the latter stage impeller need no suction chamber at all, and this design is embodied in the multi-stage pump embodiment of the present invention. Referring to FIG. 7, as an example of application as a pre-rotator, the figure shows a semi-open type high potential ratio impeller structure with a pre-rotator as a combination of an axial inflow pre-rotator and a high potential ratio impeller. An embodiment. Among them, 31 is a semi-open high potential ratio impeller, 32 is the lower rim of the pre-spinner, 33 is a sail blade of the pre-spinner, 34 is a rigid rib of the pre-spin, and 35 is an upper rim of the pre-spin .

如图所示，预旋器装在高势比叶轮 31 的吸入室中。吸入室为叶轮中心轴套以外和叶片根部以内的一个圆环柱形容腔。将预旋器的两节轮圈 32和 35滑套（动配合）在叶轮轴套上，将 4条刚性肋条相间径向紧固在 8片叶轮叶片中的 4片的根部之入口面上，即完成组装。图中预旋器的叶片数 4是叶轮叶片数 8的约数。 As shown in the figure, the pre-rotator is installed in the suction chamber of the high potential ratio impeller 31. The suction chamber is a circular cylindrical shaped cavity outside the impeller's central sleeve and inside the blade root. The two sections of the pre-spinner 32 and 35 slip sleeves (moving fit) are fixed on the impeller sleeve, and the four rigid ribs are radially fastened to the entrance surface of the root of four of the eight impeller blades. The assembly is complete. In the figure, the number of blades of the pre-rotator 4 is a sub-multiple of the number of blades of the impeller 8.

装有预旋器的高势比叶轮可以用于单级泵，也可以用于多级泵，作为整体装配到离心泵中。预旋器是本发明叶轮流道 90度入口角设计的配套部件，其自适应预旋机制对于改善泵的入口水力特性和抗气蚀特性能够发挥重要作用，尤其是当泵偏离设计工况运行时，其自适应机制对于提高泵的运行效率和延长泵的使用寿命具有特别重要的意义。参照图 8，作为遏制相对涡旋和全面改善叶轮的运行特性的均速岔道技术的一个实施例，图中给出了带均速岔道的高势比叶轮的示意结构。其中， 36是 L形叶片， 37是均速梳叶、 38是近压力面岔道， 39是近吸力面岔道， 40是岔道出口， 41是岔道入口， 42是岔道出口附近的叶槽加速区， 43是叶槽出口外的单边约束速度整理区。 The high potential ratio impeller with pre-spinner can be used for single-stage pumps or multi-stage pumps, and it can be assembled into the centrifugal pump as a whole. The pre-spinner is a supporting component of the design of the 90-degree inlet angle of the impeller flow channel of the present invention, and its adaptive pre-spin mechanism can play an important role in improving the inlet hydraulic characteristics and anti-cavitation characteristics of the pump, especially when the pump runs away from the design conditions. At this time, its adaptive mechanism is of special significance for improving the operating efficiency of the pump and extending the service life of the pump. Referring to FIG. 8, as an example of an average speed bifurcation technology that suppresses the relative vortex and comprehensively improves the operating characteristics of the impeller, the schematic structure of a high potential ratio impeller with a uniform speed bifurcation is shown in the figure. Among them, 36 is an L-shaped blade, 37 is a uniform-speed combing blade, 38 is a near-pressure surface bifurcation, 39 is a near-suction surface bifurcation, 40 is a bifurcation exit, 41 is a bifurcation entrance, and 42 is a blade groove acceleration area near the bifurcation exit. 43 is a unilaterally constrained speed finishing area outside the leaf groove outlet.

如图所示，高势比叶轮的圆形或锯齿形轮盘上旋转对称地布设有设计数量的 L形叶片，在 L形叶片间的叶槽流道前中部宽阔处，顺势布设有 2片均速梳叶即产生 3个均速岔道。 38 为近压力面岔道， 39 为近吸力面岔道，两者之间是中间岔道。均速梳叶前中部亦呈径向走势，尾部光滑转向，顺流线方向指向叶槽加速段。梳叶在相对速度较低的前提下对液流形成密集约束，其法向力的沿途积分结果将包含一个剪力矩，该力矩的作用方向与相对涡旋的方向相反，因而构成遏制涡旋的重要因素之一。更重要的机制在于，由于岔道入口如图中 41接近而未达到叶槽入口，由于岔道出口如图中 40接近而未达到叶槽出口，且其出口截面积是按照一个经优化试验得到的经验系数分配的，其近压力面岔道分配较多而近吸力面岔道分配较少，因而前者的沿途压力一路较低而后者的沿途压力一路较高，这种压力场梯度分布的差异，在相对速度较低的前提下，正好是抵抗相对涡旋的抗性力，这是遏制涡旋的主要机制。另外，压力差别以较小的系数传递到入口区域，所形成的压力梯度又是没有梳叶的入口区涡旋的遏制因素。压力差别所形成的出口速度差别又能够对近压力面岔道出口如图中 42形成引射动力而使其加速，并且形成的速度梯度在出口之外如图中 43 降低了外侧的绝对速度和内侧的相对速度，这正是理想的低损耗速度分布。这两大因素加上近吸力面岔道流程较长等有利因素，相对涡旋在最优化的岔道出口面积比条件下能够被遏制住。 As shown in the figure, the number of L-shaped blades is arranged on the circular or zigzag wheel of the high potential ratio impeller in a rotationally symmetrical manner. At the wide front part of the channel between the L-shaped blades, 2 pieces are arranged in the homeopathy. Combining leaves at an even speed produces 3 average speed forks. 38 is a near-pressure side bifurcation, 39 is a near-suction side bifurcation, and the middle is a branch between the two. The front and middle of the average speed combing leaf also showed a radial trend, the tail turned smoothly, and the downstream direction pointed to the accelerating section of the blade groove. Comb leaves form dense constraints on the flow under the premise of relatively low velocity. The integral of the normal force along the way will include a shear moment, which acts in the opposite direction to the direction of the relative vortex. One of the important factors. The more important mechanism is that, because the bifurcation entrance approaches 41 as shown in the figure and does not reach the leaf trough entrance, the bifurcation exit does not reach the leaf groove as it approaches 40 as shown in the diagram, and its exit cross-sectional area is based on an experience obtained through optimization experiments Coefficient distribution, its near-pressure side bifurcation distribution is more and near-suction surface bifurcation allocation is less, so the former along the way pressure is lower all the way and the latter along the way pressure is higher all the way, the difference of this pressure field gradient distribution, in the relative speed The lower premise is exactly the resistance to the relative vortex. The main mechanism of vortex control. In addition, the pressure difference is transmitted to the inlet area with a small coefficient, and the pressure gradient formed is a containment factor for the vortex in the inlet area without combing leaves. The difference in the exit speed caused by the pressure difference can form an ejection force to accelerate the bifurcation exit near the pressure surface as shown in Figure 42 and accelerate it, and the speed gradient formed outside the exit as shown in Figure 43 reduces the absolute outside speed and the inside The relative velocity, which is the ideal low-loss velocity distribution. These two factors coupled with the favorable factors such as the longer bifurcation flow near the suction surface, the relative vortex can be contained under the optimized ratio of the exit area of the bifurcation.

没有相对涡旋，叶槽及其岔道中的相对速度将减小半个数量级，这是特别重要的。在通常规格的叶轮尺寸和转速下，相对涡旋在压力面的负叠加和在吸力面的正叠加，都可能使液流速度超过临界值而进入紊流状态。降低半个数量级以后，液流速度可以设计在水力规范之内，这时的流程损耗或者局部阻力损耗都小得可以忽略，如前所述的相对速度较低的设计前提，也显然可以得到完全的满足。 Without relative vorticity, the relative velocity in the lobes and their forks will be reduced by half an order of magnitude, which is particularly important. Under the normal size impeller size and speed, the negative superposition of the relative vortex on the pressure surface and the positive superposition on the suction surface may cause the liquid flow velocity to exceed the critical value and enter a turbulent state. After reducing by half an order of magnitude, the flow velocity can be designed within the hydraulic specifications. At this time, the process loss or local resistance loss can be negligibly small. As mentioned above, the design premise of relatively low speed can obviously also be completely achieved. Satisfaction.

带均速岔道的高势比叶轮具有全程水力效率高、抗气蚀特性好的显著优势。这种技术与半开式或闭式、单级或多级、有无预旋器、是不是锯齿形轮盘、配不配内减摩装置等设计特征的组合没有任何配伍禁忌，因而可以广泛地应用。在工艺上，如图所示的结构是容易制造的。最简单的工艺是模成型，包括压铸、粉末冶金、注塑、压塑等工艺路线，而且只需使用最廉价的两合模，其生产成本很低，并且动平衡特性好。参照图 9，图中给出了一种均速高势比叶轮（带均速岔道的高势比叶轮之简称，下同）与预旋器组合的实施例。其中， 44是叶轮的 L形叶片， 45是均速岔道， 46是预旋器的下轮圈， 47是预旋器的上轮圈， 48是预旋器帆式叶片， 49预旋器的刚性肋条， 50是叶轮轴套， 51是叶轮转轴。 The high-potential with average speed bifurcation has the obvious advantages of high hydraulic efficiency and good anti-cavitation characteristics. The combination of this technology with design features such as semi-open or closed, single-stage or multi-stage, with or without pre-spinner, with or without serrated wheel, with or without internal friction reduction device, has no contraindications, so it can be widely used application. Technically, the structure shown in the figure is easy to manufacture. The simplest process is molding, including die-casting, powder metallurgy, injection molding, compression molding and other technological routes, and only the cheapest two-clamping mold is used. Its production cost is very low, and its dynamic balance characteristics are good. Referring to FIG. 9, an embodiment in which a uniform speed and high potential ratio impeller (abbreviation of high potential ratio impeller with average speed bifurcation, hereinafter the same) is combined with a pre-spinner is shown. Among them, 44 is the L-shaped blade of the impeller, 45 is the uniform speed bifurcation, 46 is the lower rim of the pre-spinner, 47 is the upper rim of the pre-spinner, 48 is the pre-spinner sail blade, and 49 is the pre-spinner. Rigid ribs, 50 is the impeller sleeve, 51 is the impeller shaft.

均速高势比叶轮通过轴套 50装配和定位在转轴 51上，叶轮有 L形叶片如 44，形成数量相同的叶槽流道。每个叶槽流道中布设有均速梳叶，形成均速岔道如 45 等。叶轮轴套 ***是圆环柱形吸入室腔，其间安装有轴向入流预旋器。预旋器的下轮圈 46安装在吸入室下部，上轮圈 47安装在上部，它们都是用聚四氟乙烯等自润滑材料制成的，因而可以各自独立地在叶轮轴套上转动。两个轮圈的外表面为互相吻接的旋转曲面，其母线的方向角连续地转过 90度，以使液流在加载旋转中完成径向运动分量到轴向运动分量的转换。如图中 48等，预旋器的弹性帆式叶片悬挂在如图中 49等刚性肋条上，肋条固定在叶轮叶片根部入口处。工作时，肋条随叶轮一道旋转，带动帆式叶片和两个轮圈同步旋转，帆式叶片对液流做功使其预旋。叶片由于分布式负荷而产生分布式变形，其平衡应力的大小和方向使叶片成为螺桨形曲面，并因而决定轮圈的滞后角。螺桨形曲面和轮圈滞后角在液流动态变化时会自适应调整，这种机制可以使损耗减小，其中包括叶片迎角的自适应变化的贡献。 The impeller with average speed and high potential ratio is assembled and positioned on the rotating shaft 51 through the sleeve 50. The impeller has L-shaped blades such as 44 to form the same number of grooved channels. Each blade channel is provided with a uniform-speed combing blade to form a uniform-speed bifurcation such as 45. The periphery of the impeller shaft sleeve is a circular cylindrical suction chamber cavity, and an axial inflow pre-rotator is installed therebetween. The lower rim 46 of the pre-rotator is installed in the lower part of the suction chamber, and the upper rim 47 is installed in the upper part. They are all made of self-lubricating material such as polytetrafluoroethylene, so they can be independently rotated on the impeller sleeve. The outer surfaces of the two rims are rotating curved surfaces that meet each other, and the direction angle of the generatrix is continuously rotated through 90 degrees, so that the fluid flow completes the conversion from the radial motion component to the axial motion component during the load rotation. As shown in Fig. 48 and the like, the elastic sail-type blades of the prerotator are suspended on rigid ribs such as 49 in the figure, and the ribs are fixed at the root entrance of the impeller blade. During operation, the ribs rotate together with the impeller, which drives the sail blades and two rims to rotate synchronously. The sail blades perform work on the liquid flow to pre-spin. The distributed deformation of the blade due to the distributed load, the magnitude and direction of its equilibrium stress make the blade a propeller-shaped curved surface, and thus determine the lag angle of the rim. The propeller-shaped surface and rim lag angle are adaptively adjusted when the fluid flow changes dynamically. This mechanism can reduce the loss, including the contribution of the adaptive change of the blade angle of attack.

L形叶片高势比叶轮应用于轴向入流离心泵时，预旋器是重要的配置，因而这种组合将是一种常用的设计。其中，锯齿形轮盘半开式均速高势比叶轮可以用于装配不带内减摩装置的高势比单 ^泵，这是常规结构的高势比单级泵中最简单的一种。参照图 10，图中出了较为复杂和效率较高的一种悬臂式高势比单级泵。其中， 52 是蜗道， 53是梯形槽导环， 54是均速高势比叶轮， 55是预旋器， 56是机械轴封， 57是悬臂式转轴， 58是后盖， 59是前盖。 When the L-shaped vane high potential ratio impeller is applied to an axial inflow centrifugal pump, the pre-spinner is an important configuration, so this combination Will be a commonly used design. Among them, the zigzag disc half-open average speed high potential ratio impeller can be used to assemble a high potential ratio single pump without an internal friction reduction device, which is the simplest of the conventional high potential ratio single-stage pumps. . Referring to FIG. 10, a cantilever type high potential ratio single stage pump with a relatively complicated and high efficiency is shown in the figure. Among them, 52 is a volute, 53 is a trapezoidal groove guide ring, 54 is an average speed high potential ratio impeller, 55 is a pre-spinner, 56 is a mechanical shaft seal, 57 is a cantilever shaft, 58 is a rear cover, 59 is a front cover .

预旋均速高势比二次型蜗道悬臂泵由闭式均速高势比叶轮 54、装在叶轮吸入室中的预旋器 55、机械轴封 56、带二次型蜗道 52曲面的前盖 58和后盖 59及悬臂轴等结构组成。其中，叶轮 54为半开式或加铆前盖的闭式结构， 8片 L形叶片隔出 8个叶槽流道。每个叶槽中有 2片均速梳叶，形成 3个均速岔道，叶轮工作时输出高势比液流。预旋器 55装在叶轮吸入室中，有 4片弹性帆式叶片，固定在 4条刚性肋条和两个轮圈上，轮圈滑套在叶轮轴套上。 ' The pre-spinning average speed high potential ratio secondary worm cantilever pump consists of a closed-type high-speed ratio potential impeller 54, a pre-spinner 55 installed in the impeller suction chamber, a mechanical shaft seal 56, and a curved surface with a secondary worm 52 The front cover 58 and the rear cover 59 and the cantilever shaft are composed. Among them, the impeller 54 is a semi-open type or a closed structure with a riveted front cover, and 8 L-shaped blades separate 8 blade groove flow channels. Each blade groove has 2 uniform-speed combing leaves, forming 3 uniform-speed bifurcations. When the impeller works, it outputs a high potential specific flow. The pre-spinner 55 is installed in the impeller suction chamber, and has 4 elastic sail blades, which are fixed on 4 rigid ribs and two rims, and the rim slides on the impeller sleeve. '

这种叶轮输出势动比高，抗涡旋，抗气蚀，具有变工况适应性。其中，预旋器对液流加载预旋，能避免入口处的撞击湍流； L形叶片流道及其出口的高势比设计能降低输出速度；均速岔道阻遏相对涡旋，能避免回流、尾缘涡等有害流态，使流场低速层流化，所产生的速度梯度还能降低轮沿摩擦速度和出口外邻域的绝对速度。 The impeller has a high output potential ratio, anti-vortex, anti-cavitation, and adaptability to changing conditions. Among them, the pre-spinner pre-spins the liquid flow, which can avoid the impact of turbulence at the entrance; the high potential ratio design of the L-shaped blade flow channel and its outlet can reduce the output speed; the uniform speed bifurcation blocks the relative vortex and can prevent backflow, The trailing edge vortex and other harmful flow patterns make the flow field low-speed laminarization, and the resulting speed gradient can also reduce the wheel friction speed and the absolute speed in the vicinity of the exit.

高势比叶轮的出口液流具有模拟连续开口的均布化效果，出口流速的径向分量等于流量除以轮周面积，'其数值较小，这有利于釆用蜗道导流。但是，当叶轮出口宽度较小时，如迳直采用蜗道导流，或釆用较宽的矩形截面导环，都会产生局部激励。本实例釆用二次型蜗道或者小入口导环加二次型蜗道的组合导流设计。 The outlet flow of the high potential ratio impeller has a uniform distribution effect that simulates continuous openings. The radial component of the outlet velocity is equal to the flow divided by the area around the wheel. 'The value is small, which is conducive to the use of worm guides. However, when the width of the impeller outlet is small, such as using straight worm guides or using a wide rectangular cross section guide ring, local excitation will occur. In this example, a combined diversion design using a secondary worm or a small inlet guide ring and a secondary worm is used.

其中，二次型蜗道 52釆用优化截面设计，由两种截面段光滑吻接而成，起始段为定长轴 2L之长半椭圆截面，短半轴为 Among them, the secondary worm trajectory 52 釆 has an optimized cross-section design and is formed by smoothly matching two cross-section sections. The initial section is a long semi-elliptical section with a fixed long axis of 2L, and the short semi-axis is

b=Q e (2α— 1 + (ΐ_ α) θ/π)/ (π²Ι (9) 成为半圆后为定弦长 2L之大弓形，弓形半径 r约束于超越方程 b = Q e (2α— 1 + (ΐ_ α) θ / π) / (π ² Ι (9) becomes a large bow with a fixed chord length of 2L after becoming a semicircle, and the bow radius r is constrained by the transcendental equation

Γ ² (π— Sin— L/r) ) +L (r²_L²) ⁰'⁵ = Q θ (2α— 1 +(1— α) θ/π)/(2 πν) 〜（10) 这里， Q、 θ、 ct、L、 V分别为设计体积流量、蜗道截面对应圆心角、蜗道优选系数、蜗道入口柱面宽度之半、设计蜗道出口平均流速。最小摩擦面和最小梯度设计法及其方程 (9)、 ( 10) 式对于低损耗蜗道的设计具有重要意义，其中（10) 式可用 2阶以上幂级数解析，或用数值解法解之。蜗道优化系数 α是一个取值 0.5〜1的真小数，具体取值可通过理论分析导出，也可以釆用优选法通过少量的试验得到。 Γ ² (π— Sin— L / r)) + L (r ² _L ² ) ⁰ ' ⁵ = Q θ (2α— 1 + (1— α) θ / π) / (2 πν) ~ (10) here , Q, θ, ct, L, V are the design volume flow, the center angle of the worm section, the worm preference coefficient, the half of the worm inlet cylinder width, and the average worm outlet velocity. The minimum friction surface and minimum gradient design method and its equations (9) and (10) are of great significance for the design of low-loss worms, where (10) can be analyzed by power series of order 2 or higher, or solved by numerical methods . The worm optimization coefficient α is a true decimal value of 0.5 to 1. The specific value can be derived through theoretical analysis, or it can be obtained through a small amount of experiments by using the optimization method.

(9)、 ( 10) 式中，蜗道入口宽度即叶轮出口宽度，当该宽度较小时，有可能产生局部激励，应该***等腰梯形槽导环 53 过渡。梯形截面出入口底边宽度分别等于蜗道入口和叶轮出口宽度，两者之比为

(9) and (10) In the formula, the width of the worm entrance is the width of the impeller exit. When the width is small, local excitation may occur, and the isosceles trapezoidal groove guide ring 53 should be inserted for transition. The width of the bottom edge of the entrance and exit of the trapezoidal section is equal to the width of the entrance of the worm and the exit of the impeller. The ratio of the two is

其中、ω、Ι、 Κ分别为叶轮出口柱面宽度之半、叶轮角速度、叶轮半径、叶轮反馈减速比，梯形的高一般取叶轮出口柱面宽度的 3〜5倍，即 61^〜10 较为恰当。显然，导环作为过渡流道，其参数是受前后流道参数制约的。 Among them, ω, Ι, and K are respectively half of the width of the impeller exit cylinder, the impeller angular velocity, the impeller radius, and the impeller feedback reduction ratio. The height of the trapezoid is generally 3 to 5 times the width of the impeller exit cylinder, which is 61 ^ ~ 10. appropriate. Obviously, the guide ring is used as a transition flow channel, and its parameters are restricted by the parameters of the front and rear flow channels.

***导环后，叶轮输出液流以近乎切向的方向进入，其流线将因导环中的径向压力梯度的分布而连续转向为接近于圆弧的对数螺旋线，其径向坐标增量意味着液流截面积的扩大，也意味着为克服压差进入高压区必须消耗动能为进入做功，这就是梯形槽导环增压过程。为消除局部激励而设置的导环，将首先自动承接导流增压的任务，然后才能完成与汇流流道无局部激励连通的任务。 ***导环可以减轻蜗道的负荷，其优化系数 α将增大，其速度梯度将减小，工作效率因而提高。当 α接近于 1时，蜗道将主要作为一个汇流流道起作用。因此，导环的导流负荷比与蜗道优化系数 α是相互关联的。 After inserting the guide ring, the impeller output liquid flow enters in a nearly tangential direction, and its streamline will be continuously turned into a logarithmic spiral line close to the arc due to the radial pressure gradient distribution in the guide ring. Its radial coordinates Increment means that the cross-sectional area of the liquid flow is enlarged, and it also means that the kinetic energy must be consumed to enter the high pressure area to overcome the pressure difference. This is the trapezoidal groove guide ring pressurization process. The guide ring set to eliminate local excitation will first automatically undertake the task of diversion and boost pressure, and then the task without local excitation and communication with the manifold can be completed. Inserting the guide ring can reduce the load of the worm, its optimization coefficient α will increase, its speed gradient will decrease, and the work efficiency will increase. When α is close to 1, the volute will mainly function as a confluence channel. Therefore, the diversion load ratio of the guide ring and the worm optimization coefficient α are interrelated.

泵的前后壳盖 59和 58在蜗道对称面分型，也可以在前端面之蜗道入口柱面分型。后一种分型工艺有利于减小体积。壳盖采用精密铸造或者模成型工艺制造，其外部有径向加强筋结构，以增加强度和节约材料。 The front and rear casing covers 59 and 58 of the pump are typed on the symmetric surface of the worm, and can also be typed on the cylindrical surface of the worm inlet at the front end. The latter parting process helps to reduce the volume. The shell cover is manufactured by precision casting or die-casting process, and has a radially reinforced rib structure on the outside to increase strength and save material.

从图中可见，本实例中蜗道占据了较大的空间，这是长途奔泻汇流的结果，这种泵结构的缺点因而很明显。体积大不但使用不便，还会增加制造成本。这种结构因袭了传统的单级泵蜗道的框架，因而不是本发明的最佳实施方案，但在釆用蜗道的单级泵设计中，其高效率的特点却是非常突出的。参照图 11，图中给出了出轴端腔内减摩驱动二相流冷却轴封的一种流道结构。其中， 60是转轴， 61是轴封腔结构体， 62是环形静止静密封件， 63是环形静摩擦片， 64是二相流入管， 65是环形动摩擦片， 66是环形旋转静密封件及其压簧， 67是卡簧或卡销， 68是环形盖板， 69是抱轴环形开口。 It can be seen from the figure that the volute in this example occupies a large space, which is the result of the long-distance running and confluence. The disadvantages of this pump structure are therefore obvious. The large size is not only inconvenient to use, but also increases manufacturing costs. This structure is not the best embodiment of the present invention because it follows the frame of a traditional single-stage pump worm. However, in the design of a single-stage pump using a worm, its high efficiency is very prominent. Referring to FIG. 11, a flow channel structure of a two-phase flow cooling shaft seal for reducing friction in a shaft-end cavity is shown. Among them, 60 is a rotating shaft, 61 is a shaft seal cavity structure, 62 is an annular static static seal, 63 is an annular static friction plate, 64 is a two-phase inflow pipe, 65 is an annular dynamic friction plate, 66 is an annular rotating static seal and its Compression spring, 67 is a circlip or bayonet, 68 is a ring-shaped cover plate, and 69 is a ring-shaped ring-shaped opening.

根据机械动密封的示意性结构。转轴 60从轴封端机壳伸出，环形轴封静摩擦片 63通过静止静密封件 62 固定在轴封腔机壳上并形成机壳与动摩擦片的圆柱面密封。环形动摩擦片 65套在转轴上，通过环形旋转静密封件及其压簧 66进行圆柱面及平面静密封，并传递卡簧或卡销 67传来的压力和转矩，与轴同步旋转。动摩擦片与静摩擦片间形成动密封，生成一定功率的热，如不传走该热功率，动密封及其连接构件将因连续升温而烧毁。 Schematic structure according to mechanical dynamic seal. The rotating shaft 60 protrudes from the shaft sealing end casing, and the annular shaft sealing static friction plate 63 is fixed on the shaft sealing cavity casing through the static static sealing member 62 and forms a cylindrical surface seal between the casing and the moving friction plate. The annular dynamic friction plate 65 is set on the rotating shaft, and the cylindrical surface and the plane are statically sealed by the annular rotating static seal and its compression spring 66, and transmits the pressure and torque transmitted by the circlip or bayonet 67, and rotates synchronously with the shaft. A dynamic seal is formed between the moving friction plate and the static friction plate, and a certain amount of heat is generated. If the heat power is not transmitted, the dynamic seal and its connecting member will be burned due to continuous heating.

图中，内减 . 动二相流入管 64对着静摩擦片接入轴封腔，环形盖板 68将轴封腔与相邻端腔隔开， g下一个抱轴环形开口 69 与端腔相通。二相流将对静摩擦片形成液流动量冲击和气泡浮升搅 '扰，这能增强其表面液流速度。二相流在 65、 66、 67三个转动部件驱动下旋转和气液分离，液位的径向坐标与开口 69 同，腔中几乎被旋转液环充满。液环与摩擦片间存在相对运动，其热对流循环机制有利于降低散热体周围温度。液体吸热升温后与分离出来的气体在出口重新合成二相流，并以较低的轴向速度喷向叶轮端面进入端腔。 In the figure, the internal two-phase inflow pipe 64 faces the static friction plate and enters the shaft seal cavity. The annular cover plate 68 separates the shaft seal cavity from the adjacent end cavity. G The next annular shaft opening 69 communicates with the end cavity. . The two-phase flow will disturb the fluid flow of the static friction plate and disturb the bubble floating, which can enhance the surface liquid flow velocity. The two-phase flow is rotated and separated by gas and liquid under the driving of three rotating parts 65, 66, 67. The radial coordinate of the liquid level is the same as the opening 69, and the cavity is almost filled with a rotating liquid ring. There is relative movement between the liquid ring and the friction plate, and its thermal convection circulation mechanism is beneficial to reduce the temperature around the heat sink. After the liquid absorbs heat and heats up, the two-phase flow is recombined with the separated gas at the outlet, and is sprayed to the impeller end face and the inlet end at a lower axial speed. Cavity.

内减摩是本发明克服轮盘摩擦损耗、提高内机械效率的一项重要设计。轴封冷却牵涉到泵的运行安全，是一种必要的技术设计。较之组织单独的冷却循环，本发明的方法将端腔二相流循环与轴封冷循环合一，简化了设计，节约了压力液体循环流量，因而能提高泵的容积效率。并且，升温后的二相流粘滞系数减小，有利于增加减摩效果。参照图 12， '图中给出了前端腔减摩时防止气体逃逸的一种阻气间隙结构。其中， 70 是叶轮盖板， 71是前端腔， 72是入口动配合间隙兼离心分离流道， 73为固定在叶轮前盖板近轴部位的小动环， 74是动配合间隙和泄漏流道， 75是二相流入管， 76是前端腔静止腔壁或泵之入管， 77是吸入室或其贯通流道。 Internal friction reduction is an important design of the present invention to overcome the friction loss of the disk and improve the internal mechanical efficiency. Shaft seal cooling involves the safe operation of the pump and is a necessary technical design. Compared with the separate cooling cycle of the organization, the method of the present invention integrates the end-cavity two-phase flow cycle and the shaft seal cold cycle into one, which simplifies the design and saves the circulation flow of the pressure liquid, thereby improving the volumetric efficiency of the pump. In addition, the viscosity coefficient of the two-phase flow after heating is reduced, which is beneficial to increase the friction reduction effect. Referring to FIG. 12, the figure shows a gas blocking gap structure that prevents gas from escaping during friction reduction of the front end cavity. Among them, 70 is the impeller cover, 71 is the front cavity, 72 is the inlet dynamic fit clearance and centrifugal flow channel, 73 is a small moving ring fixed to the near-axis portion of the impeller front cover, 74 is the dynamic fit clearance and leakage flow channel , 75 is a two-phase inflow pipe, 76 is a stationary cavity wall of a front-end cavity or an inlet pipe of a pump, and 77 is a suction chamber or a through flow channel thereof.

图中，在前端腔腔壁近轴部位布设环形槽，槽中纳入随叶轮旋转的小动环 74，将环形槽隔成一个顶端远轴的 V形环槽，其一侧环形间隙 72连通前端腔 71，另一侧环形间隙 74 连通吸入室。将二相流入管连通间隙 72，则二相流在动环驱动下离心分离，部分流量的液体从 V形槽底部间隙转向 180度缓慢流入间隙 74和吸入室 77, 其流阻产生阻塞作用，能防止气体逃逸，从而形成 V形槽阻气间隙。气体浮升到间隙 72的近轴空间流入前端腔 71。二相流中的液体流量应该大于经 74流走的流量，其剩余部分也经间隙 72进入端腔 71，然后从叶轮边沿间隙中流入导流器。上述选择性分离机制只需要很小的构件尺寸，因为设计目标仅仅为在岔道的一个小邻域内使泄漏侧流体为纯液体就行了。 In the figure, an annular groove is arranged at the near-axis portion of the cavity wall of the front end cavity, and a small moving ring 74 rotating with the impeller is included in the groove to separate the annular groove into a V-shaped annular groove with a distal far end. The annular gap 72 on one side communicates with the front end. The cavity 71 and the annular gap 74 on the other side communicate with the suction chamber. The two-phase inflow tube communicates with the gap 72, and the two-phase flow is centrifuged under the driving of a moving ring. Part of the flow of liquid turns from the gap at the bottom of the V-shaped groove to 180 degrees and slowly flows into the gap 74 and the suction chamber 77. Its flow resistance has a blocking effect. Can prevent gas from escaping, thereby forming a V-shaped gas barrier gap. The paraxial space where the gas floats up to the gap 72 flows into the front-end cavity 71. The liquid flow in the two-phase flow should be greater than the flow away through 74, and the remainder also enters the end cavity 71 through the gap 72, and then flows into the deflector from the edge gap of the impeller. The above selective separation mechanism only requires a small component size, because the design goal is only to make the leak-side fluid pure liquid in a small neighborhood of the fork.

叶轮前端腔的微小循环流量充气设计依赖于阻气间隙的正常工作。在阻气间隙的设计环槽 74至吸入室流程应该具有较大的阻力系数，二相流液体流量应该大于该环槽泄漏流量，这是两个重要前提。如不能满足该前提，前者将导致二相流循环流量加大，后者将导致充气端腔雪崩般泄压而为液体所充盈，充气减摩状态将不复存在。 The tiny circulating flow inflation design of the impeller front cavity relies on the normal operation of the air gap. The design of the choke gap The flow from the ring groove 74 to the suction chamber should have a large resistance coefficient. The liquid flow of the two-phase flow should be greater than the leakage flow of the ring groove. These are two important prerequisites. If this premise cannot be met, the former will lead to an increase in the circulating flow of the two-phase flow, and the latter will cause avalanche-like pressure relief in the inflation end cavity to be filled by the liquid, and the state of inflation reduction will no longer exist.

如果牺牲一些容积效率指标，则可以不使用这种复杂的阻气间隙，只需加大二相流的流量，允许二相流直接分流一部分回到吸入室，就能够实现内减摩而获得效率的提髙。这是因为：其一，当分流的两个流道在一定的分岔长度上保持为同一种气液比例的二相流时，流动将是稳定的，不存在发生雪崩式气体逃逸的可能性；其二，容积效率对二相流流量损失的变化率是一较小的常数，而机械效率收益对内减摩的变化率是相对幅度达到 90%或更高的一个阶跃，其幅度为高次幂函数，具有高敏感性，因而牺牲前者可以获取效率收益。参照图 13，图.中给出了一种半开式叶轮悬臂泵的充气驱动装置及其连接的实施方案。其中， 79是压力液体流量调节阀， 80是进气流量调节阀， 81是射流器， 82是泵的机械轴封， 83是轴封腔环形盖板出口， 84是半开式离心泵的后端腔。 If some volumetric efficiency indicators are sacrificed, such a complex air gap may not be used, and only the flow rate of the two-phase flow needs to be increased, allowing the two-phase flow to be directly shunted back to the suction chamber, and internal friction reduction can be achieved to obtain efficiency. Mention This is because: first, when the two flow channels that are diverted maintain a two-phase flow with the same gas-liquid ratio over a certain bifurcation length, the flow will be stable, and there is no possibility of avalanche gas escape Secondly, the rate of change of volumetric efficiency to the loss of two-phase flow is a small constant, while the rate of change of mechanical efficiency gain to internal friction reduction is a step with a relative amplitude of 90% or higher, with a magnitude of High power functions have high sensitivity, so sacrificing the former can obtain efficiency gains. Referring to FIG. 13, an embodiment of an inflatable driving device of a semi-open impeller cantilever pump and its connection is shown in FIG. Among them, 79 is the pressure liquid flow regulating valve, 80 is the intake flow regulating valve, 81 is the ejector, 82 is the mechanical shaft seal of the pump, 83 is the outlet of the annular cover of the shaft seal cavity, and 84 is the rear of the semi-open centrifugal pump. End cavity.

图中，压力液体经调节阀 79调节流量后进入射流器 81，引射经调节阀 80调节流量的气体生成二相流，经管路接入轴封腔，冷却机械轴封 82后，从环形盖板中心出口流入后端腔，对其充气减摩。驱动射流器的压力液体一般可以从离心泵的出管分流引出，其压力比叶轮输出静压力高 0.05MPa以上时即能正常工作，离心泵的运行参数通常能够满足这个条件。调节陶 79用于调节压力液体的流量，整定在能正常充气的较小流量。调节阀 80用于调节气体流量，其开度不恰当可能造成输'出压力偏低而不能使端腔充气，或者充气直径比不能达到最大值，因而必须能够细调。所用气体应该对泵送液体无害，由于射流器对气源压力要求宽泛，多数情况下可以将空气作为充气介质，这时该阀入口连通大气就行了。射流器 81 的容量和引射压比及输出压力应该与端腔减摩需求的最大充气流量、最高端腔压力相匹配，否则不能达到预期效果。充气端腔中的气体一般不会消耗掉，因而整个装置所需的流量很小。. 参照图 14，图中给出了一种闭式叶轮悬臂泵的充气减摩装置及其连接方案。其中， 85 是出轴端机械密封， 86是后端腔， 87、 88分别是后端腔、前端腔的流量分配管， 89是前端腔， 90是射流器， 91是引射气体流量调节阀， 92是压力液体流量调节阀， 93是前端腔 V形槽阻气间隙。 In the figure, the pressure liquid enters the ejector 81 after adjusting the flow rate through the adjustment valve 79, and the gas adjusted by the adjustment valve 80 is ejected to generate a two-phase flow, which is connected to the shaft seal cavity through the pipeline, and after cooling the mechanical shaft seal 82, After the board center exit flows End cavity, inflate it to reduce friction. The pressure liquid driving the ejector can generally be diverted from the outlet pipe of the centrifugal pump, and the pressure can be normally operated when the pressure is higher than the static pressure of the impeller by more than 0.05 MPa. The operating parameters of the centrifugal pump can usually meet this condition. The regulating pottery 79 is used to regulate the flow of the pressure liquid, and is set to a small flow that can be normally inflated. The regulating valve 80 is used to regulate the gas flow rate. An inappropriate opening may cause the output pressure to be too low to inflate the end cavity, or the inflation diameter ratio cannot reach the maximum value, so it must be able to be fine-tuned. The gas used should be harmless to the pumped liquid. Since the ejector has a wide range of pressure requirements on the gas source, air can be used as the inflation medium in most cases. At this time, the inlet of the valve should be connected to the atmosphere. The capacity, ejection pressure ratio, and output pressure of the ejector 81 should match the maximum inflation flow and the maximum end cavity pressure required for friction reduction in the end cavity, otherwise the expected effect cannot be achieved. The gas in the inflatable end cavity is generally not consumed, so the flow required by the entire device is small. Referring to FIG. 14, the figure shows a pneumatic friction reducing device of a closed impeller cantilever pump and a connection scheme thereof. Among them, 85 is the mechanical seal at the shaft end, 86 is the rear cavity, 87 and 88 are the flow distribution tubes of the rear cavity and the front cavity, 89 is the front cavity, 90 is the ejector, and 91 is the ejection gas flow regulating valve. , 92 is a pressure liquid flow regulating valve, and 93 is a front-end cavity V-shaped air gap.

闭式叶轮离心泵的内减摩驱动装置由压力液体调节阀 92、射流器 90、引射气体调节阀 91、流量分配管 87和 88及前端腔阻气间隙 93组成。当泵之出口压力比叶轮输出静压力高 0.05MPa以时，压力液体从该出口分流引出。 92用于调节压力液体流量，整定在能正常充气的较小流量。 91用于调节气体流量，使用空气时其入端通大气。射流器的流量、最高压力及引射压比与需求流量、最高压力及入口压力是匹配的。与图 13 中的半开式叶轮泵不同的是，闭式叶轮的两个端腔均需要充气，并且其前端腔有一个通吸入室的并联回流间隙，需要设置成如图 12所示的 V形槽阻气间隙。由于前后端腔同时充气，二相流流量要大一些。输送流量分配管 87和 88的作用是设置管道阻力系数差，据以控制流量分配，其前提是并联的目标端腔在充气状态下具有相同的压力。所幸实际情况正好如此，因而稳态运行时，流量将受分配管控制。在初始化动态过程中，前端腔将首先充气，然后是后端腔。 The internal friction reducing driving device of the closed impeller centrifugal pump is composed of a pressure liquid regulating valve 92, an ejector 90, an ejection gas regulating valve 91, a flow distribution pipe 87 and 88, and a front-end cavity air gap 93. When the outlet pressure of the pump is higher than the static pressure output by the impeller by 0.05 MPa, the pressure liquid is diverted from this outlet. 92 is used to regulate the flow of pressurized liquid, set to a small flow that can be normally inflated. 91 is used to adjust the gas flow, and its inlet is open to the atmosphere when air is used. The flow rate, maximum pressure and ejection pressure ratio of the ejector are matched with the required flow, maximum pressure and inlet pressure. Different from the semi-open impeller pump in Fig. 13, both end cavities of the closed impeller need to be inflated, and the front end cavity has a parallel return gap through the suction chamber, which needs to be set to V as shown in Fig. 12 Grooved air gap. Because the front and rear cavities are inflated at the same time, the two-phase flow is larger. The function of the delivery flow distribution pipes 87 and 88 is to set the difference in pipeline resistance coefficient to control the flow distribution based on the premise that the parallel target end cavities have the same pressure in the inflated state. Fortunately, this is exactly the case, so during steady operation, the flow will be controlled by the distribution pipe. During the initialization dynamics, the front-end cavity will be inflated first, followed by the rear-end cavity.

图中，阻气间隙 93是一个 V形环槽，其作用在于使二相流气液分离和分流，槽中随叶轮转动的小动环带动进入的二相流旋转，其离心力使气体浮升到近轴空间而被小动环隔离，液体则从环槽远轴底部绕过动环进入泄漏间隙，从而阻塞气体泄漏通道。 In the figure, the choke gap 93 is a V-shaped ring groove, which is used to separate and split the two-phase gas and liquid. The small two-phase ring that rotates with the impeller rotates the incoming two-phase flow. The centrifugal force causes the gas to float to The paraxial space is isolated by the small moving ring, and the liquid bypasses the moving ring from the bottom of the ring groove far shaft and enters the leakage gap, thereby blocking the gas leakage channel.

在 V形槽阻气间隙的替代方案中，除了前述加大二相流流量的简单办法以外，还可以在同一位置用橡胶、聚四氟乙烯、尼龙等材料制成的软挡圈取代 V形槽阻流。在有液体润滑的前提下，它们与转轴之间能形成小而稳定的间隙，对液体和气体的阻力系数均充分大，二相流的流量损失将充分小。具体方法是将二相流入管的出口对着软挡圈与轴的接触处开放，在端腔与吸入室压差的驱动下，软挡圈将得到良好的润滑。参照图 15，图中给出了向心导轮的一种示意性结构，这是一种带装配外壳的部件。其中， 101是圆环柱外壳（带鼻形紧固螺栓通孔）， 102是转移段流道的轴面投影， 103是导轮基板， 104是导轮轴套， 105是螺栓孔， 106是曲率半径逐渐减小的导叶， 107是叶轮至导轮的转移段流道， 108是转移段流道截止隔舌， 109是减速增压流道， 110是流道的圆柱面出口。 In the alternative to the V-shaped groove air gap, in addition to the simple method of increasing the flow rate of the two-phase flow described above, the V-shape can be replaced by a soft stop ring made of rubber, Teflon, nylon and other materials at the same position. The trough is blocking flow. Under the premise of liquid lubrication, they can form a small and stable gap with the rotating shaft, the resistance coefficients to liquid and gas are sufficiently large, and the flow loss of the two-phase flow will be sufficiently small. The specific method is to open the outlet of the two-phase inflow pipe to the contact between the soft stop and the shaft. Under the drive of the pressure difference between the end cavity and the suction chamber, the soft stop will be well lubricated. Referring to FIG. 15, there is shown a schematic structure of a centrifugal guide wheel, which is a component with an assembled housing. Among them, 101 is a circular column shell (with a nose-shaped fastening bolt through hole), 102 is an axial plane projection of a transfer passage, 103 is a guide wheel base plate, 104 is a guide wheel bushing, 105 is a bolt hole, and 106 is a curvature The guide vanes with a decreasing radius, 107 is the flow channel of the transfer section from the impeller to the guide wheel, 108 is the stopper tongue of the transfer section flow channel, 109 is the deceleration boost flow channel, and 110 is the cylindrical surface outlet of the flow channel.

向心导轮由圆环柱形外壳 101、基板 103、轴套 104以及曲率半径逐渐减小的导叶如 106组成。外壳上带有转移段流道腔如 107，导叶间是减速增压流道如 109。向心导轮的导叶数少于叶轮叶片数，这是因为导轮中的绝对流速远高于叶轮中的相对流速，需要较大的当量直径来降低阻力系数。但导叶数也不可太少，太少将延长液流的汇流流程而增大摩擦面积。实践中，可以通过理论规划或者优选试验（釆用优选法）确定设计尺寸下的最佳导叶数。在转移段流道中，应该保证液流无速度大小和方向的突变，这样，轴向位移将低速完成，圆周速度将基本保持，换向损耗等局部阻力损耗将大为减小。 The centrifugal guide wheel is composed of a circular cylindrical housing 101, a base plate 103, a shaft sleeve 104, and a guide vane such as 106 with a decreasing radius of curvature. The casing is provided with a transfer channel cavity such as 107, and a deceleration and booster flow channel such as 109 is provided between the guide vanes. The number of guide vanes of the centripetal guide wheel is less than the number of impeller blades. This is because the absolute flow velocity in the guide wheel is much higher than the relative flow velocity in the impeller, and a larger equivalent diameter is required to reduce the drag coefficient. However, the number of guide vanes should not be too small, too few will prolong the confluent flow of the liquid flow and increase the friction area. In practice, the optimal number of guide vanes at the design size can be determined through theoretical planning or optimization experiments (using the optimization method). In the flow channel of the transfer section, it should be ensured that the liquid flow has no sudden change in speed and direction. In this way, the axial displacement will be completed at a low speed, the peripheral speed will be basically maintained, and local resistance losses such as commutation losses will be greatly reduced.

向心导轮增压流道段的截面积扩张率及其变化的设计较为复杂。作为力学参数，它应该随泵送介质粘滞系数的大小增减，因为它是决定沿途阻力型导流之动能损耗率 ₂的关键要素之一。作为几何参数，将扩张率定义为导流圆心角上的函数较为方便。函数值的分布决定于约束流道边界的导叶之曲率半径的分布，考虑旋转对称性，这就是同一导叶的前后两相关点的曲率半径的分布，而流道宽度则直观地体¾¾为沿途相关点组的曲率半径差别的积累，其中相关点的距离与流道数有关，随导流圆心角的变化而改变。由于全程减速比等于入出口截面积的反比，根据该扩张率的分布和该反比，用差分数值解法直接计算出相关点组及其到相关流道中线的距离，就可以逐点算出导叶坐标，从而精确地设计出所要求的导叶形状。设计时可以采用常数扩张率，但优化方案是以变扩张率为基础的。 The design of the cross-sectional area expansion rate of the supercharged runner section of the centrifugal guide wheel and its change is more complicated. As a mechanical parameter, it should increase or decrease with the viscosity coefficient of the pumped medium, because it is one of the key elements that determines the kinetic energy loss rate ₂ of the resistance type diversion along the way. As a geometric parameter, it is convenient to define the expansion rate as a function of the center angle of the diversion circle. The distribution of the function value is determined by the distribution of the curvature radius of the guide vane which constrains the flow channel boundary. Considering the rotational symmetry, this is the distribution of the curvature radius of the two relevant points before and after the same guide vane, and the flow channel width is intuitively The accumulation of differences in the radius of curvature of the relevant point groups along the way, where the distance of the relevant points is related to the number of flow channels and changes with the change of the diversion center angle. Since the overall reduction ratio is equal to the inverse ratio of the cross-sectional area of the inlet and outlet, according to the distribution of the expansion rate and the inverse ratio, the differential point method is used to directly calculate the relevant point group and its distance to the centerline of the relevant flow channel, and the vane coordinates can be calculated point by point. , So as to accurately design the required shape of the guide vane. A constant expansion rate can be used in the design, but the optimization scheme is based on a variable expansion rate.

各导流流道的出口汇聚于导轮中心环腔的外圆柱面，该圆柱面到轴套之间的圆环柱形区域是导轮的出口汇流区。如图所示，导轮的轴套外表面是一个使液流转 90度轴向输出的旋转曲面。也可在导轮的圆环柱形出口汇流区安装如图 6所示的径向入流预旋器，预旋器具有速度场整理功能，能使液流在旋转中同时改变轴面速度的方向和大小，使之整体转 90度从轴向输出，安装预旋器能提髙效率和改善变工况运行特性。 The outlets of the guide runners converge on the outer cylindrical surface of the central ring cavity of the guide wheel, and the circular cylindrical area between the cylindrical surface and the shaft sleeve is the exit convergence area of the guide wheel. As shown in the figure, the outer surface of the shaft sleeve of the guide wheel is a rotating curved surface that rotates the fluid by 90 degrees in the axial direction. It is also possible to install a radial inflow pre-spinner as shown in Figure 6 in the circular cylindrical exit confluence area of the guide wheel. And size, make it turn 90 degrees as a whole to output from the axial direction. Installing a pre-spinner can improve efficiency and improve the operating characteristics under variable conditions.

向心导轮的结构特别适合于采用两合模成型工艺制造，批量生产的成本很低。参照图 16，图中给出了髙势比叶轮腔与向心导轮组合之转移段流道的示意性结构。其中， 111 是导轮外壳上构成转移段流道腔及其腔壁支撑的区域， 112 是转移段流道导轮部分的一个断面 113是转移段流道叶轮腔部分的一个断面， 114是叶轮腔盖， 115是导轮的后向底面， 116 是新周期开始时流道深度位置， 117 是流道轴向正位于底部平面的位置， 118是两部分截面分界线和截止隔舌出现的位置， 119是截面叶轮腔部分的最小边际曲线， 120是截面叶轮腔部分的最大边际曲线。图中放大部分标出了转移段流道截面变化的示意性轮廓，为简单起见，不考虑径向坐标的变化。向心导.轮的转移段流道起自前一导流流道入口段截止隔舌（其轴面投影为线段The structure of the centrifugal guide wheel is particularly suitable for manufacturing by a two-clamp molding process, and the cost of mass production is very low. Referring to FIG. 16, a schematic structure of a flow passage of a transition section in which a pseudopotential ratio impeller cavity and a centripetal guide wheel are combined is shown. Among them, 111 is a region on the outer shell of the guide wheel constituting the transfer section flow channel cavity and its cavity wall support, 112 is a section of the transfer section flow channel guide wheel section 113 is a section of the transfer section flow channel impeller cavity section, 114 is an impeller Cavity cover, 115 is the rear bottom surface of the guide wheel, 116 is the depth position of the runner at the beginning of the new cycle, 117 is the position where the runner is axially located at the bottom plane, 118 is the position where the two-section cross-section boundary line and the cutoff tongue appear 119 is the minimum marginal curve of the impeller cavity section, and 120 is the maximum marginal curve of the impeller cavity section. The enlarged part in the figure marks the schematic contour of the cross section of the flow channel in the transfer section. For simplicity, the change in radial coordinates is not considered. The flow channel of the transfer section of the centripetal guide wheel starts from the cutoff tongue of the inlet section of the previous diversion channel (the axial plane is projected as a line segment)

118 ) ，到所连通 ¾导流流道入口段截止隔舌止。该流道跨越叶轮腔和导轮，分为叶轮腔部分和导轮部分，前者是叶轮出口圆柱面与叶轮腔盖围成的汇流空间，由该前盖临腔壁面之外沿曲面形状确定，后者是导流流道入口段，贯通于叶轮腔。两部分装配吻接合一，其合成截面的形状和面积随导轮圆心角的变化而周期性变化。其规律是： 118), to the stop of the connecting section of the diversion channel. The flow path spans the impeller cavity and the guide wheel, and is divided into an impeller cavity part and a guide wheel part. The former is a confluence space surrounded by the impeller outlet cylindrical surface and the impeller cavity cover. The front cover is determined along the curved surface outside the cavity wall surface. The latter is the inlet section of the diversion channel, which runs through the impeller cavity. The two parts are assembled and joined together, and the shape and area of the composite section change periodically with the change of the center angle of the guide wheel. The law is:

a、从起点到终点，随着导流圆心角的增大，合成截面的面积从最小值线性增大到最大值。其比例系数等于叶轮转过单位角度排出的液流体积设计值除以液流出口绝对速度设计值，或者还乘以一个^;于 1而小于导轮增压流道最小扩张比的扩张系数，从而使转移段流道也具有减速增压功能。' a. From the start point to the end point, as the diversion center angle increases, the area of the composite section linearly increases from the minimum value to the maximum value. Its proportionality factor is equal to the design value of the volume of the liquid flow discharged by the impeller through a unit angle divided by the design value of the absolute speed of the liquid flow outlet, or it is multiplied by ^; Thus, the flow passage of the transfer section also has a deceleration and pressure increasing function. '

其中，两部分的截面积是分两段分别变化的。从起点到前一导流流道增压段正位点，即其截面最后端移到流道底平面上如图中 117的点（角度），叶轮腔部分截面积从最小值线性增大到最大值，导轮部分截面积保持为 0不变。从该点到终点，叶轮腔部分截面积从最大值线性减小到最小值，导轮部分截面积从 0线性增大到最大值。 Among them, the cross-sectional area of the two parts is changed in two sections. From the starting point to the positive position of the pressure-increasing section of the previous diversion runner, that is, the end of its cross-section is moved to the point (angle) at the bottom plane of the runner as shown at 117 in the figure, the cross-sectional area of the impeller cavity increases linearly from the minimum value to The maximum value, the cross-sectional area of the guide wheel part remains at 0. From this point to the end point, the cross-sectional area of the impeller cavity decreases linearly from the maximum to the minimum, and the cross-sectional area of the guide wheel linearly increases from 0 to the maximum.

b、上述合成截面积最小值和叶轮腔部分截面积最小值相等，等于图中隔舌出现位置 118直线段、曲线 119和叶轮圆柱面母线构成的曲边三角形的面积，这是由液流最大轴向加速度的限幅值导出的。曲线 119由两段椭圆弧与中间一段圆弧吻接而成，其解析参数由截面积和端点坐标确定。合成截面积的最大值等于其最小值加上导轮部分截面积的最大值，后者等于合成截面积增大比例系数与从起点到终点所绕过的圆心角的乘积。叶轮腔部分截面积的最大值等于图中隔舌出现位置 118直线段、曲线 120和叶轮圆柱面母线构成的曲边三角形的面积。曲线 120是导流流道入口段截止期间汇流流道截面之最大边际，由两段椭圆弧吻接而成，其解析参数由端点坐标和导流流道入口段截止期间合成截面积的增量确定。 b. The minimum value of the composite cross-sectional area is the same as the minimum cross-sectional area of the impeller cavity, which is equal to the area of the curved triangle formed by the straight line segment 118, the curve 119, and the cylinder generatrix of the impeller. Derived from the limit value of the axial acceleration. Curve 119 is composed of two elliptical arcs and a middle arc. The analytical parameters are determined by the cross-sectional area and the coordinates of the endpoints. The maximum value of the composite cross-sectional area is equal to its minimum value plus the maximum value of the cross-sectional area of the guide wheel part, which is equal to the product of the ratio of the increase of the composite cross-sectional area and the center angle of the circle from the start to the end. The maximum sectional area of the impeller cavity is equal to the area of the curved triangle formed by the straight line segment 118, the curve 120, and the generatrix of the impeller's cylindrical surface. Curve 120 is the maximum margin of the cross section of the manifold during the cut-off period of the inlet section of the diversion channel, which is composed of two elliptical arcs. The analytical parameters are the increase in the cross-sectional area of the cross section during the cut-off period of the section of the inlet section determine.

c、从起点到终点，随着导流圆心角的增大，两部分截面的形状分两段分别变化。叶轮腔部分在其截面积增大期间，截面形状为曲边三角形，其曲线边由曲线 119位置开始，经一系列类似曲线的中间过程变化到曲线 120。导轮部分在其截面积增大期间，截面形状由起始直线段 118开始，经历多种变化：首先是以 118为长轴的长半椭圆，其短半轴逐渐增大；成为半圆后，改为半圆边际连续前移，形成前半圆后接矩形的截面；当隔舌出现时，半圆移到 116位置，转移段流道与叶轮腔隔开而成为增压流道。 c. From the start point to the end point, as the diversion center angle increases, the shape of the cross section of the two parts changes in two sections. During the increase of the cross-sectional area of the impeller cavity, the cross-sectional shape is a curved triangle, and its curved edges start from the position of curve 119 and change to curve 120 through a series of intermediate processes similar to the curve. During the increase of the cross-sectional area of the guide wheel, the cross-sectional shape starts from the starting straight line segment 118 and undergoes various changes: First, the long semi-ellipse with 118 as its long axis, and its short semi-axis gradually increases; after becoming a semicircle, Instead, the semi-circle margins are continuously moved forward to form a rectangular cross section followed by a front semi-circle. When the tongue appears, the semi-circle moves to the 116 position, and the transfer section flow path is separated from the impeller cavity to become a pressurized flow path.

d、从隔舌出现开始， 116和 118限定的流道继续前移和变形。在少量前移形成隔舌的最小物理宽度以后，其后向侧边际线由隔舌前向边际直线段变为向后弯曲的长半椭圆，其短半轴连续增加，成为牟圆后再改为平移，直到进入流道底面 117为止。该过程中，其前向边际半圆连续前移，直到与导轮底平面 115相切时，改为连续压缩半圆为半椭圆，最后变为直线与底平面贯通。增压流道截面前移正位期间，其面积按减速增压要求变化。上述导轮部分的截面变化过程中，其中心线的径向坐标可能发生变化。当导叶起点是流道入口段起点时，中心线径向坐标连续减小，当导叶起点是流道入口段终点时，中心线径向坐标不变。 ·■ d. From the appearance of the tongue, the flow channels defined by 116 and 118 continue to move forward and deform. After a small amount of forward movement to form the minimum physical width of the tongue, the posterior lateral marginal line changes from the forward-to-margin straight line segment of the tongue to a curved long semi-ellipse. The short semi-axis increases continuously and becomes a round shape. For translation, it enters the bottom surface 117 of the runner. In this process, the forward marginal semicircle is continuously moved forward until it is tangent to the bottom plane 115 of the guide wheel, and the semicircle is continuously compressed into a semi-ellipse, and finally a straight line penetrates the bottom plane. During the section of the booster runner moving forward, its area changes according to the deceleration booster requirement. During the change of the cross section of the above-mentioned guide wheel part, the radial coordinate of its centerline may change. When the starting point of the guide vane is the starting point of the inlet section of the flow channel, the radial coordinate of the center line continuously decreases. When the starting point of the guide vane is the end point of the inlet section of the flow channel, the radial coordinate of the center line does not change. · ■

转移段流道设计的关键在于严格控制流道截面的变化，包括两部分截面的形状和面积的变化。从最小截面积开始，经叶轮腔变截面汇流、联合变截面汇流、分割截面等过程，采用了长半椭圆变短半轴、半圆平移等构造流道截面边际并线性扩大截面积的方法，能产生所需的速度场分布并控制边际摩擦损耗率指标，其中流速的切向、径向和轴向分量的变动源自壁面法向力的冲量积分及其对压力分布的动态影响。速度场分布及其空间变化率对流道流态的影响是高度敏感的，对效率有重大影响，弄不好还产生水锤震颤效应或空化气蚀效应。这是一个多功能曲面设计的复杂问题，所公开的方法还不是最优的，但防止破坏性效应和控制摩擦面积及增大当量直径的目标，已经得到了体现。虽然，所动用的几何规划技巧使这种设计难于用传统方法表达和制订加工工艺，但釆用现代 CAD、 CAM技术及模成型工艺后，实现起来并不困难，并且成本较低。参照图 17，图中给出了一种闭式叶轮超减摩和导轮控制转移段流道之结构示意图。其中， 121 是导轮外壳上构成转移段流道及其腔壁支撑的区域， 122是转移段流道截面导轮部分， 123是前盖延伸超减摩闭式叶轮的装配位置， 124是叶轮腔盖， 125是导轮后端面， 126是隔舌出现时转移段流道的前向侧底部， 127是增压流道正位后的后向侧底部， 128是隔舌出现的位置， 129是转移段流道之叶轮腔部分的截面， 130是叶轮叶片尾部， 131是叶轮流道， 132是延伸的叶轮盖， 133是叶轮腔盖。 The key to the design of the flow channel in the transfer section is to strictly control the changes in the cross section of the flow channel, including the changes in the shape and area of the two sections. Starting from the minimum cross-sectional area, through the process of variable cross-section confluence, combined variable cross-section confluence, and split cross-section of the impeller cavity, a method of constructing the flow channel cross-section margin and linearly expanding the cross-sectional area by using a long semi-ellipse to shorten the semi-axis, semi-circular translation, etc. Generate the required velocity field distribution and control the marginal friction loss index. The changes in the tangential, radial, and axial components of the flow velocity are derived from the impulse integral of the wall normal force and its dynamic impact on the pressure distribution. The velocity field distribution and its spatial change rate are highly sensitive to the influence of the flow path flow pattern, which has a significant impact on the efficiency. If it is not good, water hammer chatter effect or cavitation cavitation effect will be produced. This is a complex problem of multifunctional curved surface design. The disclosed method is not yet optimal, but the goals of preventing destructive effects and controlling frictional areas and increasing the equivalent diameter have been reflected. Although the geometric planning techniques used make it difficult to express and formulate the manufacturing process using traditional methods, it is not difficult and cost-effective to implement modern CAD, CAM and molding processes. Referring to FIG. 17, a structure diagram of a flow path of a closed impeller super friction reduction and guide wheel control transfer section is shown. Among them, 121 is the area on the outer shell of the guide wheel constituting the transfer section flow channel and its cavity wall support, 122 is the section of the transfer section flow channel section guide wheel, 123 is the assembly position of the front cover extended super friction reducing closed impeller, 124 is the impeller Cavity cover, 125 is the rear end face of the guide wheel, 126 is the forward side bottom of the transfer section when the diaphragm appears, 127 is the rear side bottom after the pressurized runner is aligned, 128 is the location where the tongue appears, 129 Is the cross section of the impeller cavity part of the transfer channel, 130 is the tail of the impeller blade, 131 is the impeller flow channel, 132 is the extended impeller cover, and 133 is the impeller cavity cover.

图中放大部分标出了导轮控制转移段流道截面变化的示意性边际轮廓。这种向心导轮的导叶具有与圆周腔壁吻接的变曲率起点，该起点是转移之后的增压流道正位点，由该点决定转移段流 m中心的径向坐标。转移段流道截面分为叶轮腔部分和导轮部分，两部分装配吻接合一。截面的叶轮腔部分被叶轮盖包裹于叶轮中，具有固定的面积和形状，由其承担轴面速度分量的转向调整。截面的导轮部分是两个相邻隔舌之间的一段与叶轮腔连通的空间的横断面，该截面独立控制汇流和切向及轴向运动过程。随着导流圆心角的增加，截面的导轮部分以隔舌为起点和终点周期性地变化，一个周期内的变化规律是： The enlarged part of the figure marks the schematic marginal contour of the cross-section change of the runner in the control wheel transfer section. The guide vanes of this centripetal guide wheel have a starting point of variable curvature that is in contact with the wall of the circumferential cavity. The starting point is the positive position of the pressurized runner after the transfer, and this point determines the radial coordinate of the center m of the transfer section. The cross section of the flow channel of the transfer section is divided into the impeller cavity part and the guide wheel part, and the two parts are fitted with a kiss joint. The impeller cavity section of the cross section is wrapped in the impeller by the impeller cover, has a fixed area and shape, and it carries out the steering adjustment of the speed component of the shaft surface. The guide wheel section of the cross section is a cross section of a space between two adjacent separating tongues which communicates with the impeller cavity. This section independently controls the process of confluence and tangential and axial movement. With the increase of the diversion center angle, the section of the guide wheel periodically changes with the tongue as the starting point and the ending point. The change law in a cycle is:

a、截面积从 0线性增大到最大值。增大比例系数等于叶轮转过单位角度排出的液流体积设计值除以液流出口绝对速度设计值，或者还乘以一个大于 1而小于导轮增压流道最小扩张比的扩张系数。截面积最大值等于增大比例系数乘以流道入口段对应的圆心角。当增大比例系数包含扩张系数因子时，转移段流道具有减速增压功能。 a. The cross-sectional area increases linearly from 0 to the maximum. Increasing the proportionality factor is equal to the design value of the liquid volume discharged by the impeller through a unit angle divided by the design value of the absolute velocity of the liquid outlet, or it is multiplied by an expansion coefficient greater than 1 and smaller than the minimum expansion ratio of the booster runner of the guide wheel. The maximum cross-sectional area is equal to the increase of the proportionality factor multiplied by the center angle of the corresponding channel inlet section. When the increase scale factor includes an expansion coefficient factor, the transition section flow passage has a deceleration and pressure increasing function.

b、截面由起始真线段 128开始，经历多种形状变化：首先是以 128为长轴的长半椭圆，其短半轴逐渐增大；成为半圆后，改为半圆边际连续前移，形成前半圆后接矩形的截面；当隔舌出现时，半圆移到 126位置，转移段流道与叶轮腔隔开而成为增压流道。 c、隔舌出现和隔离叶轮腔后， 126和 128限定的流道成为增压流道，仍继续前移和变形。在少量前移留下隔舌的最小物理宽度后，其后向侧边际线由直线段变为向后弯曲的长半椭圆，其短半轴连续加长，成为半圆后再改为平移，直到最后点进入流道底面 127为止。该过程中，其前向边际半圆连续前移，直到与导轮底平面 125相切时，改为连续压缩半圆为半椭圆，最后变为直线与底平面贯通。上述轮廓线或质心移动的速度应该大于汇流期间的相应移动速度一个恰当的百分比，例如大于 50% , 以使隔舌的截面积和强度能够连续增加。增压流道截面前移正位期间，其面积按减速增压要求变化。 b. The section starts from the initial true line segment 128 and undergoes various shape changes: First, the long semi-ellipse with 128 as the long axis, and the short semi-axis gradually increases; after becoming a semicircle, it is changed to a semicircle and the margins move forward continuously to form The front semicircle is followed by a rectangular cross section; when the tongue appears, the semicircle moves to the 126 position, and the flow passage of the transfer section is separated from the impeller cavity to become a pressurized flow passage. c. After the diaphragm appears and isolates the impeller cavity, the flow channel defined by 126 and 128 becomes a pressurized flow channel, which continues to move forward and deform. After a small amount of forward movement leaves the minimum physical width of the tongue, the rear side marginal line changes from a straight line segment to a long curved semi-ellipse that is curved backward. The short semi-axis is continuously extended to become a semicircle and then changed to translation until the end. Point into the bottom surface of the runner 127. In this process, its forward marginal semicircle is continuously moved forward until it is tangent to the bottom plane 125 of the guide wheel, and the semicircle is continuously compressed into a semi-ellipse, and finally a straight line penetrates the bottom plane. The moving speed of the contour line or the center of mass should be greater than the corresponding moving speed during the confluence by an appropriate percentage, such as greater than 50%, so that the cross-sectional area and strength of the tongue can be continuously increased. During the section of the booster runner moving forward, its area changes according to the deceleration booster requirement.

上述方案的复杂程度明显小于图 16所示的设计，其速度场分布情况和边际摩擦损耗率指标也优于前者，其流速轴面分量的转向动反力和壁面法向力的分布均匀性也更好，压力脉动也很小。这种设计是以与前盖延伸的闭式叶轮配套为前提的，当进行端腔充气减摩时，由于前盖侧端腔的减摩面覆盖了转移段流道叶轮腔部分的全部摩擦面，按 5次律计算，显然能产生较大的转移段流道减摩效益，因而谓之超减摩。忽略叶轮盖内侧的相对速度摩擦，则转移段流道的摩擦面将只剩下导轮部分。由于该部分截面的边际线不是封闭曲线，因而最佳截面形状将不再是圆形，如欲进行优化，只需作同截面积下的非封闭边际线长度的最小化规划就行了。上述方案是一个近似优化的简单设计。 The complexity of the above scheme is significantly smaller than the design shown in Figure 16. Its velocity field distribution and marginal friction loss rate index are also better than the former, and the uniformity of the steering dynamic reaction force and wall normal force distribution of the axial component of the flow velocity is also Even better, the pressure pulsation is also small. This design is based on the premise that it is matched with the closed impeller with the front cover extended. When the end cavity is inflated to reduce friction, the friction reduction surface of the front cover side end cavity covers the entire friction surface of the impeller cavity portion of the flow channel of the transfer section. According to the calculation of the fifth-order law, it can obviously produce a large friction reduction benefit in the flow passage of the transfer section, so it is called super friction reduction. Ignoring the relative speed friction on the inner side of the impeller cover, the friction surface of the runner of the transfer section will only have the guide wheel portion. Because the margin line of the partial section is not a closed curve, the optimal cross-sectional shape will no longer be circular. To optimize, you only need to make a plan for minimizing the length of the non-closed margin line under the same cross-sectional area. The above scheme is a simple design with approximate optimization.

图 17所示方案同样需要采用三维 CAD才能设计出表达清楚的加工蓝图，釆用模成型工艺的制造成本也较低，其中叶轮盖是冲压成形的。参照图 18, 图中给出了一种中心蜗道分汇流变角度出管对称端盖结构示意图。其中， 141是端盖的装配止口， 142是承压盖板， 143为中心蜗道深部入口， 144为中心蜗道浅部， 145为流道围护结构支撑的轴承腔， 146为中心蜗道的轴向投影， 147为中心蜗道深部与浅部之间的隔舌，为跨接环形入口内外边际圆的一条径向直线段，是蜗道的起始线， 148是中心蜗道浅部， 149是轴套， 150是环形入口的外圆。 The solution shown in Figure 17 also requires the use of 3D CAD to design a clearly expressed processing blueprint. The manufacturing cost of the die-casting process is also low, and the impeller cover is stamped. Referring to FIG. 18, a schematic diagram of a symmetrical end cap structure of a central worm channel branching and merging angle outlet pipe is shown. Among them, 141 is the assembly stop of the end cover, 142 is the pressure-bearing cover plate, 143 is the deep entrance of the central worm channel, 144 is the shallow central worm channel, 145 is the bearing cavity supported by the flow channel envelope structure, and 146 is the central worm The axial projection of the channel, 147 is the tongue between the deep and shallow part of the central worm, a radial straight line that bridges the inner and outer marginal circles of the annular entrance, is the starting line of the worm, and 148 is the shallow of the central worm. 149, the shaft sleeve, 150 is the outer circle of the annular entrance.

对称端盖模块由带装配止口 141的承压盖板 142、盖板上的三维蜗道 144及其环形出入口 143、与蜗道接口 146连通的直线段管道、蜗道结构体支承的轴套 149和轴承腔 145 等结构组成，是一个多结构一体化的零件。端盖的中心蜗道是一种合成切向、径向和轴向运动的三维流道，其起始位置是环形入口圆平面上的隔舌 147，其末端位置在增加了径向和轴向坐标的隔舌下方。蜗道入出口及其内部均具有三个方向上的运动连续性，其动力学特征是流体加速度的时间变化率小，流场参数和壁面法向力的空间变化率也较小并且时不变，这是蜗道流场稳定的力学特征之一。图上难以标明的出自力学考虑的几何设计还包括：由隔舌开始，蜗道截面积与圆心角成正比地增加，蜗道底部中心的径向和轴向坐标随着扩大截面积的需要逐渐增加，形成三维扩展的蜗形斜坡，转过一周后进入隔舌的下面，随后与直线段管道切向吻接。蜗道截面的形状变化规律是：起点为隔舌直线段，然后为长轴在入口平面上的变短轴长半椭圆，成为半圆后逐渐下沉并光滑地加大下部的曲率半径，沿一曲率变化率适当的渐开弧线发展，直到进入隔舌的下面，然后保持截面积地变形为圆截面与管道吻接。 The symmetrical end cover module is composed of a pressure-bearing cover plate 142 with an assembly stop 141, a three-dimensional worm channel 144 and its annular inlet and outlet 143 on the cover plate, a linear segment pipe communicating with the worm interface 146, and a shaft sleeve supported by the worm structure. 149 and bearing cavity 145 and other structures, is a multi-structure integrated parts. The central worm channel of the end cap is a three-dimensional flow channel that synthesizes tangential, radial and axial movements. Its starting position is the tongue 147 on the circular plane of the circular inlet. The end position is increased in the radial and axial directions. Below the tongue of the coordinates. The entrance and exit of the volute and its interior have movement continuity in three directions. Its dynamic characteristics are that the time change rate of fluid acceleration is small, and the spatial change rates of flow field parameters and wall normal force are also small and constant. This is one of the mechanical characteristics of turbulent flow field stability. The geometric design due to mechanical considerations that are difficult to indicate in the figure also includes: Starting from the tongue, the cross-sectional area of the volute increases in proportion to the center angle, and the radial and axial coordinates of the center of the volute bottom gradually increase with the need to expand the cross-sectional area. It increases to form a three-dimensionally expanding snail slope. After one week of rotation, it enters the lower part of the tongue, and then tangentially connects with the straight-line pipe. The shape of the worm section is as follows: the starting point is a straight segment of the tongue, and then the long axis becomes a semi-ellipse with a shortened axis on the entrance plane. After becoming a semicircle, it gradually sinks and smoothly increases the radius of curvature of the lower part. The involute curve with an appropriate curvature change rate develops until it enters the lower part of the tongue, and then maintains a cross-sectional area to deform into a circular cross-section to fit the pipe.

分析并充分利用对称端盖的几何及力学特性，采用本发明前述的模块化组合方法，对端盖进行部件技术设计上的目标功能或目标用途用法的下列扩充，将产生离心泵设计方法和应用方式上的许多改进可能性： Analyze and make full use of the geometric and mechanical characteristics of symmetrical end caps. Using the aforementioned modular combination method of the present invention, the following extensions of the target function or target use of the component technical design of the end cap will result in centrifugal pump design methods and applications. Many improvement possibilities in the way:

a、利用端盖环形接口及三维蜗道内部兼容和约束三维运动的特性，能构造或自适应生成叶轮和导轮多流道工作的分流、汇流、旋转、转向等连接边界条件，使之既满足叶轮入口的连接要求，又满足向心导轮出口的连接要求，并且对于单级泵和多级泵具有普遍性，这就产生了用作单级泵和多级泵通用的流场边界模块的模型，成为支持模块化组合并实施保守环量设计的技术基础； a. Utilizing the characteristics of the end cap annular interface and the compatibility of three-dimensional motion inside the three-dimensional worm trajectory, it is possible to construct or adaptively generate the boundary conditions such as the shunt, confluence, rotation, and steering of the impeller and guide wheel in the multi-flow channel. Meet the requirements for the connection of the impeller inlet and the connection of the centrifugal guide wheel outlet, and it is universal for single-stage and multi-stage pumps, which has produced a flow field boundary module used as a single-stage and multi-stage pump Model becomes the technical basis for supporting modular combination and implementing conservative loop design;

b、利用端盖环形接口及三维蜗道内部的方向兼容性和三维运动的连续性，扩展为流入流出方向互反的、分流汇流性质互反的技术设计兼容性，据以用作前后通用的流场对称边界模块，成为支持模块化组合所需连接模式的边界基础； b. Utilizing the directional compatibility of the end cap annular interface and the three-dimensional worm trajectory and the continuity of three-dimensional motion, it expands to the compatibility of the technical design compatibility of the reverse inflow and outflow directions and the reversal and confluence properties. The flow field symmetrical boundary module becomes the boundary basis for supporting the connection mode required for the modular combination;

c、利用端盖环形接口及三维蜗道内部的三个方向的运动连续性，限制和优化流速的空间和时间变化率，使之最小化，据以用作具有稳定性和低损耗特性的流场边界模块，以使得模块化组合所需的连接模式性能更好； c. Utilize the continuity of movement in the three directions of the end cap annular interface and the three-dimensional volute to limit and optimize the spatial and temporal rate of change of the velocity to minimize it, and use it as a flow with stability and low loss characteristics. Field boundary module to make the connection mode performance required by the modular combination better;

d、利用端盖环形接口和装配止口的旋转对称性，以及所带蜗道和引出管基于隔舌相对角定位的特点，据以构造前后盖各自独立变角度出管的功能，以支持模块化组合所需的装配结构设计， '并简化与实际液流***的连接关系； d. Utilizing the rotational symmetry of the ring-shaped interface of the end cap and the assembly stop, and the relative positioning of the worm and the lead-out tube based on the relative angle of the separating tongue, so as to construct the functions of the independently variable-angle outlet tubes of the front and rear covers to support the module. Assemble the required assembly structure design, and simplify the connection relationship with the actual fluid flow system;

e、利用端盖之承压盖板、轴承座等结构进行了一体化设计的特点，在技术和工艺设计上确定为可模成型的单一零件型功能部件。在蕴含上述技术扩充以后，就可构造支持连接模式的装配尺寸和接口参数可标准化的新型端盖模块，以扩大其体积小、设计简单、成本低、功能强的价值运用范围。 e. Utilizing the features of the integrated design of the pressure-resistant cover plate and bearing seat of the end cover, it is determined as a moldable single-part functional component in terms of technology and process design. After the expansion of the above technology is included, a new end cap module with standardized assembly dimensions and interface parameters that support the connection mode can be constructed in order to expand the value application range of its small size, simple design, low cost, and strong functions.

上述技术扩充是一种恰得所需的设计。将向心导轮与对称端盖配套，进而扩大为向心增压模块与变角度出管对称端盖模块配套，可以使离心泵的体积大为缩小，其变角度出管的功能更是为用户所欢迎，其对称性、其技术设计及应用方法扩充以后增加的通用性，将有助于简化离心泵的设计、制造和使用。所有这些特点及利用特点的功能扩充均有利于同时降低生产成本和用户的总拥有成本。这种设计在单级泵中使用时，其优势更是特别明显。例如图 10、图 13、图 14所示的悬臂泵，其导流器和汇流流道在叶轮***叠加的尺寸浪费，使人感到特别可惜，应用本实施例公开的设计，这种缺点就得以避免。从后续公开的实施例的说明中，对称端盖模块的应用优势将能看得更清楚。图 19〜图 27是依据模块化方法轴向组合叶轮与向心导轮构成向心增压模块的实例。参照图 19〜图 27，首先综合说明这些叶导轮组合向心增压模块的共同特点和优势，然后将各自的个性特征及其效果简要地枚举列于表 10。 The technical expansion described above is just the right design. Matching the centripetal guide wheel with the symmetrical end cap, and then expanding it to the centripetal booster module and the variable angle outlet tube symmetrical end cover module, which can greatly reduce the volume of the centrifugal pump, and its variable angle outlet tube function is Users welcome that its symmetry, its technical design, and the increased versatility of its application methods will help simplify the design, manufacture, and use of centrifugal pumps. All these features and the functional expansion utilizing them are beneficial to reduce both the production cost and the total cost of ownership of the user. The advantages of this design are particularly evident when used in single-stage pumps. For example, in the cantilever pump shown in FIG. 10, FIG. 13, and FIG. 14, the size of the deflectors and the manifolds stacked on the periphery of the impeller is wasted, which makes people feel particularly unfortunate. By applying the design disclosed in this embodiment, this disadvantage can be achieved avoid. From the description of the embodiments disclosed later, the application advantages of the symmetrical end cap module will be more clearly seen. 19 to 27 are examples of forming a centripetal booster module by axially combining an impeller and a centrifugal guide wheel according to a modular method. Referring to FIG. 19 to FIG. 27, first, the common features and advantages of these impeller-guided centrifugal booster modules are comprehensively explained. The individual characteristics and their effects are briefly listed in Table 10.

这些模块是包含不同叶轮技术或工艺的赋能模块，按照 "液流从近轴环形口带环量流入和流出" 的连接模式，用同一个规格的 1个或多个赋能模块串联，并与 2个对应规格的对称端盖模块组合，能组成不同型号的、具有模块互换性的向心增压离心泵。 These modules are energization modules containing different impeller technologies or processes. In accordance with the connection mode of "fluid flow in and out from the paraxial annular mouth with annular flow," one or more energization modules of the same specification are connected in series, and Combined with two symmetrical end cover modules of corresponding specifications, it can form different types of centripetal booster centrifugal pumps with module interchangeability.

向心增压模块由向心导轮、叶轮和叶轮腔盖板轴向组合而成，有的还配有其他功能附件，具有标准化的接口参数和装配尺寸。其中，向心导轮是模成型一体化制造的，其腔侧平面或旋转曲面与叶轮形成间隙配合，腔侧外沿有依据叶轮参数设计的转移段流道前向边际曲面，其级段式外壳上有装配止口，与外壳一体相连的中隔板作为导叶支承基板，同时起隔离叶轮腔和导轮腔并承受其间压差的作用；叶轮腔盖板为模成型减重结构零件，其腔侧旋转曲面与叶轮形成间隙配合，腔侧外沿有依据叶轮参数设计的转移段流道后向边际曲面。装配时，顺序装入导轮、叶轮和叶轮腔盖板，三者分别通过外壳止口、转轴和导轮之叶轮腔定位。运行时，液流从模块入口轴向流入旋转的叶轮流道，从中接受叶片法向力功沿途加速并积分离心力功增加比能，经转移段流道进入导轮，在其中减速增压后，转 90 度从近轴环形开口带环量流出模块。 The centrifugal booster module is an axial combination of a centrifugal guide wheel, an impeller, and an impeller cavity cover. Some are also equipped with other functional accessories, with standardized interface parameters and assembly dimensions. Among them, the centrifugal guide wheel is integrally manufactured by molding, and the cavity side plane or rotating curved surface forms a clearance fit with the impeller. The outer edge of the cavity side has a forward marginal curved surface of the transfer section flow channel designed according to the impeller parameters. The casing has an assembly stop, and a middle partition plate integrally connected with the casing serves as a guide vane supporting substrate, and at the same time, it plays a role of isolating the impeller cavity and the impeller cavity and withstanding the pressure difference therebetween; The cavity-side rotating curved surface cooperates with the impeller to form a clearance, and the outer edge of the cavity side has a rearward marginal curved surface of the transfer section flow channel designed according to the impeller parameters. During assembly, the guide wheel, the impeller and the impeller cavity cover are sequentially installed, and the three are respectively positioned through the casing stop, the shaft and the impeller cavity of the guide wheel. During operation, the liquid flow flows axially from the inlet of the module into the rotating impeller flow path, receives the normal force work of the blade to accelerate along the way and integrates the centrifugal force work to increase the specific energy, enters the guide wheel through the transfer section flow path, and after decelerating and supercharging, Rotate 90 degrees out of the module from the paraxial ring-shaped opening.

向心增压模块是模块化组合方法和保守环量设计的产物。向心导轮使向心增压模块具有液流流程、流道连接、流态参数的空间周期性——从叶轮入口到导轮出口的周期性，这种周期性是模块划分的原理性基础。这种基础是反演需求的模块目的性设计的结果，并不是对偶然发现的利用。保守环量设计旨在优化流场速度的空间和时间变化率，来源于对流体机械的局部激励和局部损耗的宏观规律的思考。完备约束的概念和对流体动量矩惯性的尊重则是保守环量设计的观念基础。这些思考和原则已经贯彻到本发明的前述系列特征中了，它们在优化液流转移的动力学过程、稳定流场和减小损耗等方面均具有良好的效果，甚至连流道壁的动反力载荷都可以减轻。将这些设计组织和应用于具有全局性价值的模块化方法中，将更能发挥作用。基于上述思想和技术路线，本发明为图 19〜图 27实例中的向心增压模块扩充和规划了如下的共性特征和功能性能特点： Centripetal boost module is the product of modular combination method and conservative loop design. The centripetal guide wheel enables the centripetal booster module to have the spatial periodicity of the fluid flow process, the flow channel connection, and the flow parameter-the periodicity from the impeller inlet to the guide wheel outlet. This periodicity is the principle basis of the module division . This basis is the result of the purposeful design of the module for inversion requirements, not the use of accidental discovery. The conservative loop design aims to optimize the spatial and temporal rate of change of the flow field velocity, which is derived from the consideration of the macroscopic laws of local excitation and local loss of fluid machinery. The concept of complete constraints and respect for the moment of inertia of fluid momentum are the conceptual basis of conservative ring design. These thoughts and principles have been implemented in the aforementioned series of features of the present invention. They have good effects in optimizing the dynamic process of liquid flow transfer, stabilizing the flow field, and reducing losses, and even the dynamic reaction of the flow channel wall. Force loads can be reduced. Organizing these designs and applying them to a modular approach with global value will be more effective. Based on the above ideas and technical routes, the present invention expands and plans the following common features and functional performance features for the centripetal booster module in the examples of Figure 19 to Figure 27:

a、向心增压模块由各类叶轮和向心导轮轴向组合而成，其内外装配尺寸和接口参数是标准化的，其互换性覆盖设计、生产和使用过程。这种设计能为企业和用户带来许多利益和方便，并能大大地丰富和快速地传播离心泵的技术类型。 a. The centrifugal booster module is composed of various impellers and centripetal guide wheels in axial combination. The internal and external assembly dimensions and interface parameters are standardized, and their interchangeability covers the design, production and use processes. This design can bring many benefits and conveniences for enterprises and users, and can greatly enrich and quickly spread the type of technology of centrifugal pumps.

b、向心导轮的汇流及转移段流道与增压流道串联而不是并联，从而不存在兼顾汇流和增压的约束沖突，它们均具有完备的约束壁面，且转移和增压流道具有可预设的扩张率，能全程避免欠约束和局部激励现象，其增压效率最高可达 98 %。叶轮与导轮之间保持圆周速度过流因而具有液流方向与运行工况无关的特点，使叶导轮接口的速度匹配特性良好，并具有 100%的变工况适应性，流量减少时泵效率反而升高。 C、采用 "液流从近轴环形口带环量流入和流出" 的连接模式，叶导轮直径相同，且导轮轴向尺寸小于叶轮。因此， '模块结构紧凑，体积最小，多级泵体积减小 50%以上，制造成本大幅度降低。叶轮入口和导轮出口的速度分布基本相同，均具有较大的圆周分量。如此设计既能改善叶轮吸入室的速度匹配特性和变工况适应性，又能降低导流负荷和缩短导流流程。较之现有技术，前者属于产生新特性的功能性改进，后者属于提高性能的结构改良，两者的综合效果是改变效率曲线的规律而不仅仅是提升一点或一段的效率数据。 b. The flow path of the confluence and transfer section of the centrifugal guide wheel is connected in series rather than in parallel with the booster flow path. Therefore, there is no constraint conflict that takes into account the convergence and booster pressure. They all have a complete constraint wall surface, and the transfer and booster flow props It has a preset expansion rate, which can avoid under-constraint and local excitation phenomenon, and its boosting efficiency can be up to 98%. The peripheral speed of the impeller and the guide wheel is maintained so that the flow direction is independent of the operating conditions. The speed of the impeller interface is well matched, and it has 100% adaptability to changing conditions. When the flow rate is reduced, the pump Instead, the efficiency increases. C. Adopt the connection mode of "fluid flow in and out from the paraxial annular mouth with annular flow." The impeller diameter is the same, and the axial dimension of the impeller is smaller than the impeller. Therefore, 'the module has a compact structure and the smallest volume. The volume of the multi-stage pump is reduced by more than 50%, and the manufacturing cost is greatly reduced. The speed distribution of the impeller inlet and the guide wheel outlet are basically the same, and both have a large circumferential component. Such a design can not only improve the speed matching characteristics of the impeller suction chamber and adaptability to changing working conditions, but also reduce the diversion load and shorten the diversion process. Compared with the prior art, the former belongs to the functional improvement that generates new features, and the latter belongs to the structural improvement to improve performance. The combined effect of the two is to change the law of the efficiency curve, not just to improve the efficiency data by a point or a paragraph.

d、如实例所枚举模块中的叶轮可组合不同的技术和工艺特征，包括高势比、径向和轴向预旋、抗涡旋和均速化、内减摩、超减摩类创新特征以及传统后弯式设计，也包括半开式、闭式结构特征。组合不同叶轮的模块具有不同的效果。提高势动比和导流效率、提高叶轮程效率、改善抗气蚀特性、提高变工况运行适应性等效果直接来源于叶轮的创新设计，因所述的模块化和数学规划而提高性价比，以及在设计、生产和使用过程中变换组合的互换性产生的诸多便利，则属于模块化组合的效益，其价值亦因技术而异。 d. The impellers in the module enumerated as examples can combine different technical and process characteristics, including high potential ratio, radial and axial pre-spin, anti-vortex and uniform speed, internal friction reduction, and ultra-friction innovations. Features and traditional back-bend design also include semi-open and closed structural features. Combining modules with different impellers has different effects. The effects of improving the potential ratio and flow diversion efficiency, increasing the impeller stroke efficiency, improving the anti-cavitation characteristics, and improving the adaptability of variable operating conditions are directly derived from the innovative design of the impeller, which improves cost-effectiveness due to the modularity and mathematical planning described, And the many conveniences created by the interchangeability of changing combinations in the design, production, and use processes are the benefits of modular combinations, and their values vary by technology.

各种向心增压模块的个性特征及其效果的说明罗列于表 10。 The individual characteristics and effects of various centripetal booster modules are listed in Table 10.

' 表 10 向心增压赋能模块个性特征及其效果说明表图号标示特征的 ' 组合的叶轮技术特征及其组合效果说明 '' Table 10 Individual characteristics and effect description of centripetal boosting module

模块名称半开式叶轮向包含半开式传统叶轮，赋予液流势动比约等于 1的比能增量，图 19 Module name Semi-open impeller direction Contains the traditional semi-open impeller, which gives a specific energy increase of liquid flow potential ratio equal to approximately 1, Figure 19

心增压模块 ' 在向心导轮中部分动能转化为势能。叶轮效率略低于闭式。闭式叶轮向心包含闭式叶轮，赋予液流势动比约等于 1的比能增量，在向心图 20 Cardiac boost module '' Part of the kinetic energy is converted into potential energy in the radial guide wheel. The impeller efficiency is slightly lower than the closed type. Closed impeller centripetal Contains a closed impeller, which gives a specific energy increase of liquid flow potential ratio equal to approximately 1, in centripetal Figure 20

增压模块导轮中部分动能转化为势能。 Booster module Part of the kinetic energy in the guide wheel is converted into potential energy.

包含内减摩闭式叶轮，赋予液流势动比约等于 1的比能增量，减摩闭式叶轮 Contains friction-reducing closed impeller, which increases the specific energy of liquid flow potential ratio equal to approximately 1. The friction-reducing closed impeller

图 21 在向心导轮中部分动能转化为势能；具有前腔阻气间隙、前后向心增压模块 Figure 21 Part of the kinetic energy is converted into potential energy in the centripetal guide wheel

端腔连通均压孔、减摩驱动二相流入管等减摩组件，充气运行时轮盘摩擦损耗降低 82〜95 %，提高效率 5〜9%。 Friction reduction components such as end-cavity pressure equalization holes and anti-friction driving two-phase inflow pipes reduce the disc friction loss by 82 to 95% and increase the efficiency by 5 to 9%.

半开式均速高包含半开式均速高势比叶轮，具有 L形叶片、反切向出口、叶图 22 势比叶轮向心槽尾部加速段、均速岔道等减速设计，其输出液流势动比可高增压模块达 3〜9，其入导速度低，导流损耗小。叶轮效率略低于闭式。闭式均速高势包含闭式均速高势比叶轮，具有 L形叶片、反切向出口、叶槽图 23 比叶轮向心增尾部加速段、均速岔道等减速设计，其输出液流势动比高，其压模块入导速度低，导流损耗低。包含预旋闭式均速高势比叶轮，具有 L形叶片、反切向出口、预旋闭式均速叶槽尾部加速段、均速岔道等减速设计，其输出液流势动比可图 24 高势比叶轮向高达 3〜9，其入导速度低，导流损耗小；包含预旋器，轴向来心增压模块流等速预旋，叶轮入口具有工况变化适应性，提高效率并避免气烛 Semi-open type average speed high includes half-open type average speed high potential ratio impeller, with L-shaped blades, reverse tangential outlet, leaves Figure 22 potential ratio impeller centrifugal groove tail acceleration section, average speed bifurcation and other deceleration design, its output liquid flow The potential-to-dynamic ratio can be as high as 3 to 9 for the booster module, which has a low conduction speed and a small conduction loss. The impeller efficiency is slightly lower than the closed type. Closed average speed high potential includes closed type average speed high potential ratio impeller, with L-shaped blades, counter-tangential outlets, blade grooves The dynamic ratio is high, and the pressure conduction speed of the compression module is low, and the flow loss is low. Contains pre-rotating closed-type average speed high potential ratio impeller, with L-shaped blades, reverse tangential exit, pre-rotating closed-type constant speed impeller tail acceleration section, average speed bifurcation and other deceleration designs. Its output liquid flow potential ratio can be shown in Figure 24 High potential ratio of the impeller is as high as 3 ~ 9, its guide speed is low, and the flow loss is small; it includes a pre-spinner, and the axially-centered supercharged module flow has a constant velocity pre-spin. The impeller inlet has adaptability to working conditions and improves efficiency. And avoid gas candles

包含内减摩闭式均速高势比叶轮，具有 L形叶片、反切向出口、减摩闭式均速叶槽尾部加速段、均速岔道等减速设计，其输出液流势动比可图 25 高势比叶轮向高达 3〜9，其入导速度低，导流损耗小；具有阻气间隙、前后心增压模块端腔连通均压孔、减摩驱动二相流入管减摩组件，大幅降低轮盘摩擦损耗。 Contains internal reduction friction closed average speed high potential ratio impeller, with L-shaped blades, reverse tangential exit, tail reduction acceleration reduction section of closed friction constant speed impeller, average speed bifurcation and other deceleration designs. 25 High potential specific impeller direction is as high as 3 ~ 9, its guide speed is low, and its flow loss is small; it has air-gap clearance, front and rear center pressure booster module end cavity communication pressure equalization holes, and anti-friction drive two-phase inflow pipe anti-friction component, Significantly reduce wheel friction loss.

包含预旋内减摩闭式均速高势比叶轮，具有 L形叶片、反切向减摩预旋闭式出口、叶槽尾部加速段、均速岔道等减速设计，其输出液流势均速高势比叶 Contains pre-spinning internal friction-reducing closed average speed high potential ratio impeller, with L-shaped blades, anti-tangential anti-friction pre-spinning closed outlet, blade groove tail acceleration section, average speed bifurcation and other deceleration designs, and its output liquid flow potential is even. High potential ratio leaf

图 26 动比可高达 3〜9，其入导速度低，导流损耗小；具有前腔阻气轮向心增压模间隙、前后端腔连通均压孔、减摩驱动二相流入管减摩组件，块充气运行大幅度降低轮盘摩擦损耗；包含预旋器，轴向来流等速预旋，叶轮入口具有工况变化适应性，提高效率并避免气蚀。包含超减摩预旋闭式均速高势比叶轮，具有 L形叶片、反切向出口、叶槽尾部加速段、均速岔道等减速设计，其输出液流势超减摩预旋闭 Figure 26 The dynamic ratio can be as high as 3 ~ 9, which has a low conduction speed and small diversion loss; it has a centripetal booster mold clearance for the front cavity choke wheel, a pressure equalization hole for the front and rear cavity communication, and a two-phase inflow reduction tube for antifriction drive. Friction components, block inflation operation greatly reduce the friction loss of the disc; Contains pre-spinner, axial inflow constant-speed pre-spinning, impeller inlet has adaptability to working conditions, improves efficiency and avoids cavitation. Contains super-reduction anti-friction pre-spinning average speed high potential ratio impeller, with L-shaped blades, counter-tangential exit, tail section acceleration section, average speed bifurcation and other deceleration designs. Its output fluid potential is super-striking pre-spin closure

动比可高达 3〜9，其入导速度低，导流损耗小；具有前腔阻气式均速髙势比 The dynamic ratio can be as high as 3 ~ 9, and its conduction velocity is low, and the conduction loss is small.

图 27 间隙和前后端腔减摩驱动二相流入管，其叶轮盖延伸包裹转移叶轮向心增压 Figure 27 The gap and the front and rear chambers reduce friction and drive the two-phase inflow pipe. The impeller cover is extended and wrapped to transfer the impeller.

段流道截面的叶轮腔部分，充气运行大幅度降低轮盘摩擦损耗模块 The impeller cavity part of the section of the flow channel section, the aeration operation greatly reduces the friction loss of the disc. Module

和转移汇流流道摩擦损耗；包含预旋器，轴向来流等速预旋，叶轮入口具有工况变化适应性，提高效率并避免气蚀。参照图 19， '图中给出了依据模块化方法轴向组合传统半开式叶轮与向心导轮的向心增压模块。其中， 151是叶轮流道入口， 152是叶轮腔盖， 153是装配止口， 154是叶轮， 155 是转移段流道截面的叶轮腔部分， 156是转移段流道截面的导轮部分， 157 是带外壳的向心导轮， 158是导轮增压流道， 159是导轮出口圆柱面， 160是在模块中约束叶轮的转轴。 Friction loss of transfer manifold; Contains pre-spinner, axial inflow constant-speed pre-spin, impeller inlet has adaptability to working conditions, improves efficiency and avoids cavitation. Referring to Fig. 19, the figure shows a centripetal booster module that axially combines a traditional semi-open impeller and a centrifugal guide wheel according to a modular method. Among them, 151 is the inlet of the impeller flow path, 152 is the impeller cavity cover, 153 is the assembly stop, 154 is the impeller, 155 is the impeller cavity portion of the transfer channel cross section, 156 is the guide wheel portion of the transfer channel cross section, 157 It is a centripetal guide wheel with a shell, 158 is a supercharged flow path of the guide wheel, 159 is a cylindrical surface of the guide wheel exit, and 160 is a rotating shaft that constrains the impeller in the module.

本例中，半幵式叶轮向心增压模块由向心导轮 157、半开式叶轮 154和叶轮腔盖板 152 轴向组合而成。其中，导轮 157和叶轮腔盖 152上的旋转曲面、两者外沿转移段流道配合曲面都是配合半开式叶轮 154的参数专门设计的，包括依据叶轮形状尺寸和配合间隙确定旋转曲面的母线坐标和依据流体参数确定转移段流道的壁面坐标。 In this example, the centrifugal booster module of the half-blade type impeller is axially combined with a centrifugal guide wheel 157, a semi-open impeller 154, and an impeller cavity cover plate 152. Among them, the rotating curved surface on the guide wheel 157 and the impeller cavity cover 152, and the matching surface of the flow path of the outer edge transfer section of the two are specially designed according to the parameters of the semi-open impeller 154, including determining the rotating curved surface according to the shape and size of the impeller and the fit clearance. The coordinates of the generatrices and the wall coordinates of the flow channel of the transfer section are determined according to the fluid parameters.

本半开式叶轮向心增压模块输出常势比液流，适合于组装叶轮速度为 10米 /秒左右的离心泵，当流道当量直径加大时速度可以提高。由于转移段流道约束度高于传统导流器，其叶轮出口回流的现象将有所遏制。其应用优势主要在于模块化所带来的工艺效益和组合所能带来的功能和性能效益。参照图 20，图中给出了模块化组合经典闭式叶轮与向心导轮的向心增压模块。其中， 161是叶轮流道入口， 162是叶轮腔盖， 163是装配止口， 164是传统技术闭式叶轮， 165 是转移段流道截面的叶轮腔部分， 166是转移段流道截面的导轮部分， 167 是带外壳的向心导轮， 168是导轮增压流道， 169是导轮流道出口圆柱面， 170是约束叶轮的转轴。 The semi-open impeller centripetal booster module outputs a constant potential specific flow, which is suitable for assembling a centrifugal pump with an impeller speed of about 10 meters per second. The speed can be increased when the equivalent diameter of the flow channel is increased. Because the flow channel is more constrained than the traditional deflector in the transfer section, The phenomenon of backflow of the impeller outlet will be curbed to some extent. Its application advantages mainly lie in the technological benefits brought by the modularity and the functional and performance benefits brought by the combination. Referring to FIG. 20, a centripetal booster module combining a classic closed impeller and a centrifugal guide wheel is shown. Among them, 161 is the inlet of the impeller flow path, 162 is the impeller cavity cover, 163 is the assembly stop, 164 is the traditional closed-type impeller, 165 is the impeller cavity part of the flow channel section of the transfer section, and 166 is the guide of the flow channel section of the transfer section. For the wheel part, 167 is a centripetal guide wheel with a shell, 168 is a guide wheel booster runner, 169 is a cylindrical surface of the guide runner exit, and 170 is a constraining shaft of the impeller.

本例中，闭式叶轮向心增压模块由向心导轮 167、闭式叶轮 164和叶轮腔盖板 162轴向组合而成。其中，导轮 167和叶轮腔盖 162上的旋转曲面、两者外沿转移段流道配合曲面都是配合闭式叶轮 164的参数专门设计的，包括依据闭式叶轮形状尺寸和配合间隙确定旋转曲面的母线坐标和依据流体参数确定转移段流道的壁面坐标，也包括从叶轮腔盖 162 上挖去叶轮盖所占据的空间，以使叶槽流道与出口流道吻接。本模块的装配要求、运行原理、适应性和应用效果与图 19所示实施例基本相同，所不同的是闭式叶轮所具有的性能差别。参照图 21，图中给出了模块化组合经典闭式叶轮与向心导轮并与内减摩技术进一步组合的向心增压模块。其中， 171 是安装于叶轮腔盖板上的 V形槽阻气间隙环形盖板， 172 是安装于叶轮盖板上与之一道旋转的 V形槽小动环， 173是 V形槽阻气间隙之二相流入口， 174是穿过外壳和叶轮腔盖板进入入口 173的充气驱动二相流入管， 175是叶轮腔盖板， 176 是充气的叶轮前端腔， 177 是叶轮上布设在穿过叶片的前盖固定铆钉中的前后端腔连通均压孔， 178是充气的后端腔， 179是带外壳导轮， 180是闭式叶轮。 In this example, the closed-type impeller centripetal booster module is formed by axially combining a centrifugal guide wheel 167, a closed impeller 164, and an impeller cavity cover plate 162. Among them, the rotating curved surface on the guide wheel 167 and the impeller cavity cover 162, and the mating curved surface of the flow path of the outer edge transfer section of the two are specially designed according to the parameters of the closed impeller 164, including determining the rotation according to the shape and size of the closed impeller and the fit clearance. The generatrical coordinates of the curved surface and the wall coordinates of the flow passage of the transfer section are determined according to the fluid parameters, and the space occupied by the impeller cover is excavated from the impeller cavity cover 162 to make the impeller flow passage and the outlet flow passage match. The assembly requirements, operating principles, adaptability, and application effects of this module are basically the same as the embodiment shown in Figure 19, except that the closed impeller has different performance. Referring to Fig. 21, a centripetal booster module combining a classic closed impeller with a centrifugal guide wheel and a further combination of internal friction reduction technology is shown. Among them, 171 is a V-shaped groove air-gap annular cover plate mounted on the impeller cavity cover plate, 172 is a small V-groove air-gap ring installed on the impeller cover plate and rotated one by one, and 173 is a V-shaped groove air gap clearance For the two-phase flow inlet, 174 is an inflatable drive two-phase inflow pipe that passes through the casing and the impeller cavity cover plate and enters the inlet 173, 175 is the impeller cavity cover plate, 176 is the front end cavity of the inflatable impeller, and 177 is arranged on the impeller to pass through The front and rear cavities in the blade's front cover fixing rivet communicate with pressure equalizing holes, 178 is an aerated rear cavity, 179 is a guide wheel with a casing, and 180 is a closed impeller.

本例中，减摩闭式叶轮向心增压模块由向心导轮 179、闭式叶轮 180和叶轮腔盖板 175 及 V形槽阻气间隙环形盖板 171、. V形槽动环 172、充气驱动二相流入管 174、前盖固定铆钉中的前后端腔均压孔 177等内减摩零件或结构组合而成。其中，导轮 179和叶轮腔盖 175 上的旋转曲面、两者外沿转移段流道配合曲面都是配合闭式叶轮 180的参数专门设计的，包括从叶轮腔盖 175上去叶轮盖所占据的空间，以使叶槽流道与出口流道吻接。由叶轮腔盖板 175上的环槽、环形盖板 171和旋转动环 172构成的 V形槽阻气间隙可保持内减摩状态。均压孔 177使后端腔与前端腔连通和等压充盈气体减摩，不需另外接管。入管 174 连接射流器等二相流驱动压力源后，可驱动双端腔内减摩。本模块的装配要求、运行原理和适应性等与图 20所示实施例基本相同，组合内减摩技术将使闭式叶轮的轮盘摩擦损耗减少 82%〜95 %，泵效率将因此而提髙 5〜9%。参照图 22，图中给出了模块化组合半开式均速高势比叶轮与向心导轮的向心增压模块。其中， 181是叶轮流道入口， 182是叶轮腔盖， 183是半开式均速高势比,叶轮， 184是叶轮流道的出口转向加速段， 185是 L形叶片尾部， 186是转移段流道截面的导轮部分， 187是转移段流道截面的导轮部分， 188是带外壳的向心导轮， 189是导轮增压流道， 190 是导轮流道出口圆柱面。 In this example, the anti-friction closed impeller centripetal booster module consists of a centrifugal guide wheel 179, a closed impeller 180 and an impeller cavity cover plate 175, and a V-shaped groove air gap annular cover plate 171, a V-shaped groove moving ring 172 2. Inflatable driving two-phase inflow pipe 174, front and rear cavity equalizing pressure holes 177 in the front cover fixing rivet, and other internal friction reducing parts or structures are combined. Among them, the rotating curved surface on the guide wheel 179 and the impeller cavity cover 175, and the mating surface of the flow path of the outer edge transfer section of the two are specially designed according to the parameters of the closed impeller 180, including the impeller cover taken from the impeller cavity cover 175. Space so that the chute runners and the exit runners are in contact with each other. The V-shaped air-blocking gap formed by the ring groove on the impeller cavity cover plate 175, the ring cover plate 171, and the rotating movable ring 172 can maintain the internal friction reduction state. The pressure equalization hole 177 communicates the back-end cavity with the front-end cavity and reduces the friction of the isobaric filling gas without the need for additional takeover. The inlet pipe 174 is connected to a two-phase flow driving pressure source such as a jet, and can drive friction reduction in the double-end cavity. The assembly requirements, operating principles, and adaptability of this module are basically the same as the embodiment shown in Figure 20. The combined internal friction reduction technology will reduce the disc friction loss of the closed impeller by 82% to 95%, and the pump efficiency will be improved accordingly.髙 5 ~ 9%. Referring to FIG. 22, a centripetal booster module of a modular combination of a half-open type average speed high potential ratio impeller and a centrifugal guide wheel is shown. Among them, 181 is the inlet of the impeller flow path, 182 is the impeller cavity cover, 183 is the half-open average speed high potential ratio, and the impeller is 184. The exit of the impeller flow channel turns to the acceleration section, 185 is the tail of the L-shaped blade, 186 is the guide wheel section of the flow section of the transfer section, 187 is the guide wheel section of the flow section of the transfer section, 188 is a centripetal guide wheel with a housing, 189 is the supercharged runner of the guide wheel, and 190 is the cylindrical surface of the exit of the guide wheel.

本例中，半开式均速高势比叶轮向心增压模块由向心导轮 188、半开式均速高势比叶轮 183和叶轮腔盖板 182轴向组合而成。其中，导轮 188和叶轮腔盖 182上的旋转曲面、两者外沿转移段流道配合曲面都是配合半开式均速高势比叶轮 183的参数专门设计的。工作时，相对涡旋被均速岔道阻遏，液流低速层流化，并在加速段 184中加速，出口流速等量减小。 In this example, the semi-open type average speed high potential ratio impeller centrifugal booster module is formed by axially combining the centripetal guide wheel 188, the semi-open type average speed high potential ratio impeller 183 and the impeller cavity cover plate 182. Among them, the rotating curved surface on the guide wheel 188 and the impeller cavity cover 182, and the mating surface of the flow path of the outer edge transfer section of the two are specially designed to match the parameters of the half-open average speed high potential ratio impeller 183. During operation, the relative vortex is blocked by the uniform speed bifurcation, the liquid flow is laminarized at a low speed, and it accelerates in the acceleration section 184, and the outlet velocity decreases by the same amount.

本模块的装配要求与图 19所示实施例基本相同。由于半开式均速高势比叶轮所具有的优势，叶轮输出势动比将可以达到 3〜9，其中向心导轮的入导速比将大幅度减小。因此，叶轮工作线速度可以提高到 20米 /秒以上，当流道当量直径较大时速度可以选得更髙。均速髙势比叶轮的优势，以及模块化设计所带来的工艺效益和组合所能带来的功能和性能效益，将在本实例中综合地体现出来。参照图 23，图中给出了模块化组合闭式均速高势比叶轮与向心导轮的向心增压模块。其中， 191是均速高势比闭式叶轮， 192是叶轮腔盖， 193是叶轮盖， 194是叶轮盖固定铆钉， 195是叶轮流道尾部加速段， 196是转移段流道截面的叶轮腔部分， 197是转移段流道截面的导轮部分， 198是带外壳的向心导轮， 199是导轮增压流道， 200是导轮流道出口圆柱面。 The assembly requirements of this module are basically the same as the embodiment shown in FIG. Due to the advantages of the semi-open type average speed high potential ratio impeller, the impeller output potential ratio can reach 3 ~ 9, among which the input speed ratio of the centrifugal guide wheel will be greatly reduced. Therefore, the working linear speed of the impeller can be increased to more than 20 meters per second, and the speed can be selected even more when the equivalent diameter of the runner is large. The advantages of the equalizing momentum over the impeller, as well as the technological benefits brought by the modular design and the functional and performance benefits brought by the combination, will be comprehensively reflected in this example. Referring to Fig. 23, a centrifugal booster module of a modular combination closed-type high-speed average potential impeller and a centrifugal guide wheel is shown. Among them, 191 is a closed-type impeller with a uniform velocity and a high potential ratio, 192 is an impeller cavity cover, 193 is an impeller cover, 194 is an impeller cover fixing rivet, 195 is an impeller flow channel tail acceleration section, and 196 is an impeller cavity of a flow section of a transfer section. Part 197 is the guide wheel section of the runner section of the transfer section, 198 is the centripetal guide wheel with the housing, 199 is the guide wheel booster runner, and 200 is the cylindrical surface of the runner exit.

本例中，闭式均速高势比叶轮向心增压模块由向心导轮 198、半开式均速高势比叶轮 In this example, the closed-type constant-velocity high-potential-ratio impeller centripetal booster module consists of a centripetal guide wheel 198 and a semi-open type uniform-velocity high-potential-ratio impeller.

193和叶轮腔盖板 192轴向组合而成。其中，导轮 188和叶轮腔盖 182上的旋转曲面、两者外沿转移段流道配合曲面都是配合闭式均速高势比叶轮 193的参数专门设计的，包括从叶轮腔盖 192上挖去叶轮盖所占据的空间，以使叶橹流道与出口流道吻接。工作时，相对涡旋被均速岔道阻遏，液流低速层流化，并在加速段 195中加速，出口流速等量减小。 193 and the impeller cavity cover 192 are axially combined. Among them, the rotating curved surface on the guide wheel 188 and the impeller cavity cover 182, and the mating surface of the flow path of the outer edge transfer section of the two are specially designed to meet the parameters of the closed-type average high-potential ratio impeller 193, including from the impeller cavity cover 192. Dig out the space occupied by the impeller cover, so that the ridge flow channel and the outlet flow channel are in contact with each other. During operation, the relative vortex is blocked by the uniform speed bifurcation, the liquid flow is laminarized at a low speed, and it accelerates in the acceleration section 195, and the outlet velocity decreases by the same amount.

本模块的装配要求与图 20所示实施例基本相同。闭式均速高势比叶轮的输出势动比大约可以达到 3〜9，叶轮工作速度在 20米 /秒以上，向心导轮的入导速比将大幅度减小。本模块的叶轮程效率高于半开式叶轮模块，其均速高势比优势、模块化设计带来的工艺效益和组合带来的功能和性能效益将体现得更好。本模块也是进一步组合其他创新技术的设计基础。参照图 24，图中给出了模块化组合闭式均速高势比叶轮、轴向来流预旋器和向心导轮的向心增压模块。其中， 201是轴向来流预旋器， 202是叶轮腔盖， 203是叶轮盖， 204是闭式均速高势比叶轮， 205 是叶轮流道尾部加速段， 206 是转移段流道截面叶轮腔部分， 207是转移段流道截面导轮部分， 208是带外壳的向心导轮， 209是导轮增压流道， 210是导轮出口。 The assembly requirements of this module are basically the same as the embodiment shown in FIG. 20. The closed-velocity average high-potential ratio impeller's output potential-to-momentum ratio can reach about 3-9, and the impeller's working speed is more than 20 meters per second, and the input guide ratio of the centripetal guide wheel will be greatly reduced. The impeller range efficiency of this module is higher than that of the semi-open impeller module. Its advantages of average speed and high potential ratio, the technological benefits brought by the modular design, and the functional and performance benefits brought by the combination will be better reflected. This module is also the design basis for further combining other innovative technologies. Referring to FIG. 24, a centrifugal supercharging module of a modular combination closed-type average speed high-potential ratio impeller, an axial flow pre-rotator, and a centrifugal guide wheel is shown. Among them, 201 is the axial inflow pre-rotator, 202 is the impeller cavity cover, 203 is the impeller cover, 204 is the closed-type average speed high potential ratio impeller, 205 is the tail acceleration section of the impeller flow channel, and 206 is the flow section of the transfer section. In the impeller cavity part, 207 is the section of the runner section of the transfer channel, 208 is a centripetal guide wheel with a casing, 209 is a guide wheel booster runner, and 210 is Guide wheel exit.

本例中，预旋闭式均速高势比叶轮向心增压模块由向心导轮 208、均速高势比闭式叶轮 204、预旋器 201和叶轮腔盖板 202组合而成。其中，导轮 188和叶轮腔盖 182上的旋转曲面、两者外沿转移段流道配合曲面都是配合闭式均速高势比叶轮 193的参数专门设计的，包括从叶轮腔盖 192上挖去叶轮盖所占据的空间，以使叶槽流道与出口流道吻接。工作时，相对涡旋被均速岔道阻遏，液流低速层流化，并在加速段中加速，出口流速等量减小。预旋器 201使轴向来^ ί产生等速预旋，使叶轮入口流场具有工况变化自适应性，避免湍流和气蚀。 In this example, the pre-spinning closed-type constant-velocity high-potential-ratio impeller centripetal booster module is composed of a centripetal guide wheel 208, a uniform-velocity high-potential-ratio closed-type impeller 204, a prerotator 201, and an impeller cavity cover plate 202. Among them, the rotating curved surface on the guide wheel 188 and the impeller cavity cover 182, and the mating surface of the flow path of the outer edge transfer section of the two are specially designed to meet the parameters of the closed-type average high-potential ratio impeller 193, including from the impeller cavity cover 192. Cut out the space occupied by the impeller cover, so that the flow path of the blade groove is in contact with the outlet flow path. During operation, the relative vortex is blocked by the uniform speed bifurcation, the liquid flow is laminarized at a low speed, and it accelerates in the acceleration section, and the outlet velocity decreases by an equal amount. The pre-spinner 201 generates an axially constant pre-spin, so that the flow field at the inlet of the impeller is adaptive to changes in working conditions, and turbulence and cavitation are avoided.

本模块的装配要求与图 20所示实例相同。工作时，叶轮输出势动比可达 3〜9，叶轮速度在 20米 /秒以上。本模块的效率高于前述所有实例。模块化设计的工艺效益、与其他模块的组合效益，将使本实例模块的组合结构成为离心泵设计中的热选组件之一。参照图 25，；图中给出了模块化组合均速髙势比闭式叶轮、内减摩组件和向心导轮的向心增压模块。其中， 211是安装于叶轮腔盖板上的 V形槽阻气间隙环形盖板， 212是安装于叶轮盖板上与之一道旋转的 V形槽小动环， 213是 V形槽阻气间隙之二相流入口， 214 是穿过外壳和叶轮腔盖板进入入口 213 的充气驱动二相流入管， 215 是叶轮腔盖板， 216 是充气的叶轮前端腔， 217是叶轮上布设在穿过叶片的前盖固定铆钉中的前后端腔连通均压孔， 218是充气的后端腔， 219是带外壳导轮， 220是闭式叶轮。 The assembly requirements for this module are the same as the example shown in Figure 20. During operation, the impeller output momentum ratio can reach 3 ~ 9, and the impeller speed is above 20 meters / second. This module is more efficient than all the previous examples. The technological benefits of the modular design and the combined benefits with other modules will make the combined structure of the modules in this example one of the hot selection components in the design of a centrifugal pump. Referring to Figure 25, the figure shows a modular combined centrifugal pressure equalizing ratio closed impeller, internal friction reduction assembly and a centrifugal booster module of the centrifugal guide wheel. Among them, 211 is a V-shaped groove air blocking gap cover plate installed on the impeller cavity cover plate, 212 is a V-shaped groove small moving ring installed on the impeller cover plate and rotated one by one, and 213 is a V-shaped groove air blocking gap For the two-phase flow inlet, 214 is an inflatable drive two-phase inflow pipe that passes through the casing and the impeller cavity cover plate and enters the inlet 213, 215 is the impeller cavity cover plate, 216 is the front end cavity of the inflatable impeller, and 217 is arranged on the impeller to pass through The front and rear cavities in the front cover fixing rivets of the blades communicate with the pressure equalization holes, 218 is an aerated rear cavity, 219 is a casing guide wheel, and 220 is a closed impeller.

本例中，减摩闭式均速高势比叶轮向心增压模块由向心导轮 219、闭式均速高势比叶轮 220、叶轮腔盖板 215及 V形槽阻气间隙环形盖板 211、 V形槽动环 212、二相流入管 214、前盖铆钉中的前后端腔均压孔 217等内减摩零件或结构组合而成。其中，导轮 219 和叶轮腔盖 215上的旋转曲面、两者外沿转移段流道配合曲面都是配合闭式均速高势比叶轮 220的参数专门设计的，叶轮腔盖 215上挖去了叶轮盖所占据的空间，以使叶槽流道与出口流道吻接。工作时，相对涡旋被均速岔道阻遏，液流低速层流化，并在加速段中加速，出口流速等量减小，由叶轮腔盖板 215上的环槽、环形盖板 211和旋转动环 212构成的 V 形槽阻气间隙可保持内减摩状态。均压孔 217使后端腔与前端腔连通和等压充盈气体减摩，不需另外接管。入管 214连接射流器等二相流驱动压力源后，可驱动双端腔减摩。 In this example, the friction-reducing closed-type constant-velocity high-potential-ratio impeller centripetal booster module is composed of a centripetal guide wheel 219, a closed-type high-velocity-ratio impeller 220, an impeller cavity cover plate 215, and a V-shaped groove air gap gap annular cover. Plates 211, V-shaped groove moving ring 212, two-phase inflow pipe 214, front and rear cavity pressure equalization holes 217 in the front cover rivet, and other internal friction reducing parts or structures are combined. Among them, the rotating curved surface on the guide wheel 219 and the impeller cavity cover 215, and the flow path matching surface of the outer edge transfer section of the impeller cavity cover 215 are specially designed according to the parameters of the closed-type average velocity high-potential ratio impeller 220, and the impeller cavity cover 215 is dug out. The space occupied by the impeller cover is made to make the blade groove flow path and the outlet flow path match. During operation, the relative vortex is blocked by the uniform speed bifurcation, the liquid flow is laminarized at a low speed, and is accelerated in the acceleration section, and the outlet flow velocity is reduced by an equal amount. The ring groove on the impeller cavity cover plate 215, the ring cover plate 211, and the rotation The V-groove air-blocking gap formed by the moving ring 212 can maintain the internal friction reduction state. The pressure equalization hole 217 allows the rear cavity to communicate with the front cavity and reduce the friction of the isobaric filling gas without the need for additional takeover. The inlet tube 214 is connected to a two-phase flow driving pressure source such as a jet, and can drive the double-ended cavity to reduce friction.

本模块的装配要求与图 21所示实例相同。工作时，叶轮输出势动比可达 3〜9，叶轮速度在 20米 /秒以上。组合内减摩技术将使闭式叶轮的轮盘摩擦损耗减少 82%〜95%，泵效率将因此而提高 5〜9%。本模块的效率高于前述所有实例。模块化设计的工艺效益、与其他模块的组合效益，将使本实例模块的组合结构成为离心泵设计中的热选组件之一。参照图 26，图中给出了模块化组合均速高势比闭式叶轮、内减摩组件、预旋器和向心导轮的向心增压模块。其中， 221 是轴向来流预旋器， 222 是安装于叶轮盖板上与之一道旋转的 V形槽小动环等阻气间隙结构， 223是穿过外壳和叶轮腔盖板进入的充气驱动二相流入管， 224是叶轮盖板， 225是叶轮腔盖板， 226是充气的叶轮前端腔， 227是布设在前盖固定铆钉中的叶轮前后端腔均压孔， 228 是带外壳的向心导轮， 229 是充气的后端腔， 230是均速高势比闭式叶轮。 The assembly requirements for this module are the same as the example shown in Figure 21. During operation, the impeller output momentum ratio can reach 3 ~ 9, and the impeller speed is above 20 meters / second. The combined internal friction reduction technology will reduce the disc friction loss of the closed impeller by 82% to 95%, and the pump efficiency will be improved by 5 to 9%. This module is more efficient than all the previous examples. The technological benefits of the modular design and the combined benefits with other modules will make the combined structure of the modules of this example one of the hot selection components in the design of a centrifugal pump. Referring to FIG. 26, a centrifugal supercharging module of a modular combined average speed high potential ratio closed impeller, an internal friction reduction assembly, a pre-rotator, and a centrifugal guide wheel is shown. Among them, 221 is an axial flow pre-rotator, and 222 is installed on the cover of the impeller. Rotating V-shaped groove small moving ring and other air-blocking gap structures, 223 is an inflatable drive two-phase inflow pipe that enters through the casing and the impeller cavity cover, 224 is an impeller cover, 225 is an impeller cavity cover, and 226 is inflatable Impeller front cavity, 227 is the pressure equalizing hole in the front and rear cavity of the impeller, which is arranged in the fixed rivet of the front cover, 228 is a centripetal guide wheel with a casing, 229 is an inflatable rear cavity, and 230 is an average speed high potential ratio closed impeller .

本例中，预旋减摩闭式均速高势比叶轮向心增压模块由向心导轮 228、闭式均速高势比叶轮 230、叶轮腔盖板 225及轴向来流预旋器 221和 V形槽动环阻气结构 222、二相流入管 223等组件组成。其中，导轮 228和叶轮腔盖 225上的旋转曲面、两者外沿转移段流道配合曲面都是配合闭式均速高势比叶轮 230的参数专门设计的。工作时，叶槽中无相对涡旋，液流将在流道加速段中加速，从而等量减小出口流速。轮圈套在叶轮轴套上和刚性肋条固定在叶轮盖板上的预旋器 221用于对轴向来流加载预旋。叶轮腔盖板上的 V形槽阻气结构 222与前后端腔连通均压孔 227等构成内减摩组件，射流器等二相流驱动压力源后，可驱动双端腔内减摩。 In this example, the pre-spinning friction-reduction closed-type constant-velocity high-potential-ratio impeller centripetal booster module is pre-rotated by a centripetal guide wheel 228, a closed-type high-velocity-ratio impeller 230, an impeller cavity cover plate 225, and an axial flow. The device 221 is composed of a V-shaped groove moving ring gas blocking structure 222 and a two-phase inflow pipe 223. Among them, the rotating curved surface on the guide wheel 228 and the impeller cavity cover 225, and the matching surface of the flow path of the outer edge transfer section of the both are specially designed to meet the parameters of the closed-type average high-potential ratio impeller 230. During operation, there is no relative vortex in the blade groove, and the liquid flow will be accelerated in the acceleration section of the flow channel, thereby reducing the outlet flow rate by the same amount. The pre-spinner 221, which has a rim sleeve on the impeller sleeve and rigid ribs fixed on the impeller cover plate, is used for pre-rotation loading in the axial direction. The V-shaped groove gas blocking structure 222 on the impeller cavity cover plate communicates with the front and rear cavity pressure equalizing holes 227 to form an internal friction reducing component. After a two-phase flow driving pressure source such as a jet can drive the dual-end cavity friction reducing.

本模块的装配要求与图 21所示实例相同。工作时，闭式均速高势比叶轮 230通过流道尾部加速段增加相对流速，使出口流速等量减小，使导流效率大幅提高。组合预旋器 221 使轴向来流产生等速预旋，使叶轮入口速度场方向具有工况变化自适应性，使叶轮效率提高并能避免气蚀。组合内减摩技术将使泵效率提高 5〜9%。叶轮输出势动比可达 3〜9，叶轮速度上限可达 20米 /秒以上。本模块的效率高于前述所有实例。其模块化设计的工艺效益、与其他模块的组合效益，将使本实例模块的组合结构成为离心泵设计中的最热选的组件之一。参照图 27，图中给出了模块化组合均速高势比闭式叶轮、超减摩组件、预旋器和向心导轮的向心增压模块。其中， 231 是轴向来流预旋器， 232 是安装于叶轮盖板上与之一道旋转的 V形槽动环， 233是穿过外壳和叶轮腔盖板进入的充气驱动二相流入管， . 234是延伸并包含转移段流道叶轮腔截面部分的叶轮盖板， 235 是叶轮腔盖板， 236是均速高势比闭式叶轮， 237 是被叶轮盖板延伸后包覆减摩的转移段流道截面之叶轮腔部分， 238 是从导轮外壳进入的后端腔充气入管， 239是导轮增压流道， 240是带外壳的向心导轮。 The assembly requirements for this module are the same as the example shown in Figure 21. During operation, the closed average speed high-potential ratio impeller 230 increases the relative flow velocity through the acceleration section at the end of the flow channel, reduces the outlet flow velocity by an equal amount, and greatly improves the diversion efficiency. The combined pre-spinner 221 generates constant velocity pre-spinning in the axial incoming flow, makes the direction of the impeller inlet speed field adaptive to the change of working conditions, improves the impeller efficiency and avoids cavitation. Combined internal friction reduction technology will increase pump efficiency by 5-9%. The impeller output momentum ratio can reach 3 ~ 9, and the upper limit of the impeller speed can reach more than 20 meters per second. This module is more efficient than all the previous examples. The modular design of the process benefits, combined with other modules, will make the combined structure of the module of this example become one of the hottest components in the design of the centrifugal pump. Referring to Fig. 27, the figure shows a centrifugal supercharging module with a modular combination of an average speed and high potential ratio closed impeller, an anti-friction component, a pre-rotator and a centrifugal guide wheel. Among them, 231 is an axial incoming flow pre-rotator, 232 is a V-shaped groove moving ring installed on the impeller cover plate and rotating together, and 233 is an inflatable drive two-phase inflow pipe entering through the casing and the impeller cavity cover plate. 234 is the impeller cover that extends and contains the cross section of the impeller cavity section of the transfer channel, 235 is the impeller cavity cover, 236 is the uniform speed high potential ratio closed impeller, and 237 is covered by the impeller cover to reduce friction The impeller cavity part of the runner section of the transfer section, 238 is the rear-end cavity inflatable inlet pipe that enters from the outer shell of the guide wheel, 239 is the supercharged flow path of the guide wheel, and 240 is the centripetal guide wheel with the shell.

本例中，超减摩预旋闭式均速高势比叶轮向心增压模块由向心导轮 240、带延伸包覆转移段流道叶轮腔截面部分的叶轮盖板 234的闭式均速高势比叶轮 236、叶轮腔盖板 235 及轴向来流预旋器 231和超减摩组件 232、二相流入管 233等组件组成。其中，导轮 228 和叶轮腔盖 225上的旋转曲面、两者外沿转移段流道配合曲面都是配合闭式均速高势比叶轮 230的参数专门设计的。工作时，叶槽中无相对涡旋，液流将在流道加速段中加速，从而等量减小出口流速。预旋器 221用于对轴向来流加载预旋。安装于叶轮腔盖板上的 V形槽阻气间隙环形盖板、安装于叶轮盖板上与之一道旋转的动环 232及叶轮腔盖板入口处的环槽等组成 V形槽阻气间隙，作为超减摩重要组件支持延伸到转移段流道叶轮腔部分的前端腔充气不漏。 .后端腔以略低的压力单独充气，其入管 238穿越导轮外壳密封进入，可以充入流量被控制的纯气体，也可以将射流器等前端腔充气驱动二相流压力源经调节阀节流后分流接入，其压降是自适应的。导轮轴套可能连接静密封，也可能连接正压液封，因而无漏气之虞。 In this example, the super-anti-friction pre-spinning closed-velocity high-potential ratio impeller centripetal booster module consists of a centrifugal guide wheel 240 and an impeller cover plate 234 with a section of the impeller cavity section that extends and covers the transfer section. The high-speed potential ratio impeller 236, the impeller cavity cover plate 235, the axial inflow pre-rotator 231, the super friction reducing component 232, and the two-phase inflow pipe 233 are components. Among them, the rotating curved surface on the guide wheel 228 and the impeller cavity cover 225, and the matching curved surface of the flow channel of the outer edge transfer section of the impeller 230 are specially designed according to the parameters of the closed-type average high-potential ratio impeller 230. During operation, there is no relative vortex in the blade groove, and the liquid flow will be accelerated in the acceleration section of the flow channel, thereby reducing the outlet flow rate by the same amount. The pre-spinner 221 is used to apply a pre-spin to the axial inflow. The V-shaped groove air-blocking gap cover plate installed on the impeller cavity cover plate, the moving ring 232 installed on the impeller cover plate and rotating with one side, and the ring groove at the entrance of the impeller cavity cover plate constitute a V-shaped groove air-blocking gap. As an important component of super friction reduction, it extends to the front of the impeller cavity part of the runner of the transfer section. End cavity is not leaking. The rear cavity is individually inflated at a slightly lower pressure. Its inlet tube 238 passes through the shell of the guide wheel and is sealed in. It can be filled with pure gas with controlled flow rate. It can also charge the two-phase flow pressure source of the front cavity such as the ejector through a regulating valve. After throttling, the shunt is connected, and the pressure drop is adaptive. The idler shaft sleeve may be connected to a static seal or a positive pressure liquid seal, so there is no risk of air leakage.

本模块的装配要求与图 21所示实例基本相同，装配中应注意保护略有扩大的叶轮盖。工作时，闭式均速高势比叶轮 236通过流道尾部加速段增加相对流速，使出口流速等量减小，使导流效率大幅提高。组合预旋器 231使轴向来流产生等速预旋，使叶轮入口速度场方向具有工况变化自适应性，使叶轮效率提高并能避免气蚀。 The assembly requirements of this module are basically the same as the example shown in Figure 21, and care should be taken to protect the slightly enlarged impeller cover during assembly. During operation, the closed-type average velocity high-potential ratio impeller 236 increases the relative flow velocity through the acceleration section at the tail of the flow channel, reduces the outlet flow velocity by an equal amount, and greatly improves the diversion efficiency. The combined pre-spinner 231 generates constant velocity pre-spinning in the axial incoming flow, makes the direction of the impeller inlet speed field adaptive to changes in working conditions, improves the impeller efficiency, and can avoid cavitation.

超减摩技术将轮盘摩擦损耗降低 82%〜95 %而使泵效率提高 5〜9%的效益完全同内减摩技术，与此同时，它还能使转移段流道的汇流高速摩擦区的损耗绝大部分消除掉。按勾速圆周运动计算，这部分损耗与入导绝对速度的平方成正比，'与导轮直径和导叶数决定的汇流流道长度成正比，与截面摩擦边际弧线的长度成正比。消除这部分边际摩擦实际上属于减小导流损失系数的收益，可以根据转移段流道的当量直径及其扩张率、流速及其变化和介质粘度等参数来估算，或者作精确的沿途损耗积分。这些计算均与具体的液流参数有关。 Ultra friction reduction technology reduces the disc friction loss by 82% ~ 95% and improves the pump efficiency by 5-9%. The benefits are exactly the same as the internal friction reduction technology. At the same time, it can also make the high-speed friction zone of the transfer section flow channel confluence. Most of the losses are eliminated. Calculated according to the circular motion of the hook speed, this part of the loss is proportional to the square of the absolute velocity of the inflow, 'is proportional to the length of the manifold and determined by the diameter of the guide wheel and the number of vanes, and is proportional to the length of the cross-section friction marginal arc. Eliminating this part of the marginal friction actually belongs to the benefit of reducing the diversion loss coefficient. It can be estimated according to the equivalent diameter of the flow channel in the transfer section and its expansion rate, the flow velocity and its change, and the viscosity of the medium, or it can be used to accurately calculate the loss along the way. . These calculations are related to specific flow parameters.

本例模块中的均速高势比叶轮输出势动比可达 3〜9，叶轮速度可选在 20米 /秒以上。本模块的效率高于前述所有模块，属于性能最优良的实例。其节能效益，加上模块化设计的工艺效益，以及与其他模块组合所可能产生的效益，将可能使本实例模块的组合结构成为离心泵设计中的最热选的组件。图 28〜图 36是依据模块化方法组合向心增压模块和对称端盖模块构成向心增压单级离心泵的实例。下文首先从总体上说明向心增压单级离心泵的共同特征和优势特性，然后对每一种泵的个性特征和效果列成表格予以说明。 In this example, the impeller's output potential-to-momentum ratio can reach 3 ~ 9, and the impeller speed can be selected above 20 meters / second. The efficiency of this module is higher than all the previous modules, and it is the best example. Its energy-saving benefits, coupled with the modular design process benefits, and the benefits that can be generated by combining with other modules, will make the combined structure of the module of this example the hottest choice component in the centrifugal pump design. Figures 28 to 36 are examples of a centrifugal single-stage centrifugal pump constructed by combining a centripetal booster module and a symmetrical end cap module according to a modular approach. The following first describes the common features and advantages of centrifugal single-stage centrifugal pumps in general, and then describes the individual characteristics and effects of each pump in a table.

根据本发明模块化组合方法，向心增压单级离心泵包括 1个向心增压模块，为图 19〜图 27 所示实例模块中之一种，这些模块中的叶轮包含不同的技术或工艺，因而具有不同的特性。向心增压模块的外壳是向心导轮一体化结构的一部分，呈圆环柱形，有带定位止口和密封槽的配合面，或者还有向外突出的螺杆通孔鼻形结构。导轮结构的隔板前侧是叶轮腔，其形位适合于安装叶轮并留有恰当的间隙，其边沿有与叶轮腔盖外沿曲面合成转移段流道的曲面。 According to the modular combination method of the present invention, the centripetal booster single-stage centrifugal pump includes a centripetal booster module, which is one of the example modules shown in FIG. 19 to FIG. 27. The impellers in these modules include different technologies or Process and therefore have different characteristics. The housing of the centrifugal booster module is a part of the integrated structure of the centrifugal guide wheel, which is in the shape of a circular column and has a mating surface with a positioning stop and a sealing groove, or a screw through-hole nose structure protruding outward. The front side of the baffle of the guide wheel structure is the impeller cavity. Its shape and position are suitable for installing the impeller and leave a proper gap. The edge of the baffle has the curved surface of the runner of the transition section that is combined with the curved surface of the impeller cavity cover.

根据本发明的模块化组合方法，同一个父规格的模块装配尺寸和基本接口参数相同，具有查表检验互换性，同一个子规格具有完全互换性，两种可装配的模块具有规格对应性。其互换性覆盖设计过程、设计了以后的生产过程和生产了以后的使用过程。 According to the modular combination method of the present invention, the assembly dimensions and basic interface parameters of the module of the same parent specification are the same, and have the compatibility of checking the table to check the interchangeability. The same child specification has complete interchangeability, and the two assembleable modules have specification correspondence. . Its interchangeability covers the design process, the design of the later production process and the use of the later production process.

基于这些条件，本发明模块化组合单级离心泵的具体方案是：包含 2个变角度出管对称端盖模块和 1个向心增压模块，两种模块依据对应的子规格各具完全互换性，或者依据对应的父规格经查表检验介质、最高转速、最髙温度、最高耐压等参数互换性成立，按"液流从近轴环形口带环量流入和流出"连接模式将 3个模块轴向组合，即构成具有模块互换性的对称盖变角出管向心增压单级离心泵，组合是指设计中的连接配合、生产中的装配和使用中的修配，互换性覆盖这些过程。 Based on these conditions, the specific scheme of the modular combined single-stage centrifugal pump of the present invention is: It includes two variable-angle outlet pipe symmetrical end-cap modules and a centripetal booster module, and the two modules have complete interaction with each other according to corresponding sub-specifications. Transsexual, or basis Corresponding parent specifications are verified through a table to check the interchangeability of parameters such as medium, maximum speed, maximum temperature, and maximum pressure resistance. According to the "liquid flow from the paraxial annular mouth with the inflow and outflow" connection mode, the three module shafts are connected. Directional combination, that is, a symmetric cover variable angle outlet tube centrifugal single-stage centrifugal pump with modular interchangeability. Combination refers to connection and coordination in the design, assembly in production, and repair in use. The interchangeability covers these. process.

依据模块化组合方法，方案中的向心增压模块和对称端盖模块或者还是经过参数规划的，其中前者由向心导轮、闭式叶轮和叶轮腔盖轴向组合而成，后者是带中心蜗道和吻接管道的对称端盖单一零件， 2个对称端盖分别用作前端盖和后端盖。泵中还有轴系部件，包括转轴、轴承、键槽和键、有机材料软密封圈等，其中转轴是单级标准化零件。 According to the modular combination method, the centripetal booster module and the symmetric end cover module in the solution are also planned through parameters. The former is composed of a radial guide wheel, a closed impeller and an impeller cavity cover, and the latter is Single piece with symmetrical end cap with central worm and kiss tube, 2 symmetrical end caps are used as front end cap and rear end cap respectively. There are also shafting components in the pump, including the shaft, bearings, keyways and keys, soft seals made of organic materials, etc. The shaft is a single-stage standardized part.

在生产装配和使用修配时，向心增压模块是按照导轮、叶轮和叶轮腔盖板顺序装配的，三者分别通过外壳止口、转轴和导轮之叶轮腔定位，或者有其它附件时按其具***置伺机装配。拆卸程序则与装配过程相反。 During production, assembly, and repair, the centrifugal booster module is assembled in the order of the guide wheel, impeller, and impeller cavity cover plate. The three are positioned by the housing stop, the shaft, and the impeller cavity of the guide wheel, or when there are other accessories. Opportunistic assembly according to its specific position. The disassembly procedure is the reverse of the assembly process.

运行时，液流从入管匀速进入前端盖中心蜗道，受壁面约束转换为三维运动，流过 0〜 360度不等的角距离从近轴环形口分流，带环量轴向进入赋能模块中旋转的叶轮流道，从中接受叶片法向力功沿途加速并积分离心力功增加比能，然后经转移段流道进入导轮，在其中减速增压后，转 90度从近轴环形出口带环量流出，再汇流进入后盖中心蜗道，受壁面约束三维整理，流过 0〜360度不等的角距离从吻接出管流出。 During operation, the liquid flow enters the central volute of the front cover from the inlet pipe at a uniform speed, and is converted into a three-dimensional movement by the wall constraint. It flows through an angular distance ranging from 0 to 360 degrees and diverges from the paraxial annular mouth. The medium-rotating impeller flow channel receives the normal force work of the blade to accelerate along the way and integrates the centrifugal force work to increase the specific energy, then enters the guide wheel through the transfer section flow channel, decelerates and pressurizes it, and turns 90 degrees from the near-axis annular exit belt. The loop flows out, then converges into the central volute of the back cover, is constrained in three dimensions by the wall surface, and flows out of the kissing tube through an angular distance ranging from 0 to 360 degrees.

上述流程的优势是： 1、全程保守了环量，导流负荷轻，时间和空间变化率小，流场稳定性好，不恰当的 "折腾"少，损耗因而减小； 2、模块间保守环量与分流、汇流过程的结合使局部损耗减小，避免了现有技术中分流前的不当约束问题和分流中的欠约束问题，叶轮的入口特性较好； 3、赋能模块内部的汇流和分 ¾1过程是无局部激励的，这是本发明对转移段流道特别设计的结果。在所有向心增压离心泵中，除了无同步预旋者可能在叶轮入口处发生撞击损耗外，其余的种类都有较好的流程约束，具有大部分的变工况适应性。特别是，具有预旋均速髙势比机制者，全程都是完备约束的，具有最高的水力效率和完全的变工况适应性。而具有内减摩机制者，其内效率和总效率可以单独提高 5〜9%。 · The advantages of the above process are: 1. The circulation is conserved throughout the process, the diversion load is light, the time and space change rate is small, the flow field stability is good, the inappropriate "toss" is small, and the loss is reduced; 2. The module is conservative The combination of the loop quantity and the shunting and sinking process reduces the local loss, avoids the problem of improper constraints before shunting and the underconstraints in shunting in the prior art, and the inlet characteristics of the impeller are better; 3. Enabling the shunting inside the module The process of summation ¾1 is without local excitation, which is the result of the special design of the flow channel of the transfer section of the present invention. In all centrifugal booster centrifugal pumps, except for non-synchronous pre-spinners, which may cause impact losses at the impeller inlet, the remaining types have better process constraints and have most adaptability to variable working conditions. In particular, those who have a pre-spinning average velocity pseudo-potential ratio mechanism are fully constrained throughout, with the highest hydraulic efficiency and complete adaptability to changing conditions. For those with internal friction reduction mechanism, the internal efficiency and total efficiency can be increased by 5-9% alone. ·

' '

这种模块化组合的单级离心泵的共性特点和优势在于- The common features and advantages of this modular combination of single-stage centrifugal pumps are:

1、向心增压导流结构体积最小，成本最低，并且效率也较髙。 1. The centrifugal pressure-increasing diversion structure has the smallest volume, the lowest cost, and the relatively low efficiency.

2、向心增压模块具有液流从近轴环形口带环量轴向入出的模块连接规范性。 2. The centripetal booster module has the module connection standard for the fluid flow in and out from the paraxial annular mouth with the annular quantity.

3、对称端盖比之传统的外壳，其体积大为减小，因而成本较低，效率也较高。 3. Compared with the traditional shell, the symmetrical end cap has a greatly reduced volume, so the cost is lower and the efficiency is higher.

4、对称端盖作为轴向封装模块前后通用，单多级通用，其蜗道具有从近轴环形口带环量轴向分流入和汇流出的模块连接规范性，其出管具有变角度安装的适应性，与蜗道之吻接产生直线和回转运动双向高效转换功能。其连接功能完备，制造成本低，适应范围广。 4. Symmetrical end caps are common to the front and rear of the axially packaged module, and are used in single and multi-stage. Its wormway has the norms of module connection from the paraxial ring-shaped mouth with the amount of axial inflow and outflow, and its outlet pipe has variable angle installation. The adaptability, and the volute's kiss produces two-way efficient conversion function of linear and rotary motion. Its connection function is complete, the manufacturing cost is low, and the application range is wide.

5、在整体上，上述连接规范性、模块互换性、通用性体现或者潜在地蕴含了模块化组合方法带来的设计、制造和使用过程的技术经济利益，包括减少工作量、缩短工期、增加方便度、简化产品型系和材料配件规格、减少规范性技术壁垒、加快技术和物质流转、多因素降低成本，等等。 · 对称盖变角出管向心增压离心泵各不同技术实例特征不同，性能差异也很大。这些互有差异的个性特征及其功能性能特性，简要地列表说明如表 11。 5. On the whole, the above-mentioned connection specification, module interchangeability, and universality embody or potentially contain the technical and economic benefits of the design, manufacturing, and use process brought by the modular combination method, including reducing workload, shortening the construction period, Increase Increasing convenience, simplifying product lines and material accessories specifications, reducing regulatory technical barriers, speeding up technology and material transfers, reducing costs by multiple factors, and so on. · Symmetrical cover variable angle outlet pipe centrifugal booster centrifugal pumps have different characteristics and different performances. These different personality characteristics and their functional performance characteristics are briefly listed in Table 11.

表 11 对称盖变角出管向心增压单级泵的个性特征及其效果说明表标示特征的个性技术特征及其效果标示和说明 Table 11 Personality characteristics and effects of the variable-angle outlet tube centrifugal single-stage pump with symmetrical cover

图号 Drawing number

离心泵全名称 (将创新特征或传统特征包含在创新组合中，产生积极效果）对称盖变角出管包含 1个半开式叶轮向心增压模块和 2个对称端盖模块，叶轮图 28 半开式叶轮向心输出常势比液流入导。其特性是：导流程自适应变工况运行，增压单级离心泵导流效率提高，但低于高势比液流，叶轮程效率低于闭式叶轮。对称盖变角出管包含 1个闭式叶轮向心增压模块和 2个对称端盖模块，叶轮输图 29 闭式叶轮向心增出常势比液流入导。其特性是：导流程自适应变工况运行，导压单级离心泵流效率提高，但低于高势比液流。 Full name of the centrifugal pump (including innovative features or traditional features in the innovative combination, which has a positive effect) Symmetrical cover variable angle outlet pipe contains 1 semi-open impeller centripetal booster module and 2 symmetrical end cover modules, impeller Figure 28 The semi-open impeller has a constant potential output and is more conductive than a liquid inflow. Its characteristics are: self-adapting variable-flow operation of the guided flow, boosted single-stage centrifugal pump's efficiency is improved, but lower than the high potential ratio liquid flow, and the impeller stroke efficiency is lower than the closed impeller. Symmetric cover variable-angle outlet pipe Contains a closed impeller centripetal booster module and two symmetrical end cover modules. Impeller transmission Figure 29 The closed impeller increases the center-to-potential ratio of liquid inflow. Its characteristics are as follows: The guided flow is adaptively changed under different operating conditions, and the pressure efficiency of the single-stage centrifugal pump is improved, but lower than the high potential ratio liquid flow.

对称盖变角出管包含 1个内减摩闭式叶轮向心增压模块和 2个对称端盖模块，内减摩闭式叶轮设阻气间隙、前后端腔连通均压孔、减摩驱动二相流入管等结图 30 Symmetrical cover variable angle outlet tube includes 1 internal friction reducing closed impeller centripetal booster module and 2 symmetrical end cover modules. Internal friction reducing closed impeller is provided with air gap, front and rear cavity communication pressure equalization holes, antifriction drive Two-phase inflow pipe etc. Figure 30

向心增压单级离构，具有内减摩机制。其特性是：导流程自适应变工况运行，心泵导流效率提高，但低于高势比液流，内效率提高 5 %〜9%。 Concentric pressurized single-stage separation with internal friction reduction mechanism. Its characteristics are: the self-adaptive variable-flow operation of the guiding process, the cardiac pump's diversion efficiency is improved, but it is lower than the high potential ratio liquid flow, and the internal efficiency is increased by 5% ~ 9%.

包含 1个半开式均速高势比叶轮向心增压模块和 2个对称端盖对称盖变角出管 Contains 1 semi-open type constant speed high potential ratio impeller centrifugal booster module and 2 symmetrical end caps

模块，设 L形叶片、反切向出口、叶槽尾部加速段、均速岔道半开式均速高势 Module, with L-shaped blades, counter-tangential exit, tail section acceleration section, average speed bifurcation

图 31 等结构，具有遏制相对涡旋、叶轮输出减速、低速入导等机制。 Structures such as Figure 31 have mechanisms to curb relative vortexing, impeller output deceleration, and low-speed guidance.

比叶轮向心增压 Concentric pressurization than impeller

其特性是：导流程自适应变工况运行，压力系数提高，势动比单级离心泵 Its characteristics are: guided flow adaptively changing operating conditions, increased pressure coefficient, and potential-to-dynamic ratio single-stage centrifugal pump

达 3〜9，导流损耗降低一个数量级，叶轮程效率低于闭式叶轮。包含 1个均速高势比闭式叶轮向心增压模块和 2个对称端盖模对称盖变角出管 Up to 3 ~ 9, the flow loss is reduced by an order of magnitude, and the impeller stroke efficiency is lower than that of the closed impeller. Contains 1 closed-end impeller centripetal booster module and 2 symmetrical end cap molds

块，设 L形叶片、反切向出口、叶槽尾部加速段、均速岔道等闭式均速高势比 Block, with L-shaped blades, counter-tangential exits, accelerating section at the tail of blade groove, average speed bifurcation, etc.

图 32 结构，具有遏制相对涡旋、叶轮输出减速、低速入导等机制。 The structure in Figure 32 has the mechanism of restraining relative vortex, decelerating impeller output, and low-speed guide.

叶轮向心增压单 Impeller centripetal booster single

其特性是：导流程自适应变工况运行，压力系数提高，势动比级离心泵 Its characteristics are: guided flow adaptively changing operating conditions, increased pressure coefficient, potential-ratio centrifugal pump

达 3〜9，导流损耗降低一个量级，叶轮程效率高于半开式叶轮。包含 1个预旋闭式均速高势比叶轮向心增压模块和 2个对称端对称盖变角出管 Up to 3 ~ 9, the diversion loss is reduced by an order of magnitude, and the impeller stroke efficiency is higher than that of the semi-open impeller. Contains a pre-spinning closed-velocity high-potential ratio impeller centripetal booster module and 2 symmetrical ends, symmetrical cover, variable angle outlet tube

盖模块，设 L形叶片、反切向出口、叶槽尾部加速段、均速岔预旋闭式均速高 Cover module with L-shaped blades, counter-tangential exit, tail section acceleration section, average speed bifurcation

图 33 道等结构，具有遏制相对涡旋、叶轮输出减速、低速入导、同势比叶轮向心增 Figure 33.Structures such as channel, with curb relative vortex, deceleration of impeller output, low-speed induction, and increase of impeller to the center

步预旋等机制。其特性是：全程自适应变工况运行，压力系数压单级离心泵 Step pre-spin and other mechanisms. Its characteristics are: full-range adaptive variable operating conditions, pressure coefficient, single-stage centrifugal pump

提髙，势动比达 3〜9，导流损耗降低一个量级，抗气蚀特性好。包含 1个内减摩闭式均速高势比叶轮向心增压模块和 2个对称对称盖变角出詧端盖模块，设 L形叶片、均速岔道、反切向出口、叶槽尾部相内减摩闭式均速 As a result, the potential-to-motion ratio is 3 to 9, the flow loss is reduced by an order of magnitude, and the cavitation resistance is good. Contains an internal friction reducing closed-velocity average-velocity high-impedance centrifugal booster module and two symmetric symmetrical cover variable angle exit end cover modules, with L-shaped blades, uniform speed bifurcations, reverse tangential outlets, and the tail end phase Internal reduction friction closed average speed

对加速、阻气间隙、前后端腔连通均压孔、减摩驱动二相流入图 34 高势比叶轮向心管等结构，具有遏制相对涡旋、叶轮输出减速、低速入导等机增压单级离心泵 Acceleration, choke clearance, pressure equalization holes in the front and rear cavities, anti-friction drive two-phase inflow Figure 34 High potential ratio impeller centripetal tube and other structures, with relative vortex containment, impeller output deceleration, low-speed inlet guide, etc. Single-stage centrifugal pump

制。其特性是：导流程自适应变工况运行，压力系数提高，势动比高达 3〜9，导流损耗降低一个数量级，内机械损耗独立减小 82 %〜95 %。 system. Its characteristics are: the self-adaptation of the guided process is changed under different operating conditions, the pressure coefficient is increased, the potential ratio is as high as 3 ~ 9, the diversion loss is reduced by an order of magnitude, and the internal mechanical loss is reduced by 82% ~ 95% independently.

包含 1个内减摩预旋闭式均速高势比叶轮向心增压模块和 2个对称端盖模块，设 L形叶片、均速岔道、反切向出口、叶槽尾对称盖变角出管 Contains an internal friction reducing pre-closing average speed high potential ratio impeller centripetal booster module and two symmetrical end cover modules, with L-shaped blades, average speed bifurcations, anti-tangential exits, and symmetrical cover at the end of the blade groove. Tube

部相对加速、阻气间隙、前后端腔连通均压孔、减摩驱动二相内减摩预旋闭式 Partial relative acceleration, choke gap, front and rear cavity communication pressure equalization holes, anti-friction driving two-phase

图 35 流入管等结构，具有遏制相对涡旋、叶轮输出减速、低速入导、均速高势比叶轮 Figure 35 Structures such as inflow pipe, with relative vortex suppression, impeller output deceleration, low-speed inlet guidance, average speed high potential ratio impeller

向心增压单级离同步预旋、内减摩等机制。其特性是：全程自适应变工况运行，压力系数提高，抗气蚀特性好，势动比达 3〜9，导流损耗降低心泵 Concentric pressurized single-stage off-synchronous pre-spin, internal friction reduction and other mechanisms. Its characteristics are: full-time adaptive variable operating conditions, increased pressure coefficient, good anti-cavitation characteristics, a potential-to-motion ratio of 3 to 9, and reduced flow loss.

一个量级，内机械损耗独立减小 82%〜95 %。 One order of magnitude, the internal mechanical loss is independently reduced by 82% ~ 95%.

包含 1个预旋超减摩闭式均速高势比叶轮向心增压模块和 2个对称端盖模块，设 L形叶片、均速岔道、反切向出口、叶槽尾对称盖变角出管 Contains 1 pre-spin super-friction closed-type high-potential ratio impeller centripetal booster module and 2 symmetrical end cover modules, with L-shaped blades, average speed bifurcation, counter-tangential exit, and symmetrical cover at the end of the blade groove. Tube

部相对加速、阻气间隙、叶轮盖扩展、减摩驱动双二相流入管预旋超减摩闭式等结构，具有遏制相对涡旋、叶轮输出减速、低速入导、同步图 36 均速高势比叶轮 Relative acceleration, choke clearance, impeller cover expansion, anti-friction drive dual two-phase inflow pipe pre-spin super-friction closed type, etc., with relative vortex suppression, impeller output deceleration, low-speed guidance, synchronization Figure 36 High average speed Potential Impeller

预旋、内减摩、转移段流道减摩等机制。其特性是：全程自适向心增压单级离 Pre-rotation, internal friction reduction, and friction reduction of the flow channel in the transfer section. Its characteristics are:

应变工况运行，压力系数提高，抗气蚀特性好，势动比达 3〜9，心泵 Operating under strain conditions, the pressure coefficient is increased, the cavitation resistance is good, the potential-to-motion ratio is 3 to 9, the heart pump

导流损耗降低一个量级，内机械损耗独立减小 82%〜95 %，换向转移损耗进一步降低。参照图 28，图中给出了模块化组合半开式叶轮向心增压模块和对称端盖的离心泵结构。其中， 241是前端盖及其入管， 242是前端盖上的分流中心蜗道， 243是叶轮腔盖， 244 是叶轮流道， 245是半开式叶轮， 246是转移段流道截面的导轮部分， 247是带外壳的向心导轮， 248是导轮增压流道， 249是后盖上的汇流中心蜗道， 250是后盖及其出管。 The conduction loss is reduced by an order of magnitude, the internal mechanical loss is reduced by 82% ~ 95% independently, and the commutation transfer loss is further reduced. Referring to Fig. 28, a centrifugal pump structure with a modular combination of a semi-open impeller centrifugal booster module and a symmetrical end cover is shown. Among them, 241 is the front end cover and its inlet tube, 242 is the shunt center worm on the front end cover, 243 is the impeller cavity cover, 244 is the impeller flow channel, 245 is the semi-open impeller, and 246 is the guide wheel of the flow section of the transfer section In part, 247 is a centripetal guide wheel with a casing, 248 is a guide wheel booster flow path, 249 is a convergence center volute on the rear cover, and 250 is the rear cover and its outlet pipe.

本实例为对称盖变角出管半开式叶轮向心增压单级离心泵，包含 1个半开式叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由半开式叶轮 245、叶轮腔盖 243和向心导轮 247组成，后者分别用作前盖 241和后盖 250，通过轴系及紧固件轴向组合而成。 This example is a semi-open impeller centrifugal single-stage centrifugal pump with symmetrical cover and variable angle outlet pipe. It includes a semi-open impeller centrifugal booster module and two variable-angle outlet tube symmetrical end cover modules. The impeller 245, the impeller cavity cover 243, and the centrifugal guide wheel 247 are respectively used as the front cover 241 and the rear cover 250, and are axially combined by a shaft system and a fastener.

变角出管半幵式向心增压单级泵是一种新型离心泵，具有导流程变工况运行适应性等宝贵特性，适合于现有技术离心泵的简单改造，主要效益在于降低成本和方便用户安装，同时具有提高效率的潜力。其叶轮输出常势比液流，叶轮速度一般以 10米 /秒左右为宜，当流道当量直径加大时叶轮速度可以提髙。参照图 29，图中给出了模块化组合闭式叶轮向心增压模块和对称端盖的离心泵结构。其中， 251是前端盖及其入管， 252是前端盖上的分流中心蜗道， 253是叶轮腔盖， 254是叶轮流道， 255是闭式叶轮， 256是转移段流道截面的导轮部分， 257是带外壳的向心导轮， 258是导轮增压流道， 259是后盖上的汇流中心蜗道， 260是后盖及其出管。 Variable angle outlet tube semi-concentric centrifugal single-stage booster pump is a new type of centrifugal pump. It has valuable features such as the adaptability of the guided flow and the changing operating conditions. It is suitable for the simple modification of the existing centrifugal pump. The main benefit is to reduce costs. It is easy to install and has the potential to improve efficiency. The output of the impeller is usually more specific than the liquid flow. The impeller speed is generally about 10 meters per second. When the equivalent diameter of the runner is increased, the impeller speed can be increased. Referring to FIG. 29, a centrifugal pump structure of a modular combination closed impeller centrifugal booster module and a symmetrical end cover is shown. Among them, 251 is the front end cover and its inlet tube, 252 is the shunt center volute on the front end cover, 253 is the impeller cavity cover, 254 is the impeller flow channel, 255 is the closed impeller, and 256 is the guide wheel section of the flow section of the transfer section 257 is a centripetal guide wheel with a casing, 258 is a guide wheel booster flow path, 259 is a convergence center volute on the rear cover, and 260 is the rear cover and its outlet pipe.

本实例为对称盖变角出管闭式叶轮向心增压单级离心泵，包含 1个半开式叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由半开式叶轮 255、叶轮腔盖 253和向心导轮 257组成，后者分别用作前盖 251和后盖 260，通过轴系及紧固件轴向组合而成。 This example is a single-stage centrifugal centrifugal pump with centrifugal booster and closed-end centrifugal pump with symmetrical cover and variable angle outlet tube. It includes a semi-open impeller centrifugal booster module and two variable-angle outlet-tube symmetrical end-cap modules. The impeller 255, the impeller cavity cover 253, and the centripetal guide wheel 257 are respectively used as the front cover 251 and the rear cover 260, and are formed by axially combining the shaft system and the fastener.

变角出管闭式向心增压单级泵是一种新型离心泵，具有导流程变工况运行适应性等特性，适合于现有技术离心泵的简单改造，主要效益在于降低成本和方便用户安装，同时具有比半开式叶轮更明显地提高效率的潜力。其叶轮输出常势比液流，叶轮速度一般以 10 米 /秒左右为宜，当流道当量直径加大时叶轮速度可以提高。参照图 30，图中给出了模块化组合内减摩闭式叶轮向心增压模块和对称端盖的离心泵结构。其中， 261是前端盖及其入管， 262是前端盖上的分流中心蜗道， 263是叶轮前端腔阻气间隙， 264是二相流入管， 265是叶轮腔盖， 266是铆钉中的前后端腔连通均压孔， 267 是带外壳的向心导轮， 268是闭式叶轮， 269是后盖上的汇流中心蜗道， 270是后盖及其出管。 Variable angle outlet tube closed centrifugal single-stage pump is a new type of centrifugal pump, which has the characteristics of adaptability to the operating conditions of the guided flow and changing conditions. It is suitable for the simple modification of the existing centrifugal pump. The main benefits are reduced cost and convenience. User-installed, with the potential to increase efficiency significantly more than half-open impellers. The output of the impeller is more constant than the liquid flow. The impeller speed is generally about 10 meters per second. When the equivalent diameter of the runner is increased, the impeller speed can be increased. Referring to Fig. 30, the structure of a centrifugal pump with a modular combination internal friction reducing closed impeller centrifugal booster module and a symmetrical end cover is shown. Among them, 261 is the front end cap and its inlet tube, 262 is the shunt center volute on the front end cap, 263 is the impeller front cavity choke gap, 264 is the two-phase inflow tube, 265 is the impeller cavity cover, and 266 is the front and rear ends in the rivet The cavity communicates with the pressure equalization hole, 267 is a centripetal guide wheel with a housing, 268 is a closed impeller, 269 is a convergence center worm on the back cover, and 270 is the back cover and its outlet pipe.

本实例为对称盖变角出管减摩闭式叶轮向心增压单级离心泵，包含 1个减摩闭式叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式叶轮 268、叶轮腔盖 265、向心导轮 267及阻气间隙 263、二相流入管 264、前后端腔连通均压孔 266组成，后者分别用作前盖 261和后盖 270, 通过轴系及紧固件轴向组合而成。变角出管减摩闭式向心增压单级泵是一种新型离心泵，具有导流程变工况运行适应性等宝贵特性，并且所釆用的内减摩设计能使效率独立提高 5 %〜9%，因而特别适合于现有技术离心泵的改造，主要效益在于降低成本、提高效率和方便用户安装三个方面。其叶轮输出常势比液流，叶轮速度一般以 10米 /秒左右为宜，当流道当量直径加大时速度可以相应提高。参照图 31，图中给出了模块化组合半开式均速高势比叶轮向心增压模块和对称端盖的离心泵结构。其中， 271是前端盖及其入管， 272是前端盖上的分流中心蜗道， 273是叶轮腔盖， 274是半开式均速高势比叶轮， 275是转移段流道截面的叶轮腔部分， 276是转移段流道截面的导轮部分， 277是带外壳的向心导轮， 278是导轮增压流道， 279是后盖上的汇流中心蜗道， 280是后盖及其出管。 This example is a centrifugal single-stage centrifugal pump with centrifugal pressure-enclosing closed impeller with symmetrical cover and variable angle outlet tube. It includes a centrifugal supercharged centrifugal module with closed-end impeller with friction-reduction closed type and two symmetrical end-cap modules with variable angle outlet tube. The closed impeller 268, the impeller cavity cover 265, the centrifugal guide wheel 267 and the air gap 263, the two-phase inflow pipe 264, and the front and rear cavity communication pressure equalizing holes 266 are used as the front cover 261 and the rear cover 270, respectively. It is formed by axial combination of shaft system and fastener. Variable angle outlet tube anti-friction closed-type centrifugal booster single-stage pump is a new type of centrifugal pump. It has valuable characteristics such as the adaptability of the guide to change the operating conditions, and the internal anti-friction design can improve efficiency independently. % ~ 9%, so it is particularly suitable for the reconstruction of the existing centrifugal pumps. The main benefits are three aspects: reducing costs, improving efficiency, and facilitating user installation. The output of the impeller is more constant than the liquid flow. The impeller speed is generally about 10 meters per second. The speed can be increased when the equivalent diameter of the runner is increased. Referring to Fig. 31, the structure of a centrifugal pump with a modular combination of a half-open type average speed high potential ratio impeller centrifugal booster module and a symmetrical end cover is shown. Among them, 271 is the front end cover and its inlet tube, 272 is the shunt center worm on the front end cover, 273 is the impeller cavity cover, 274 is a semi-open average speed high potential ratio impeller, and 275 is the impeller cavity part of the flow channel section of the transfer section. 276 is the guide wheel section of the runner section of the transfer section, 277 is the centripetal guide wheel with the shell, 278 is the guide wheel booster runner, 279 is the convergence center volute on the rear cover, and 280 is the rear cover and its outlet. tube.

本实例为对称盖变角出管半开式均速高势比叶轮向心增压离心泵，包含 1个半开式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由半开式均速高势比叶轮 274、叶轮腔盖 273、向心导轮 277组成，后者分别用作前盖 271和后盖 280，通过轴系及紧固件轴向组合而成。 This example is a centrifugal centrifugal centrifugal centrifugal pump with a symmetrical cover and a variable-angle outlet pipe, a half-open type, and a high-potential ratio centrifugal pump. Speed high potential ratio impeller centripetal booster module and two variable angle outlet tube symmetrical end cover modules. The former consists of a half-open average speed high potential ratio impeller 274, impeller cavity cover 273, and centripetal guide wheel 277. The latter are respectively Used as the front cover 271 and the rear cover 280, which are axially combined by a shaft system and a fastener.

变角出管半开式高势比向心增压单级泵是一种新型离心泵，釆用模块化组合设计方法组合了对称端盖、高势比叶轮、向心导轮三大新型部件技术。其势动比高达 3〜9，压力系数接近理论值，导流损耗降低一个数量级，导流程自适应变工况运行，其效率大幅度提高，在降低制造成本和方便用户安装使用方面也具有明显优势。其叶轮速度可选在 20米 /秒左右，当流道当量直径加大时速度还可以提高。参照图 32，图中给出了模块化组合闭式均速高势比叶轮向心增压模块和对称端盖的离心泵结构。其中， 281是前端盖及其入管， 282是前端盖上的分流中心蜗道， 283是叶轮腔盖， 284是闭式均速高势比叶轮， 285是转移段流道截面的叶轮腔部分， 286是转移段流道截面的导轮部分， 287是带外壳的向心导轮， 288是导轮增压流道， 289是后盖上的汇流中心蜗道， 290是后盖及其出管。 The variable angle outlet pipe semi-open high-potential centripetal booster single-stage pump is a new type of centrifugal pump. It uses a modular combination design method to combine three new components: a symmetrical end cap, a high-potential ratio impeller, and a centrifugal guide wheel. technology. Its potential ratio is as high as 3 ~ 9, the pressure coefficient is close to the theoretical value, the diversion loss is reduced by an order of magnitude, and the diversion process is adaptively changed under different operating conditions. The efficiency is greatly improved, and it is also obvious in reducing manufacturing costs and facilitating installation and use by users. Advantage. The impeller speed can be selected from about 20 meters per second, and the speed can be increased when the equivalent diameter of the runner is increased. Referring to Fig. 32, the figure shows the structure of a modular combined closed-type high-potential ratio impeller centrifugal booster module and a symmetrical end cover. Among them, 281 is the front end cover and its inlet tube, 282 is the shunt center worm on the front end cover, 283 is the impeller cavity cover, 284 is the closed-type average speed high potential ratio impeller, and 285 is the impeller cavity part of the flow channel section of the transfer section. 286 is the guide wheel section of the runner section of the transfer section, 287 is the centripetal guide wheel with the shell, 288 is the guide wheel booster flow path, 289 is the convergence center volute on the rear cover, and 290 is the rear cover and its outlet pipe .

本实例为对称盖变角出管闭式均速高势比叶轮向心增压单级离心泵，包含 1个闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮 284、叶轮腔盖 283、.向心导轮 287组成，后者分别用作前盖 281和后盖 290，通过轴系及紧固件轴向组合而成。 This example is a single-stage centrifugal centrifugal pump with a closed cover and a constant-velocity high-potential ratio impeller. End cover module, the former consists of closed-type high-speed ratio impeller 284, impeller cavity cover 283, and centripetal guide wheel 287, and the latter is used as the front cover 281 and the rear cover 290, respectively, through the shaft system and the fastener shaft Direction combination.

变角出管闭式高势比向心增压单级泵是一种新型离心泵，采用模块化组合设计方法组合了对称端盖、高势比叶轮、向心导轮三大新型部件技术。其势动比高达 3〜9，压力系数接近理论值，导流损耗降低一个数量级，导流程自适应变工况运行，其效率大幅度提高并且优于半开式，在制造成本、方便安装使用等方面也具有明显优势。其叶轮速度可选在 20 米 /秒左右，当流道当量直径加大时速度还可以提高。参照图 33，图中给出了模块化组合预旋闭式均速高势比叶轮向心增压模块和对称端盖模块的离心泵结构。其中， 291是前端盖及其入管， 292是前端盖上的分流中心蜗道， 293 是轴向来流预旋器， 294是叶轮腔盖， 295是闭式均速髙势比叶轮， 296是转移段流道截面的导轮部分， 297是带外壳的向心导轮， 298是导轮增压流道， 299是后盖上的汇流中心蜗道， 300是后盖及其出管。 The variable angle outlet pipe closed high potential ratio centripetal booster single-stage pump is a new type of centrifugal pump. It adopts the modular combination design method to combine the three new component technologies of symmetrical end cover, high potential ratio impeller and centrifugal guide wheel. The potential ratio is as high as 3-9, the pressure coefficient is close to the theoretical value, the diversion loss is reduced by an order of magnitude, and the diversion process is adaptively changed under different operating conditions. Its efficiency is greatly improved and is better than that of the half-open type. It is easy to install and use at manufacturing cost. It also has obvious advantages. The impeller speed can be selected at about 20 meters per second, and the speed can be increased when the equivalent diameter of the runner is increased. Referring to Figure 33, the figure shows the structure of a centrifugal pump with a modular combination of a pre-spinning closed-type high-potential ratio impeller centrifugal booster module and a symmetrical end cover module. Among them, 291 is the front end cap and its inlet tube, 292 is the shunt center worm on the front end cap, 293 is the axial flow pre-rotator, 294 is the impeller cavity cover, 295 is the closed-type average velocity potential ratio impeller, and 296 is The guide wheel part of the cross section of the flow channel of the transfer section, 297 is a centripetal guide wheel with a housing, 298 is a guide wheel booster flow path, 299 is a convergence center volute on the rear cover, and 300 is the rear cover and its outlet pipe.

本实例为对称盖变角出管预旋闭式均速髙势比轮向心增压单级离心泵，包含 1个预旋闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮 295、装在叶轮吸入室中的预旋器 293、叶轮腔盖 294、向心导轮 297组成，后者分别用作前盖 291和后盖 300，通过轴系及紧固件轴向组合而成。 This example is a single-stage centrifugal pump with centrifugal booster and centrifugal pump for centrifugal pressure equalization with a symmetrical cover and variable angle outlet pipe. Angular outlet tube symmetrical end cover module, the former consists of a closed-type average speed high potential ratio impeller 295, a pre-spinner 293 installed in the impeller suction chamber, an impeller cavity cover 294, and a centripetal guide wheel 297, and the latter is used as the front The cover 291 and the rear cover 300 are axially combined by a shaft system and a fastener.

变角出管预旋闭式高势比向心增压单级泵是一种新型离心泵，釆用模块化组合设计方法组合了对称端盖、高势比叶轮、向心导轮三大新型部件技术，并增添预旋器解决叶轮入口特性问题。其势动比高达 3〜9，压力系数接近理论值，导流损耗降低一个数量级，全程自适应变工况运行，抗气蚀特性良好，其效率大幅度提高，并且制造成本低、安装使用方便。其叶轮速度可达 20米 /秒左右，当流道当量直径加大时还可以提高。参照图 34，图中给出了模块化组合减摩闭式均速高势比叶轮向心增压模块和对称端盖的离心泵结构。其中， 301是前端盖及其入管， 302是前端盖上的分流中心蜗道， 303是前端腔减摩阻气间隙， 304是减摩驱动二相流入管， 305是叶轮腔盖， 306是前后端腔连通均压孔， 307是带外壳的向心导轮， 308是闭式均速高势比叶轮， 309是后盖上的汇流中心蜗道， 310是后盖及其出管。 Variable angle outlet tube pre-spin closed high potential ratio centripetal booster single-stage pump is a new type of centrifugal pump. The method combines three new component technologies of a symmetrical end cap, a high potential ratio impeller, and a centrifugal guide wheel, and a pre-spinner is added to solve the problem of impeller inlet characteristics. Its potential ratio is as high as 3 ~ 9, the pressure coefficient is close to the theoretical value, the diversion loss is reduced by an order of magnitude, the whole process is adaptively changed in operating conditions, the anti-cavitation characteristics are good, its efficiency is greatly improved, and its manufacturing cost is low, and it is easy to install and use . Its impeller speed can reach about 20 meters per second, and it can be increased when the equivalent diameter of the runner is increased. Referring to FIG. 34, a centrifugal pump structure of a modular combination friction reduction closed-type high-potential ratio impeller centrifugal booster module and a symmetrical end cover is shown. Among them, 301 is the front end cover and its inlet tube, 302 is the shunt center volute on the front end cover, 303 is the front end cavity friction reducing air gap, 304 is the friction reducing driving two-phase inflow tube, 305 is the impeller cavity cover, 306 is the front and rear The end cavity communicates with the pressure equalization hole, 307 is a centripetal guide wheel with a shell, 308 is a closed-type average speed high potential ratio impeller, 309 is a convergence center worm on the back cover, and 310 is the back cover and its outlet pipe.

本实例为对称盖变角出管减摩闭式均速高势比叶轮向心增压单级离心泵，包含 1个减摩闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮 308、叶轮腔盖 305、向心导轮 307及阻气间隙 303、二相流入管 304、前后端腔均压孔 306组成组成，后者分别用作前盖 301和后盖 310，通过轴系及紧固件轴向组合而成。 This example is a centrifugal single-stage centrifugal pump with centrifugal pressure-enclosing closed-velocity closed-velocity high-potential ratio impeller centrifugal booster with symmetrical cover and variable angle outlet tube. Angle outlet tube symmetrical end cover module, the former is composed of closed average speed high potential ratio impeller 308, impeller cavity cover 305, centripetal guide wheel 307, and choke gap 303, two-phase inflow tube 304, front and rear cavity pressure equalization holes 306 The latter is used as the front cover 301 and the rear cover 310, respectively, and is formed by axially combining the shaft system and the fastener.

变角出管减摩闭式髙势比向心增压单级泵是一种新型离心泵，采用模块化组合设计方法组合了对称端盖、高势比叶轮、向心导轮三大新型部件技术，并配置内减摩技术解决轮盘摩擦问题。其势动比高达 3〜9，压力系数接近理论值，导流损耗降低一个数量级，并有导流程变工况适应性。其内机械损耗减小 82%〜95 %，制约泵效率的三大瓶颈问题均不存在，效率提高幅度高达两位百分数，并且制造成本低、安装使用方便。其叶轮速度不受轮盘摩擦损耗制约，可达 20米 /秒以上，流道当量直径越大，叶轮速度可以选得越髙，因而特别适合于高扬程场合。参照图 35，图中给出了模块化组合减摩预旋闭式均速高势比叶轮向心增压模块和对称端盖的离心泵结构。其中， 311是前端盖及其入管， 312是轴向来流预旋器， 313是前端腔减摩阻气间隙， 314是减摩驱动二相流入管， 315是叶轮腔盖， 316是前后端腔连通均压孔， 317是带外壳的向心导轮， 318是闭式均速高势比叶轮， 319是后盖上的汇流中心蜗道， 320 是后端盖及其出管。 Variable angle outlet tube friction reducing closed potential ratio centripetal booster single-stage pump is a new type of centrifugal pump. It adopts modular combination design method to combine three new components: symmetrical end cap, high potential ratio impeller and centripetal guide wheel. Technology, and equipped with internal friction reduction technology to solve the problem of wheel friction. Its potential-to-motion ratio is as high as 3-9, the pressure coefficient is close to the theoretical value, the diversion loss is reduced by an order of magnitude, and the process flow is adaptable to changing conditions. The mechanical loss is reduced by 82% ~ 95%, the three major bottlenecks that restrict the efficiency of the pump are not present, the efficiency is increased by up to two percentages, the manufacturing cost is low, and the installation and use are convenient. The impeller speed is not restricted by the friction loss of the disc, and it can reach more than 20 meters per second. The larger the equivalent diameter of the runner, the more the impeller speed can be selected, so it is especially suitable for high-lift situations. Referring to FIG. 35, the structure of a centrifugal pump with a modular combination antifriction pre-spinning type high-potential ratio impeller centrifugal booster module and a symmetrical end cover is shown. Among them, 311 is the front end cover and its inlet tube, 312 is the axial incoming flow pre-rotator, 313 is the front end cavity friction reducing air gap, 314 is the friction reducing driving two-phase inflow tube, 315 is the impeller cavity cover, and 316 is the front and rear ends The cavity communicates with the pressure equalization hole, 317 is a centripetal guide wheel with a shell, 318 is a closed type average speed high potential ratio impeller, 319 is a convergence center volute on the rear cover, and 320 is a rear end cover and its outlet pipe.

本实例为对称盖变角出管减摩预旋-闭式均速高势比叶轮向心增压单级离心泵，包含 1 个减摩预旋闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮 318、叶轮腔盖 315、向心导轮 317、预旋器 312及阻气间隙 313、二相流入管 314、前后端腔均压孔 316组成，后者分别用作前盖 311和后盖 320，通过轴系及紧固件轴向组合而成。 This example is a centrifugal single-stage centrifugal pump with centrifugal pressure-reducing pre-spinning and closed-type constant-velocity high-potential-ratio centrifugal booster with a symmetric cover and variable angle outlet tube. Module and two variable-angle outlet tube symmetrical end cover modules, the former consists of closed-type average velocity high potential ratio impeller 318, impeller cavity cover 315, centripetal guide wheel 317, pre-spinner 312 and choke gap 313, two-phase inflow tube 314. The pressure equalization holes 316 of the front and rear chambers are used, and the latter is used as the front cover 311 and the rear cover 320, respectively, and is formed by axially combining the shaft system and the fastener.

变角出管减摩预旋闭式高势比向心增压单级泵是一种新型离心泵，采用模块化组合设计方法组合了对称端盖、高势比叶轮、向心导轮三大新型部件技术，并配置内减摩技术解决轮盘摩擦问题，配置预旋器解决叶轮入口特性问题。其势动比高达 3〜9，压力系数接近理论值，导流损耗降低一个数量级，并具有特别宝贵的全程变工况适应性。其内机械损耗减小 82%〜95 %，制约泵效率的三大瓶颈问题均不存在，效率提高幅度达两位百分数，效率特性曲线全面上扬，抗气蚀特性达到理想化状态，并且制造成本低、安装使用方便。其叶轮速度不受轮盘摩擦损耗制约，可达 20米 /秒以上，流道当量直径越大，叶轮速度可以选得越高，普适于各种应用场合。参照图 36，图中给出了模块化组合超减摩预旋闭式均速高势比叶轮向心增压模块和对称端盖的离心泵结构。其中， 321是前端盖及其入管， 322是轴向来流预旋器， 323是阻气间隙， 324是前端腔减摩驱动二相流入管， 325是叶轮腔盖， 326是延伸包覆转移段流道的叶轮盖， 327是闭式均速高势比叶轮， 328是后端腔减摩驱动入管， 329是带外壳的向心导轮， 330是后盖及其出管。 Variable angle outlet tube anti-friction pre-spin closed high potential ratio centripetal booster single-stage pump is a new type of centrifugal pump. The design method combines three new component technologies: symmetrical end cap, high potential ratio impeller, and centrifugal guide wheel. It is also equipped with internal friction reduction technology to solve the problem of wheel friction, and a pre-spinner is used to solve the problem of impeller inlet characteristics. Its potential-to-motion ratio is as high as 3 to 9, the pressure coefficient is close to the theoretical value, the diversion loss is reduced by an order of magnitude, and it has particularly valuable adaptability to the whole process of changing conditions. The mechanical loss is reduced by 82% ~ 95%, the three major bottlenecks that restrict the efficiency of the pump are not present, the efficiency is increased by two percentages, the efficiency characteristic curve is comprehensively raised, the anti-cavitation characteristics have reached an ideal state, and the manufacturing cost Low, easy to install and use. The impeller speed is not restricted by the friction loss of the disc, and it can reach more than 20 meters per second. The larger the equivalent diameter of the flow path, the higher the impeller speed can be selected, which is generally suitable for various applications. Referring to FIG. 36, the figure shows a centrifugal pump structure with a modular combination of over-friction, pre-spin-closed, high-potential ratio impeller centripetal booster module and symmetrical end cover. Among them, 321 is the front end cover and its inlet tube, 322 is the axial incoming flow pre-rotator, 323 is the air blocking gap, 324 is the front-end cavity friction reduction driving two-phase inflow tube, 325 is the impeller cavity cover, and 326 is the extension coating transfer The impeller cover of the segment flow channel, 327 is a closed-type average speed high-potential ratio impeller, 328 is a rear cavity anti-friction driving inlet pipe, 329 is a centripetal guide wheel with a shell, and 330 is a rear cover and its outlet pipe.

本实例为对称盖变角出管超减摩预旋闭式均速高势比叶轮向心增压离心泵，包含 1个超减摩预旋闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由带有延伸包覆转移段流道的叶轮盖 326的闭式均速高势比叶轮 327、叶轮腔盖 325、向心导轮 329、预旋器 322及阻气间隙 323、前端腔二相流入管 324、后端腔二相流入管 328组成，后者分别用作前盖 321和后盖 330，通过轴系及紧固件轴向组合而成。 This example is a centrifugal supercharged centrifugal centrifugal centrifugal pump with super-friction and pre-spinning closed-speed high-potential ratio impeller. And two variable-angle exit-tube symmetrical end-cap modules, the former consists of an impeller cover 326 with an impeller cover 326 that extends and covers the flow path of the closed section. The impeller cover 326, impeller cavity cover 325, centripetal guide wheel 329, The spinner 322 and the choke gap 323, the front-end cavity two-phase inflow pipe 324, and the rear-end cavity two-phase inflow pipe 328 are used as the front cover 321 and the rear cover 330, respectively, and are axially combined by a shaft system and a fastener. Made.

变角出管超减摩预旋闭式髙势比向心增压单级泵是一种新型离心泵，采用模块化组合设计方法组合了对称端盖、高势比叶轮、向心导轮三大新型部件技术，并配置超减摩技术解决轮盘摩擦问题并降低转移段流道摩擦损耗，配置预旋器解决叶轮入口特性问题。其势动比高达 3〜9，压力系数接近理论值，导流损耗降低一个数量级，并具有特别宝贵的全程变工况适应性。其内机械损耗减小 82%〜95 %，制约泵效率的三大瓶颈问题均不存在，效率提高的幅度最大，效率特性曲线全面上扬，抗气蚀特性达到理想状态，并且制造成本不高，安装使用很方便。其叶轮速度不受轮盘摩擦损耗制约，且入导速度制约也相应减轻，因而具有最高的叶轮速度上限，流道当量直径越大，叶轮速度可选得越髙。该泵普适于各种应用场合。图 37〜图 46是依据模块化方法组合向心增压模块和对称端盖模块构成向心增压多级离心泵的实例。下文首先从总体上说明这些向心增压多级离心泵的共同特征和优势特性，然后对每一种泵的个性特征和效果以列表的方式予以说明。 Variable angle outlet tube super friction reducing pre-spinning potential ratio centripetal booster single-stage pump is a new type of centrifugal pump. It adopts modular combination design method to combine three symmetrical end caps, high potential ratio impellers, and centripetal guide wheels. Large new component technology, and equipped with super friction reduction technology to solve the problem of wheel friction and reduce the friction loss of the flow channel in the transfer section, and equipped with a pre-spinner to solve the problem of impeller inlet characteristics. Its potential-to-moment ratio is as high as 3-9, the pressure coefficient is close to the theoretical value, the diversion loss is reduced by an order of magnitude, and it has particularly valuable full-range variable operating condition adaptability. The mechanical loss is reduced by 82% ~ 95%, and the three major bottlenecks that restrict the efficiency of the pump are not present. The efficiency increase is the largest, the efficiency characteristic curve is comprehensively raised, the anti-cavitation characteristics reach the ideal state, and the manufacturing cost is not high. Easy to install and use. The impeller speed is not restricted by the friction loss of the disc, and the restriction of the conduction speed is also reduced accordingly, so it has the highest upper limit of the impeller speed. The larger the equivalent diameter of the runner, the more the impeller speed can be selected. The pump is suitable for a wide range of applications. Figures 37 to 46 are examples of a centrifugal multi-stage centrifugal pump constructed by combining a centripetal booster module and a symmetrical end cap module according to a modular approach. The following first describes the common characteristics and advantages of these centrifugal multi-stage centrifugal pumps in general, and then describes the individual characteristics and effects of each pump in a list manner.

向心增压多级离心泵包括多个向心增压模块，图 19〜图 27所示实例给出了一些可能的模块，不同的模块具有不同的特性，它们在叶轮的技术原理、结构、工艺上的差异，以及径向和轴向定位止口、动配合间隙、转移段流道截面合成等前文已有详细说明。由于向心增压模块在装配结构和流场参数上的空间周期性，这种模块具有在转轴的一般或特殊约束结构的挠度限度内进行轴向串联的宝贵属性，这是模块化构造多级泵的原理基础和限制。 The centrifugal booster multistage centrifugal pump includes multiple centripetal booster modules. The examples shown in Figure 19 to Figure 27 show some possible modules. Different modules have different characteristics. They are in the technical principle, structure, The differences in technology, as well as the radial and axial positioning of the stop, the dynamic fit clearance, and the cross section synthesis of the flow channel section of the transfer section have been described in detail previously. Thanks to The spatial periodicity of the core pressurization module on the assembly structure and flow field parameters. This module has the valuable attribute of axial series connection within the deflection limit of the general or special constraint structure of the rotating shaft. This is the modular construction of multi-stage pumps. Principle basis and limitations.

关于规格的互换性和父规格的查表检验互换性问题前文已作过说明，并结合单级泵的组合实例作了表述，这在多级泵的组合实例中同样适用。多级泵的一个特殊问题是，当级数较多和压力或扬程较高时，其外壳的最高耐压分段设计较为节约，如此，则其前后端盖模块、分段的向心增压模块规格之互换性也应变为在相应的子域中成立。 The interchangeability of specifications and the check of the parent specification to check the interchangeability have been explained previously, and combined with a combination example of a single-stage pump, which is also applicable to the combination example of a multi-stage pump. A special problem of multi-stage pumps is that when the number of stages is high and the pressure or head is high, the maximum pressure-resistant segmented design of the casing is more economical. In this way, the front and rear cover modules and the segmented centrifugal pressure increase The interchangeability of module specifications should also be established in the corresponding subdomains.

有基于此，本发明模块化组合多级离心泵的具体方案是：包含 2个变角度出管对称端盖模块和最多为 64个的多个向心增压模块，两种模块依据对应的子规格各具完全互换性，或者依据对应的父规格经查表检验介质、最高转速、最高温度、最高耐压等参数互换性成立，其中最高耐压的互换性或者是轴向分段成立的，按照 "液流从近轴环形口带环量流入和流出" 的连接模式，将对称端盖模块分作前后盖，将向心增压模块依次轴向串联，全部模块轴向组合，即构成具有模块互换性的对称盖变角出管向心增压多级离心泵，组合是指设计中的连接配合、生产中的装配和使用中的修配，互换性覆盖这些过程。 Based on this, the specific scheme of the modular combined multi-stage centrifugal pump of the present invention is: it includes 2 variable angle outlet pipe symmetrical end cover modules and a plurality of centripetal booster modules with a maximum of 64, and the two modules are based on the corresponding sub-modules. The specifications are completely interchangeable, or according to the corresponding parent specifications, the compatibility of the parameters such as medium, maximum speed, temperature, and maximum pressure is established through a look-up table. Among them, the maximum pressure withstandability or axial segmentation If it is established, according to the connection mode of "fluid flow in and out from the paraxial annular mouth with ring volume," the symmetrical end cover module is divided into front and rear covers, and the centripetal booster module is axially connected in series in sequence, and all modules are axially combined. That is to say, a symmetric cover variable angle outlet tube centrifugal booster multistage centrifugal pump with modular interchangeability is formed. The combination refers to connection and coordination in design, assembly in production and repair in use, and interchangeability covers these processes.

依据模块化组合方法，向心增压模块和对称端盖或者还是经过参数规划的。其中，前者由向心导轮、闭式叶轮和叶轮腔盖轴向组合而成，后者是带中心蜗道和吻接管道的对称端盖单一零件， 2个对称端盖分别用作前端盖和后端盖。泵中必然有轴系部件，包括转轴、轴承、键槽和键、轴封和填料函及软挡圈等，其中转轴是包含级参数的标准化零件。在生产或维修时，向心增压模块按照导轮、叶轮和叶轮腔盖板顺序装配，三者分别通过外壳止口、转轴和导轮之叶轮腔定位，或者有其它附件时按其具***置伺机装配。拆卸程序则相反。 According to the modular combination method, the centripetal booster module and the symmetrical end cap are either parameterized. Among them, the former is formed by the axial combination of a centrifugal guide wheel, a closed impeller and an impeller cavity cover, and the latter is a single part of a symmetrical end cap with a central worm and a kiss pipe, and two symmetrical end caps are used as front end covers, respectively. And back cover. There must be shafting components in the pump, including the shaft, bearings, keyways and keys, shaft seals and stuffing boxes, and soft retaining rings, etc., where the shaft is a standardized part that contains stage parameters. During production or maintenance, the centrifugal booster module is assembled in the order of the guide wheel, impeller and impeller cavity cover plate, and the three are positioned by the casing stop, the shaft and the impeller cavity of the guide wheel, or according to their specific positions when other accessories are available Opportunistic assembly. The disassembly procedure is reversed.

多级泵运行时，液流从入管以稳定流速进入前端盖中心蜗道，在其中受壁面约束转换为三维运动生成环量，再从近轴环形口流出，此为前端边界流程段。液流分流进入第 1个赋能模块的各叶轮流道，从中接受叶片法向力功沿途加速并积分离心力功增加比能，然后经转移段流道进入导轮，在其中减速增压后，转 90度从近轴环形出口带环量流出，此为第 1个赋能周期。除了静压力的积累和传递外，液流进入和流出第 2个赋能模块，以及陆续进入和流出串联的第 3、 ……第 n个……直至最后一个赋能模块的流态参数是周期性地重复的，包括入口的带环量分流和出口的带环量汇流过程的周期性，这些重复的周期构成多级赋能流程段。液流从末级赋能模块汇流进入后盖中心蜗道，受壁面约束进行三维分量整理和相互间的转换，最后以稳定流速从吻接出管流出，此为后端边界流程段。 When the multi-stage pump is running, the liquid flow enters the central volute of the front cover from the inlet pipe at a stable flow rate, and is constrained by the wall surface to be converted into a three-dimensional motion to generate a ring volume, and then flows out from the paraxial annular port. This is the front end boundary flow segment. The liquid flow shunts into the impeller flow channels of the first energizing module, receives the normal force work of the blades to accelerate along the way and integrates the centrifugal force work to increase the specific energy, and then enters the guide wheel through the transfer section flow channel. After decelerating and supercharging, Turn 90 degrees to flow out from the paraxial annular exit with a circular flow. This is the first energization cycle. In addition to the accumulation and transfer of static pressure, the flow enters and exits the second energizing module, and successively enters and exits the third, ..., nth ... the flow parameter of the last energizing module is the period The repetitive nature of the cycle includes the periodicity of the looped flow diversion at the inlet and the looped flow confluence at the exit. These repetitive periods constitute a multi-level energizing process segment. The liquid flow converges from the end-stage energizing module into the central volute of the rear cover, and is constrained by the wall surface to perform three-dimensional component arrangement and mutual conversion. Finally, the liquid flows out from the kiss-out pipe at a stable flow rate. This is the back-end boundary process segment.

上述流程的优势特点是- The advantages of the above process are −

1、全程保守环量，各级模块导流负荷减轻，时间和空间变化率减小，流场稳定性好，加上多级泵的减速优势，各级导流损耗因而同时显著减小。 2、模块间分流、汇流约束状况改善，加上多级低速优势，其局部损耗将减小或消除，其变工况适应性、抗气蚀特性也因减速而改善。 1. Conservative circulation throughout the process, the diversion load of modules at all levels is reduced, the time and space rate of change is reduced, the stability of the flow field is good, and the deceleration advantage of the multi-stage pump reduces the diversion losses at all levels. 2. Improved conditions of shunting and convergence between modules, coupled with the multi-level low-speed advantage, its local loss will be reduced or eliminated, and its adaptability to changing conditions and anti-cavitation characteristics will also be improved due to deceleration.

3、对于采用预旋均速高势比叶轮模块者，由于全程完备约束，该多级泵将具有最高的水力效率和完全的变工况适应性，其全程水力损耗属于纯粹的沿途损耗模式，在一定的级数范围内，这种损耗将随着级数的增加而减小。 3. For those who use the pre-rotating average speed high potential ratio impeller module, due to the complete constraints of the whole process, the multi-stage pump will have the highest hydraulic efficiency and complete adaptability to variable working conditions, and its full hydraulic loss belongs to the pure loss mode along the way. Within a certain number of stages, this loss will decrease as the number of stages increases.

预旋均速髙势比向心增压多级泵的沿途损耗分析如下：设叶槽流速不随级数改变，则级叶轮程损耗与级数的平方根成反比，因而全程叶轮损耗与级数的平方根成正比。由于级导流程损耗与入导速度的 3次方成正比因而与级数的 1.5次方成反比，则全程导流损耗与级数的平方根成反比。又假设叶槽速度比入导速度低一个数量级，则级叶轮程损耗比级导流程损耗小两个数量级左右。由于全程各类损耗都包含级数乘性因子，因而多级泵的全程损耗对单级泵求归一化比值时，可以应用叶导损耗比例关系作为权因子，再利用级损耗与级数的关系，就可以求出多级泵归一化于单级泵的全程损耗比，举例计算的结果如表 13。 The analysis of the loss along the path of the pre-spinning average velocity potential ratio centripetal booster multistage pump is as follows: Assuming that the flow velocity of the vane groove does not change with the number of stages, the impeller path loss is inversely proportional to the square root of the number of stages. The square root is proportional. Since the stage flow loss is proportional to the third power of the input speed and thus inversely proportional to the 1.5 power of the number of stages, the total flow loss is inversely proportional to the square root of the number of stages. It is also assumed that the speed of the vane slot is one order of magnitude lower than the speed of the input guide, and the stage impeller loss is about two orders of magnitude smaller than the stage guide loss. Because all types of losses in the whole process include the multiplicative factor of the series, when the normalized ratio of the total loss of the multi-stage pump to the single-stage pump is used, the proportional relationship between the leaf conduction loss can be applied as the weight factor, and the loss of the stage and the number of stages can be used again. Relationship, we can find the total loss ratio of the multi-stage pump normalized to the single-stage pump.

表 13 设单级泵叶导沿途损耗比为 2:98，叶槽等速之多级泵全程损耗比与级数关系表 Table 13 Assuming the loss ratio of the single-stage pump along the vane guide is 2:98, and the relationship between the total loss ratio and the number of stages of a multi-stage pump with constant speed of the vane slot

增加级数可以提高效率，这是多级泵的优势。但如果叶槽流速不是足够低，全程损耗比凹函数的极小值点将对应一个较小的级数，提高效率的潜力将不会超过一个数量级。

Increasing the number of stages can increase efficiency, which is the advantage of multi-stage pumps. However, if the flow velocity of the lobes is not sufficiently low, the minimum point of the total loss ratio than the concave function will correspond to a smaller number of stages, and the potential for improving efficiency will not exceed an order of magnitude.

4、采用内减摩叶轮者，其内效率和总效率的提高将超过 5〜9%的幅度而接近其上限，该上限是指较之单级泵而言的。比之于多级泵自身，则减摩增效上限将因叶轮速度的降低而降低，而叶轮线速度及轮径需求是与级数的平方根成反比的，因而内减摩技术对于多级泵的效益将不会有单级泵那么显著。 4. For those who adopt internal friction reducing impeller, the improvement of internal efficiency and total efficiency will exceed the range of 5-9% and approach its upper limit, which is compared with single-stage pump. Compared with the multi-stage pump itself, the upper limit of friction reduction and efficiency will be reduced due to the reduction of the impeller speed, and the impeller linear speed and wheel diameter requirements are inversely proportional to the square root of the number of stages. The benefits will not be as significant as with single-stage pumps.

从效率、成本等多因素技经价值考虑，模块化组合多级离心泵的共性特点和优势是： From the perspective of multi-factor technical and economic values such as efficiency and cost, the common features and advantages of modular multi-stage centrifugal pumps are:

1、向心增压模块具有互换性，具有互相及与边界模块间的连接规范性，其向心增压导流结构体积最小，成本最低，并且效率也较高。 1. The centripetal booster module is interchangeable and has the normative connection to each other and to the boundary module. The centripetal booster diversion structure has the smallest volume, the lowest cost, and high efficiency.

2、对称端盖模块具有前后、单多级间的通用性和与之相关的互换性，具有与赋能模块间的连接规范性，具有变角度安装的使用方便性，比之传统的外壳，其体积大为减小，制造成本因而较低，其适应范围广，效率也较高。 2. The symmetrical end cover module has the versatility of front and back, single and multi-level and the interchangeability related to it, has the standardization of connection with the enabling module, and has the convenience of use with variable angle installation, compared with the traditional shell Its volume is greatly reduced, its manufacturing cost is therefore lower, its range of adaptation is wide, and its efficiency is also high.

3、在整体上，基于上述连接规范性、模块互换性、通用性，设计方案直接体现或者潜在地蕴含了模块化组合方法带来的设计、制造和使用过程的技术经济利益，包括减少工作量、缩短工期、增加方便度、简化产品型系和材料配件规格、减少规范性技术壁垒、加快技术和物质流转、多因素降低成本，等等。对称盖变角出管向心增压多级离心泵各不同技术实例的特征差异、性能差异与单级泵基本相同， "标示特征的离心泵名称"和 "个性技术特征及其效果标示和说明"栏名和内容也大部分相同，但有关键性的内容差异，为便于査找和比对，仍冗列说明于表 12。 3. On the whole, based on the above-mentioned connection specification, module interchangeability, and versatility, the design scheme directly reflects or potentially contains the technical and economic benefits of the design, manufacturing and use process brought by the modular combination method, including reducing work. Volume, shorten the construction period, increase convenience, simplify product types and material accessories specifications, reduce regulatory technical barriers, increase Fast technology and material flow, multiple factors to reduce costs, etc. The characteristics and performance differences of different technical examples of centrifugal booster multi-stage centrifugal pumps with variable angle outlet pipes with symmetrical caps are basically the same as those of single-stage pumps. "The column names and contents are also mostly the same, but there are key content differences. For ease of searching and comparison, they are still listed in Table 12 redundantly.

对称盖变角出管向心增压多级离心泵的个性特征及其效果说明表图号标示特征的个性技术特征及其效果标示和说明 Personality characteristics and effect description table of centrifugal booster multistage centrifugal pump with variable angle outlet tube of symmetrical cover

离心泵全名称 (将创新特征或传统特征包含在创新组合中，产生积极效果）对称盖变角出管包含多个半开式叶轮向心增压模块，叶轮输出常势比液流入导。图 37 半开式叶轮向心其特性是：导流程自适应变工况运行，导流效率提高，但低于增压多级离心泵高势比液流，叶轮程效率低于闭式叶轮。 Full name of the centrifugal pump (Including innovative features or traditional features in the innovative combination, which has a positive effect) Symmetrical cover variable angle outlet pipe Contains multiple semi-open impeller centrifugal booster modules, and the impeller output is always more than liquid inflow guide. Fig. 37 Semi-open impeller centripetal Its characteristics are as follows: The guided flow is adaptively changed under different operating conditions, and the diversion efficiency is improved, but it is lower than that of the boosted multistage centrifugal pump.

对称盖变角出管包含多个闭式叶轮向心增压模块，叶轮输出常势比液流入导。图 38 闭式叶轮向心增其特性是：导流程自适应变工况运行，导流效率提高，但低于压多级离心泵高势比液流。 Symmetric cover variable angle outlet pipe contains multiple closed impeller centripetal booster modules, and the impeller output is always more conductive than the liquid inflow. Fig. 38 Closed-type impeller increases centripetally Its characteristics are: The guide flow is adaptively changed under different operating conditions, and the diversion efficiency is improved, but it is lower than the high potential ratio liquid flow of the pressure multistage centrifugal pump.

对称盖变角出管包含多个内减摩闭式叶轮向心增压模块，设阻气间隙、前后端内减摩闭式叶轮腔连通均压孔、减摩驱动二相流入管等结构，具有内减摩机制。图 39 The symmetrical cover variable angle outlet pipe includes multiple internal friction reducing closed-wheel impeller centrifugal booster modules, which are provided with air blocking gaps, front and rear internal friction reducing closed impeller cavities, pressure equalization holes, and friction reducing driving two-phase inflow pipes. With internal friction reduction mechanism. Fig. 39

向心增压多级离其特性是：导流程自适应变工况运行，导流效率提高，但低于心泵高势比液流，内效率提高到极限。 The characteristics of centripetal pressurization are as follows: The pilot process is adaptively changed under different operating conditions, and the diversion efficiency is improved, but it is lower than the high potential ratio liquid flow of the heart pump, and the internal efficiency is increased to the limit.

包含多个半开式均速高势比叶轮向心增压模块，设 L形叶片、对称盖变角出管 Contains multiple semi-open type constant speed high potential ratio impeller centrifugal booster modules, with L-shaped blades, symmetrical cover variable angle outlet pipe

反切向出口、叶槽尾部加速段、均速岔道等结构，具有遏制相半开式均速高势 Anti-tangential exit, tail groove accelerating section, average speed bifurcation and other structures have a containment phase

图 40 对涡旋、叶轮输出减速、低速入导等机制。其特性是：导流程比叶轮向心增压 Figure 40 shows the vortex, impeller output deceleration, and low-speed guidance. Its characteristics are:

自适应变工况运行，压力系数提高，势动比高达 3〜9，导流损多级离心泵 Adaptive variable operating conditions, increased pressure coefficient, high potential-to-dynamic ratio of 3-9, diversion loss, multi-stage centrifugal pump

耗降低一个数量级，叶轮程效率低于闭式叶轮。 The power consumption is reduced by an order of magnitude, and the impeller stroke efficiency is lower than that of the closed impeller.

包含多个均速高势比闭式叶轮向心增压模块，设 L形叶片、反对称盖变角出管 Contains multiple constant speed high potential ratio closed impeller centripetal booster modules, with L-shaped blades, anti-symmetric cover and variable angle outlet pipe

切向出口、叶槽尾部加速段、均速岔道等结构，具有遏制相对闭式均速高势比 Structures such as tangential exit, tail section acceleration section, average speed bifurcation, etc., have a relatively closed average speed high potential ratio

图 41 涡旋、叶轮输出减速、低速入导等机制。其特性是：导流程自叶轮向心增压多 Figure 41 Vortex, impeller output deceleration, low-speed guidance, etc. Its characteristics are:

适应变工况运行，压力系数提高，势动比高达 3〜9，导流损耗级离心泵 Adapt to variable operating conditions, increase pressure coefficient, potential ratio up to 3-9, diversion loss level centrifugal pump

降低一个数量级，叶轮程效率高于半开式叶轮。 Reduced by an order of magnitude, the impeller stroke efficiency is higher than the semi-open impeller.

包含多个预旋闭式均速高势比叶轮向心增压模块，设 L形叶片、对称盖变角出管 Contains multiple pre-spinning closed-velocity high-potential ratio impeller centrifugal booster modules with L-shaped blades, symmetrical cover variable angle outlet pipes

反切向出口、叶槽尾部加速段、均速岔道等结构，具有遏制相预旋闭式均速高 Anti-tangential exit, tail groove acceleration section, average speed bifurcation and other structures with containment phase

图 42 对涡旋、叶轮输出减速、低速入导、同步预旋等机制。其特性势比叶轮向心增 Figure 42 shows the mechanisms of vortex, impeller output deceleration, low-speed guidance, and synchronous pre-spin. Its characteristics are increased centripetally than the impeller

是：全程自适应变工况运行，压力系数提高，势动比高达 3〜9，压多级离心泵 Yes: The whole process is self-adaptive under varying working conditions, the pressure coefficient is increased, and the potential-to-motion ratio is as high as 3 ~ 9.

导流损耗降低一个数量级，抗气蚀特性好。包含多个内减摩闭式均速高势比叶轮向心增压模块，设 L形叶对称盖变角出管 Diversion loss is reduced by an order of magnitude, and cavitation resistance is good. Contains multiple internal friction reducing closed-type high-potential ratio impeller centrifugal booster modules with L-shaped blade symmetrical cover and variable angle outlet tube

片、均速岔道、反切向出口、叶槽尾部相对加速、阻气间隙、内减摩闭式均速 Blade, average speed bifurcation, reverse tangential exit, relative acceleration at the end of the blade groove, air gap, internal friction reduction closed average speed

图 43 前后端腔连通均压孔、减摩驱动二相流入管等结构，具有遏制高势比叶轮向心相对涡旋、叶轮输出减速、低速入导等机制。其特性是：导流增压多级离心泵程自适应变工况运行，压力系数提髙，势动比高达 3〜9，导流损耗降低一个数量级，内机械损耗减小 82%〜95 %。 Figure 43 The front and rear chambers are connected with pressure equalization holes and anti-friction driving two-phase inflow pipes, which have mechanisms to curb high potential ratio centrifugal centripetal relative vortex, impeller output deceleration, and low-speed guide. Its characteristics are: Diversion booster multi-stage centrifugal pump range adaptive variable operating mode operation, pressure coefficient increase, potential ratio up to 3 ~ 9, diversion loss reduced by an order of magnitude, internal mechanical loss reduced by 82% ~ 95% .

包含多个内减摩预旋闭式均速髙势比叶轮向心增压模块，设 L 对称盖变角出管 Contains multiple internal anti-friction, pre-spinning, closed-velocity equalization potential impeller centripetal booster modules, with L symmetrical cover variable angle outlet tube

形叶片、均速岔道、反切向出口、叶槽尾部相对加速、阻气间内减摩预旋闭式隙、前后端腔连通均压孔、减摩驱动二相流入管等结构，具有图 44 均速髙势比叶轮遏制相对涡旋、叶轮输出减速、低速入导、同步预旋、内减摩向心增压多级离等机制。其特性是：全程自适应变工况运行，压力系数提高，心泵抗气蚀特性好，势动比高达 3〜9，导流损耗降低一个数量级，内机械损耗减小 82%〜95 %。 Shaped blades, uniform speed bifurcation, reverse tangential exit, relative acceleration at the tail end of the blade groove, anti-friction pre-spin closed gap in the choke chamber, front and rear cavity communication pressure equalization holes, anti-friction driving two-phase inflow pipe, etc. The mechanism of average speed and potential reduction is that the impeller restrains relative vortex, impeller output deceleration, low-speed inductive guidance, synchronous pre-spinning, internal friction reduction, and centrifugal pressure boosting. Its characteristics are: full self-adaptive variable operating conditions, increased pressure coefficient, good anti-cavitation characteristics of the heart pump, a potential-to-motion ratio of up to 3-9, a reduction in flow loss by an order of magnitude, and an internal mechanical loss of 82% to 95%.

包含多个预旋超减摩闭式均速高势比叶轮向心增压模块，设 L 形叶片、均速岔道、反切向出口、叶槽尾部相对加速、阻气间对称盖变角出管 Contains multiple pre-spin super-friction closed-type high-potential ratio impeller centrifugal booster modules with L-shaped blades, uniform speed bifurcations, reverse tangential outlets, relative acceleration at the end of the blade groove, and symmetrical cover with variable angle between the choke outlets

隙、叶轮盖扩展、减摩驱动双二相流入管等结构，具有遏制相预旋超减摩闭式 Clearance, impeller cover expansion, anti-friction driving dual two-phase inflow pipe, etc., with containment phase

图 45 对涡旋、叶轮输出减速、低速入导、同步预旋、内减摩、转移叶轮均速高势比 Figure 45: Vortex, impeller output deceleration, low-speed guidance, synchronous pre-spin, internal friction reduction, transfer

段流道减摩等机制。其特性是：全程自适应变工况运行，压力向心增压多级离 Dumping channel friction reduction and other mechanisms. Its characteristics are: full-range adaptive variable operating conditions, pressure

系数提高，抗气蚀特性好，势动比高达 3〜9，导流损耗降低一心泵 Increased coefficient, good anti-cavitation characteristics, high potential-to-dynamic ratio of 3 ~ 9, reduced flow loss

个数量级，内机械损耗减小 82 %〜95 %，换向转移损耗进一步降低。 Orders of magnitude, the internal mechanical loss is reduced by 82% ~ 95%, and the commutation transfer loss is further reduced.

包含多个由预旋均速高势比半开式叶轮和半开式导轮组成的向对称盖变角出管心增压模块，设 L形叶片、均速岔道、反切向出口、叶槽尾部预旋双半开式均 Contains a number of semi-open impellers and semi-open guide pressure booster modules consisting of pre-spinning average speed high potential ratio semi-open impellers and semi-open guide wheels, with L-shaped blades, uniform speed bifurcations, reverse tangential outlets, blade slots Tail pre-spin double open

图 46 相对加速、径向同步预旋器等结构，具有遏制相对涡旋、叶轮速高势比向心增输出减速、低速入导、同步预旋等机制。其特性是：全程自适压多级离心泵应变工况运行，压力系数提高，抗气蚀特性好，势动比髙达 3〜 Figure 46 Relative acceleration, radial synchronous pre-rotator and other structures have mechanisms to curb relative vortex, impeller speed high potential ratio to increase centripetal output deceleration, low-speed guide, synchronous pre-rotation and other mechanisms. Its characteristics are: multi-stage centrifugal pump with self-adaptable pressure throughout the operation under strain conditions, increased pressure coefficient, good anti-cavitation characteristics, and a potential ratio of up to 3 ~

9，导流损耗降低一个量级，内损耗减小，结构特别简单等。参照图 37，图中给出了模块化组合半开式叶轮向心增压模块和对称端盖的多级离心泵结构。其中， 331是前端盖中心蜗道， 332是前端盖及其入管， 333是叶轮腔盖， 334是半开式叶轮， 335是带外壳的向心导轮， 336是叶轮流道， 337是转移段流道截面部分， 338 是导轮增压流道.， 339 ¾后盖及其出管， 340是后盖中心蜗道。 9. The diversion loss is reduced by an order of magnitude, the internal loss is reduced, and the structure is particularly simple. Referring to Fig. 37, a multistage centrifugal pump structure with a modular combination of a semi-open impeller centrifugal booster module and a symmetrical end cover is shown. Among them, 331 is the central volute of the front cover, 332 is the front cover and its inlet tube, 333 is the impeller cavity cover, 334 is a semi-open impeller, 335 is a centripetal guide wheel with a casing, 336 is an impeller flow channel, and 337 is a transfer Section flow section, 338 is the supercharged flow channel of the guide wheel, 339 ¾ rear cover and its outlet pipe, 340 is the center volute of the rear cover.

本实例为对称盖变角出管半开式叶轮向心增压多级离心泵，包含最多为 64个的多个半开式叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由半开式叶轮 334、叶轮腔盖 333和向心导轮 335组成，后者分别用作前盖 332和后盖 340，通过轴系及紧固件连接组合。 This example is a semi-open impeller centrifugal multi-stage centrifugal pump with symmetrical cover and variable angle outlet pipe. It includes multiple semi-open impeller centrifugal booster modules with a maximum of 64 and two variable-angle outlet tube symmetrical end cover modules. The former consists of a semi-open impeller 334, an impeller cavity cover 333, and a centripetal guide wheel 335, and the latter is used as a front cover 332 and a rear cover 340, respectively, and is connected and combined through a shaft system and a fastener.

变角出管半开式向心增压多级泵是一新型离心泵，具有导流程变工况运行适应性等特性，适合于现有技术离心泵的简单改造，主要效益在于降低成本和方便用户安装，同时具有提高效率的潜力。其进出管角度可变的特点可以使离心泵的型系规格大为减少。其叶轮输出常势比液流，叶轮速度一般以 10米 /秒左右为宜，当流道当量直径加大时叶轮速度可以提高。多级泵的扬程与级数成正比，增加级数可以达到很高的扬程。对于确定的扬程和流量需求，经数学规划的模块可以降低用户的总拥有成本。参照图 38，图中给出了模块化组合闭式叶轮向心增压模块和对称端盖的多级离心泵结构。其中， 341是前端盖中心蜗道， 342是前端盖及其入管， 343是叶轮腔盖， 344是闭式叶轮， 345是带外壳的向心导轮， 346是叶轮流道， 347是转移段流道截面导轮部分， 348 是导轮增压流道， 349是后端盖及其出管， 350是后端盖中心蜗道。 The semi-open centrifugal booster multistage pump with variable angle outlet pipe is a new type of centrifugal pump, which has the adaptability to guide the process and change the operating conditions, etc. The characteristics are suitable for the simple transformation of the existing centrifugal pumps. The main benefits are that it reduces costs and facilitates installation by users, and has the potential to improve efficiency. Its variable inlet and outlet pipe characteristics can greatly reduce the type specifications of the centrifugal pump. The output of the impeller is usually more specific than the liquid flow. The impeller speed is generally about 10 meters per second. The impeller speed can be increased when the equivalent diameter of the runner is increased. The head of a multi-stage pump is directly proportional to the number of stages. Increasing the number of stages can achieve a high head. For determined head and flow requirements, mathematically planned modules can reduce the user's total cost of ownership. Referring to FIG. 38, a multi-stage centrifugal pump structure of a modular combination closed impeller centrifugal booster module and a symmetrical end cover is shown. Among them, 341 is the central volute of the front cover, 342 is the front cover and its inlet tube, 343 is the impeller cavity cover, 344 is the closed impeller, 345 is the centripetal guide wheel with the shell, 346 is the impeller flow channel, and 347 is the transfer section The runner section of the runner, 348 is the booster runner, 349 is the rear end cap and its outlet tube, and 350 is the center volute of the rear end cap.

本实例为对称盖变角出管闭式叶轮向心增压多级离心泵，包含最多为 64个的多个闭式叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式叶轮 344、叶轮腔盖 343 和向心导轮 345组成，后者分别用作前盖 342和后盖 349, 通过轴系及紧固件连接组合。 This example is a centrifugal multi-stage centrifugal centrifugal pump with a closed-end impeller and a centrifugal pump with a symmetrical cover and variable angle outlet tube. It consists of a closed impeller 344, an impeller cavity cover 343, and a centripetal guide wheel 345. The latter is used as a front cover 342 and a rear cover 349, respectively, and is connected and combined by a shaft system and a fastener.

变角出管闭式向心增压多级泵是一种新型离心泵，具有导流程变工况运行适应性等宝贵特性，适合于现有技术离心泵的简单改造，主要效益在于降低成本和方便用户安装，同时具有提高效率的潜力，增效性能优于半开式。其进出管角度可变的特点可以使离心泵的型系规格大为减少。其叶轮输出常势比液流，叶轮速度一般以 10米 /秒左右为宜，当流道当量直径加大时叶轮速度可以提高。多级泵的扬程与级数成正比，增加级数可以达到很高的扬程。对于确定的扬程和流量需求，经数学规划的模块可以降低用户的总拥有成本。参照图 39，图中给出了模块化组合减摩闭式叶轮向心增压模块和对称端盖的多级离心泵结构。其中， 351是前端盖及其入管和中心蜗道， 352是叶轮腔盖， 353是闭式叶轮， 354 是带外壳的向心导轮， 355是前端腔 V形槽阻气间隙结构， 356是二相流入管， 357是闭式叶轮前盖板， 358是铆钉中的前后端腔连通均压孔， 359是转移段流道截面， 360是后端盖及其出管和中心蜗道。 Variable angle outlet tube closed centrifugal booster multistage pump is a new type of centrifugal pump, which has valuable characteristics such as guided flow and variable operating conditions, and is suitable for the simple modification of existing centrifugal pumps. The main benefits are reduced cost and It is convenient for users to install, and has the potential to improve efficiency. The variable inlet and outlet pipe angles can greatly reduce the size of the centrifugal pump. The output of the impeller is usually more specific than the liquid flow. The impeller speed is generally about 10 meters per second. The impeller speed can be increased when the equivalent diameter of the runner is increased. The head of a multi-stage pump is directly proportional to the number of stages. Increasing the number of stages can achieve a very high head. For determined head and flow requirements, mathematically planned modules can reduce the user's total cost of ownership. Referring to Figure 39, a multistage centrifugal pump structure with a modular combination antifriction closed impeller centrifugal booster module and a symmetrical end cover is shown. Among them, 351 is the front end cover and its inlet tube and the central volute, 352 is the impeller cavity cover, 353 is a closed impeller, 354 is a centripetal guide wheel with a housing, 355 is a front-end cavity V-shaped air gap structure, and 356 is The two-phase inflow pipe, 357 is the closed front impeller cover, 358 is the pressure equalization hole in the front and rear cavity communication in the rivet, 359 is the cross section of the flow channel of the transfer section, 360 is the rear cover and its outlet tube and the central volute.

本实例为对称盖变角出管减摩闭式叶轮向心增压多级离心泵，包含最多为 64个的多个减摩闭式叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式叶轮 353、叶轮腔盖 352和向心导轮 354及阻气间隙 355、二相流入管 356、前后端腔连通均压孔 358 组成，后者分别用作前盖 342和后盖 349，通过轴系及紧固件连接组合。其中，阻气间隙 355、二相流入管 356、前后端腔连通均压孔 358 构成级内减摩装置。在后端腔没有轴封的多级泵结构中，将驱动二相流入管从前端腔近轴处接入，并在叶片宽阔处或者铆钉中心开具通气孔，以保持前后端腔压力相等，这在某些情况下使用可节省管路。其均压作用类似于现有技术中的均压平衡孔，但比液相平衡孔的均压效果显著得多，并且不造成任何容积损失。变角出管减摩闭式向心增压多级泵是一种新型离心泵，具有内减摩因而降低内机械损耗 82〜95 %、导流程变工况运行适应性等宝贵特性，适合于现有技术离心泵的简单改造，主要效益在于降低成本和方便用户安装同时具有提高效率的潜力，增效性能优于半开式。其进出管角度可变的特点可以使离心泵的型系规格大为减少。其叶轮输出常势比液流，叶轮速度一般以 10米 /秒左右为宜，当流道当量直径加大时叶轮速度可以提高。增加级数可以达到很高的扬程，或者提高效率。经数学规划的模块可以降低用户的总拥有成本。参照图 40，图中给出了模块化组合半开式均速高势比叶轮向心增压模块和对称端盖的多级离心泵结构。其中， 361是前端盖中心蜗道， 362是前端盖及其入管， 363是叶轮腔盖， 364是半开式均速高势比叶轮， 365是带外壳的向心导轮， 366是叶轮流道， 367是转移段流道截面导轮部分， 368是导轮增压流道， 369是后端盖及其出管， 370是后端盖中心蜗道。 This example is a centrifugal multi-stage centrifugal pump with centrifugal pressure-increasing closed impeller and centrifugal centrifugal pump with symmetrical cover and variable angle outlet pipe. The cover module is composed of a closed impeller 353, an impeller cavity cover 352, a centripetal guide wheel 354, a choke gap 355, a two-phase inflow pipe 356, a front and rear cavity communication pressure equalization hole 358, and the latter is used as a front cover 342, respectively. And the rear cover 349, connected and combined by a shaft system and a fastener. Among them, the choke gap 355, the two-phase inflow pipe 356, and the front and rear chambers communicate with the pressure equalization hole 358 to constitute an intra-stage friction reducing device. In a multi-stage pump structure with no shaft seal in the rear cavity, the driving two-phase inflow pipe is connected from the proximal shaft of the front cavity, and a vent hole is opened at the blade wide or the center of the rivet to keep the pressure in the front and rear cavity equal. Used in some cases to save tubing. Its pressure equalizing effect is similar to the pressure equalizing hole in the prior art, but the pressure equalizing effect is much more significant than that of the liquid phase balancing hole, and it does not cause any volume loss. Variable angle outlet tube anti-friction closed-type centrifugal booster multi-stage pump is a new type of centrifugal pump. It has valuable characteristics such as internal friction reduction and thus reduced internal mechanical loss of 82 ~ 95%, and adaptability to variable process conditions. The simple retrofit of the prior art centrifugal pump has the main benefits of reducing costs and facilitating installation by the user, and has the potential to improve efficiency. The efficiency-enhancing performance is better than the semi-open type. Its variable inlet and outlet pipe characteristics can greatly reduce the type specifications of the centrifugal pump. The output of the impeller is usually more specific than the liquid flow. The impeller speed is generally about 10 meters per second. The impeller speed can be increased when the equivalent diameter of the runner is increased. Increasing the number of stages can achieve high heads or improve efficiency. Mathematically planned modules can reduce the total cost of ownership for users. Referring to FIG. 40, a multi-stage centrifugal pump structure with a modular combination of a half-open type average speed high potential ratio impeller centrifugal booster module and a symmetrical end cover is shown. Among them, 361 is the central volute of the front cover, 362 is the front cover and its inlet tube, 363 is the impeller cavity cover, 364 is a semi-open type average speed high potential ratio impeller, 365 is a centripetal guide wheel with a casing, and 366 is an impeller. 367 is the cross-section guide wheel section of the flow channel section of the transfer section, 368 is the supercharged flow path of the guide wheel, 369 is the rear end cover and its outlet pipe, and 370 is the center volute of the rear end cover.

本实例为对称盖变角出管半开式叶轮向心增压多级离心泵，包含最多为 64个的多个半开式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由半开式均速高势比叶轮 364、叶轮腔盖 363和向心导轮 365组成，后者分别用作前盖 362和后盖 369，通过轴系及紧固件连接组合。 This example is a semi-open centrifugal multi-stage centrifugal pump with centrifugal pump with symmetrical cover and variable-angle outlet pipe. Tube symmetrical end cover module, the former is composed of a half-open average speed high potential ratio impeller 364, impeller cavity cover 363 and centripetal guide wheel 365, and the latter is used as the front cover 362 and the rear cover 369, respectively, through the shaft system and fastening Piece connection combination.

变角出管半开式高势比向心增压多级泵是一种新型离心泵，采用模块化组合设计方法组合了对称端盖、高势比叶轮、向心导轮三大新型部件技术。其势动比高达 3〜9，级压力系数接近理论值，级导流损耗降低一个数量级，导流程自适应变工况运行，其效率大幅度提高，并在降低制造成本和方便用户安装使用方面也具有明显优势。其进出管角度可变的特点方便用户安装，还可以使离心泵的型系规格大为减少。其叶轮速度可达 20米 /秒左右，当流道当量直径加大时叶轮速度还可以提高。增加多级泵的级数可以达到很髙的扬程，或者进一步提高效率。经数学规划的模块可以降低用户的总拥有成本。参照图 41，图中给出了模块化组合闭式均速高势比叶轮向心增压模块和对称端盖的多级离心泵结构。其中， 371是前端盖中心蜗道， 372是前端盖及其入管， 373是叶轮腔盖， 374是闭式均速高势比叶轮， 375是带外壳的向心导轮， 376是叶轮流道， 377是转移段流道截面导轮部分， 378是导轮增压流道， 379是后端盖及其出管， 380是后端盖中心蜗道。 The variable angle outlet semi-open type high potential ratio centripetal booster multi-stage pump is a new type of centrifugal pump. It adopts a modular combination design method to combine three new component technologies: a symmetrical end cap, a high potential ratio impeller and a centrifugal guide wheel. . Its potential ratio is as high as 3 ~ 9, the stage pressure coefficient is close to the theoretical value, the stage diversion loss is reduced by an order of magnitude, and the guidance process is adaptively changed under different operating conditions. Its efficiency is greatly improved, and it reduces manufacturing costs and facilitates installation and use by users. It also has obvious advantages. Its variable inlet and outlet pipe features are convenient for users to install, and can also reduce the size of the centrifugal pump. The impeller speed can reach about 20 meters per second, and the impeller speed can be increased when the equivalent diameter of the runner is increased. Increasing the number of stages of a multi-stage pump can achieve very high lift, or further increase efficiency. Mathematically planned modules can reduce the total cost of ownership for users. Referring to Figure 41, the figure shows the structure of a multi-stage centrifugal pump with a modular combination closed-type high-potential ratio impeller centrifugal booster module and a symmetrical end cover. Among them, 371 is the central volute of the front cover, 372 is the front cover and its inlet tube, 373 is the impeller cavity cover, 374 is a closed average speed high potential ratio impeller, 375 is a centripetal guide wheel with a casing, and 376 is the impeller flow channel 377 is the guide wheel section of the runner section of the transfer section, 378 is the supercharged runner of the guide wheel, 379 is the rear end cover and its outlet pipe, and 380 is the center volute of the rear end cover.

本实例为对称盖变角出管闭式均速高势比叶轮向心增压多级离心泵，包含最多为 64 个的多个闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮 374、叶轮腔盖 373和向心导轮 375组成，后者分别用作前盖 372和后盖 379，通过轴系及紧固件连接组合。 This example is a centrifugal multistage centrifugal pump with a symmetrical cover and a variable-angle closed-end high-potential-ratio centrifugal booster pump. Variable angle outlet tube symmetrical end cover module. The former consists of a closed-type high-speed ratio impeller 374, an impeller cavity cover 373 and a centripetal guide wheel 375. The latter is used as a front cover 372 and a rear cover 379, respectively. Fastener connection combination.

变角出管闭式髙势比向心增压多级泵是一种新型离心泵，釆用模块化组合设计方法组合了对称端盖、髙势比叶轮、向心导轮三大新型部件技术。其势动比高达 3〜9，级压力系数接近理论值，级导流损耗降低一个数量级，导流程自适应变工况运行，其效率大幅度提高，效率由于半幵式。在降低制造成本和方便用户安装使用方面也具有明显优势。其进出管角度可变的特点方便用户安装，还可以使离心泵的型系规格大为减少。其叶轮速度可达The variable angle outlet tube closed pseudo-potential ratio centripetal booster multistage pump is a new type of centrifugal pump. It adopts a modular combination design method to combine three new component technologies: symmetrical end cap, pseudo-potential ratio impeller, and centrifugal guide wheel . Its potential-to-motion ratio is as high as 3 ~ 9, the stage pressure coefficient is close to the theoretical value, and the stage diversion loss is reduced by an order of magnitude. High and efficient due to the semi-closing style. It also has obvious advantages in reducing manufacturing costs and facilitating user installation and use. Its variable inlet and outlet pipe features are convenient for users to install, and can also greatly reduce the type specifications of the centrifugal pump. Its impeller speed can reach

20 米 /秒左右，当流道当量直径加大时叶轮速度还可以提高。增加多级泵的级数可以达到很高的扬程，或者进一步提高效率。经数学规划的模块可以降低用户的总拥有成本。参照图 42，图中给出了模块化组合预旋闭式均速高势比叶轮向心增压模块和对称端盖的多级离心泵结构。其中， 381是前端盖中心蜗道， 382是前端盖及其入管， 383是叶轮腔盖， 384是闭式均速髙势比叶轮， 385是带外壳的向心导轮， 386是预旋器， 387是叶轮加速流道， 388是导轮增压流道， 389是后端盖及其出管， 390是后端盖中心蜗道。 At about 20 m / s, the impeller speed can also increase when the equivalent diameter of the runner increases. Increasing the number of stages of a multi-stage pump can achieve very high heads or further increase efficiency. Mathematically planned modules can reduce the total cost of ownership for users. Referring to FIG. 42, a multi-stage centrifugal pump structure with a modular combination of a pre-spinning closed-velocity high-potential ratio impeller centrifugal booster module and a symmetrical end cover is shown. Among them, 381 is the central volute of the front end cover, 382 is the front end cover and its inlet tube, 383 is the impeller cavity cover, 384 is a closed-type constant velocity pseudopotential ratio impeller, 385 is a centripetal guide wheel with a casing, and 386 is a prerotator , 387 is the impeller acceleration flow path, 388 is the guide wheel booster flow path, 389 is the rear end cover and its outlet tube, and 390 is the center volute of the rear end cover.

本实例为对称盖变角出管预旋闭式均速高势比叶轮向心增压多级离心泵，包含最多为 64个的多个预旋闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮 384、预旋器 386、叶轮腔盖 383和向心导轮 385组成，后者分别用作前盖 382和后盖 389，通过轴系及紧固件连接组合。 This example is a centrifugal multi-stage centrifugal pump with pre-spinning closed-velocity average-velocity high-potential-ratio centrifugal booster with symmetrical cover and variable-angle outlet pipe. The module consists of a closed-end high-potential ratio impeller 384, a pre-rotor 386, an impeller cavity cover 383, and a centripetal guide wheel 385, and two variable-angle outlet symmetrical end-cap modules, and the latter is used as the front cover 382, respectively. It is combined with the rear cover 389 through a shaft system and fasteners.

变角出管闭式高势比向心增压多级泵是一种新型离心泵，采用模块化组合设计方法组合了对称端盖、高势比叶轮、向心导轮三大新型部件技术。其势动比高达 3〜9，级压力系数接近理论值，级导流损耗降低一个数量级。其预旋器完全消除叶轮入口区的撞击湍流和气蚀问题，使全流程自适应变工况运行，其效率大幅度提高。在降低制造成本和方便用户安装使用方面也具有明显优势。其进出管角度可变的特点方便用户安装，还可以使离心泵的型系规格大为减少。其叶轮速度可达 20米 /秒左右，当流道当量直径加大时叶轮速度还可以提高。增加多级泵的级数可以达到很高的扬程，或者进一步提高效率。经数学规划的模块可以降低用户的总拥有成本。参照图 43，图中给出了模块化组合减摩闭式均速高势比叶轮向心增压模块和对称端盖的多级离心泵结构。其中， 391是前端盖中心蜗道， 392是前端盖及其入管， 393是叶轮腔盖， 394是闭式均速高势比叶轮， 395是带外壳的向心导轮， 396是叶轮前端腔 V形槽阻气间隙， 397是减摩驱动二相流入管， 398是叶轮盖固定铆钉中的前后端腔连通均压孔， 399 是后端盖及其出管， 400是后端盖中心蜗道。 The variable angle outlet tube closed high potential ratio centripetal booster multistage pump is a new type of centrifugal pump. It adopts a modular combination design method to combine three new component technologies: a symmetrical end cap, a high potential ratio impeller and a centrifugal guide wheel. Its potential-to-motion ratio is as high as 3-9, the stage pressure coefficient is close to the theoretical value, and the stage conduction loss is reduced by an order of magnitude. Its pre-spinner completely eliminates the impact of turbulence and cavitation in the impeller inlet area, enables the entire process to adaptively change the operating conditions, and greatly improves its efficiency. It also has obvious advantages in reducing manufacturing costs and facilitating user installation and use. Its variable inlet and outlet pipe features are convenient for users to install, and can also greatly reduce the size of the centrifugal pump. The impeller speed can reach about 20 meters per second, and the impeller speed can be increased when the equivalent diameter of the runner is increased. Increasing the number of stages of a multi-stage pump can achieve very high heads or further increase efficiency. Mathematically planned modules can reduce the total cost of ownership for the user. Referring to Fig. 43, the figure shows the structure of a multi-stage centrifugal pump with a modular combination of friction reducing closed-type high-potential ratio impeller centrifugal booster module and symmetrical end cover. Among them, 391 is the central volute of the front end cover, 392 is the front end cover and its inlet tube, 393 is the impeller cavity cover, 394 is a closed-type average speed high potential ratio impeller, 395 is a centripetal guide wheel with a casing, and 396 is the front end cavity of the impeller V-shaped groove air gap, 397 is the anti-friction driving two-phase inflow pipe, 398 is the pressure equalization hole in the front and rear cavity of the impeller cover fixing rivet, 399 is the rear cover and its outlet tube, 400 is the center volute of the rear cover Road.

本实例为对称盖变角出管减摩闭式均速高势比叶轮向心增压多级离心泵，包含最多为 64个的多个减摩闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速髙势比叶轮 394、叶轮腔盖 393、向心导轮 395及阻气间隙 396、二相流入管 397、前后端腔连通均压孔 398组成，后者分别用作前盖 392和后盖 399，通过轴系及紧固件连接组合。其中，阻气间隙 396、二相流入管 397、前后端腔连通均压孔 398构成级内减摩装置。这种结构可节省管路，并且没有任何容积损失。 This example is a centrifugal multi-stage centrifugal pump with centrifugal pump with symmetrical cover and variable angle outlet tube to reduce friction and close to the average potential. The module and two variable-angle outlet tube symmetrical end cover modules, the former consists of closed-type average velocity potential ratio impeller 394, impeller cavity cover 393, centripetal guide wheel 395 and air gap 396, two-phase inflow tube 397, front and rear cavity Composed of pressure equalization holes 398, which are used as the front cover 392 and the rear cover 399, respectively, and connected and combined by a shaft system and a fastener. Among them, the air blocking gap 396, the two-phase inflow pipe 397, and the front and rear cavity communication pressure equalization holes 398 constitute an in-stage antifriction device. This structure saves pipelines without any volume loss.

变角出管减摩闭式高势比向心增压多级泵是一种新型离心泵，釆用模块化组合设计方法组合了对称端盖、高势比叶轮、向心导轮三大新型部件技术。其势动比高达 3〜9，级压力系数接近理论值，级导流损耗降低一个数量级，导流程自适应变工况运行，其效率大幅度提高。组合内减摩装置使轮盘摩擦损耗减小 82%〜95 %，可以进一步地提高效率。这种泵在降低制造成本和方便用户安装使用方面也具有明显优势，其进出管角度可变的特点方便用户安装，还可以使离心泵的型系规格大为减少。其叶轮速度可达 20米 /秒左右，当流道当量直径加大时叶轮速度还可以提高。增加多级泵的级数可以达到很高的扬程，或者进一步提高效率。经数学规划的模块可以降低用户的总拥有成本。参照图 44，图中给出了模块化组合减摩预旋闭式均速髙势比叶轮向心增压模块和对称端盖的多级离心泵结构。其中， 401 是预旋器悬挂肋条， 402 是前端盖及其入管和中心蜗道， 403是叶轮腔盖， 404是预旋器， 405是带外壳的向心导轮， 406是闭式均速高势比叶轮， 407是减摩驱动二相流入管， 408是叶轮前端腔阻气间隙， 409是叶轮盖固定铆钉中的前后端腔连通均压孔， 410是后端盖及其出管和中心蜗道。 Variable angle outlet tube anti-friction closed-type high potential ratio centripetal booster multistage pump is a new type of centrifugal pump. The method combines three new component technologies: symmetrical end cap, high potential ratio impeller, and centrifugal guide wheel. Its potential-to-motion ratio is as high as 3 to 9, the stage pressure coefficient is close to the theoretical value, the stage diversion loss is reduced by an order of magnitude, and the guidance process is adaptively operated under varying operating conditions, and its efficiency is greatly improved. The combined anti-friction device can reduce the disc friction loss by 82% ~ 95%, which can further improve the efficiency. This pump also has obvious advantages in reducing manufacturing costs and facilitating installation and use by users. The variable inlet and outlet pipe angles are convenient for users to install, and the type specifications of centrifugal pumps can be greatly reduced. The impeller speed can reach about 20 meters per second, and the impeller speed can be increased when the equivalent diameter of the runner is increased. Increasing the number of stages of a multi-stage pump can achieve very high heads or further increase efficiency. Mathematically planned modules can reduce the total cost of ownership for users. Referring to FIG. 44, a multi-stage centrifugal pump structure with a modular combination anti-friction pre-spin-closed average speed potential ratio impeller centrifugal booster module and a symmetrical end cover is shown. Among them, 401 is the pre-rotator suspension rib, 402 is the front end cover and its inlet tube and central worm, 403 is the impeller cavity cover, 404 is the pre-rotator, 405 is the centripetal guide wheel with the shell, and 406 is the closed type average speed High potential ratio impeller, 407 is the anti-friction driving two-phase inflow pipe, 408 is the air gap in the front cavity of the impeller, 409 is the pressure equalization hole in the front and rear cavity of the impeller cover fixing rivet, 410 is the rear cover and its outlet tube Central worm.

本实例为对称盖变角出管减摩预旋闭式均速高势比叶轮向心增压多级离心泵，包含最多为 64个的多个减摩预旋闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮 406、预旋器 404、叶轮腔盖 403、向心导轮 405及阻气间隙 408、二相流入管 407、前后端腔连通均压孔 409组成，后者分别用作前盖 402和后盖 410，通过轴系及紧固件连接组合。其中，阻气间隙 408、二相流入管 407、连通均压孔 409构成级模块内减摩装置。 This example is a centrifugal multi-stage centrifugal centrifugal pump with centrifugal pump with centrifugal pressure reduction and pre-spinning closed-rotation and constant-velocity high-potential ratio impeller. A centrifugal booster module and two variable-angle outlet pipe symmetrical end cover modules. The former consists of a closed average speed high potential ratio impeller 406, a pre-rotator 404, an impeller cavity cover 403, a centripetal guide wheel 405, and an air gap 408, The two-phase inflow pipe 407 and the front and rear chambers communicate with pressure equalization holes 409, and the latter is used as the front cover 402 and the rear cover 410, respectively, and is connected and combined by a shaft system and a fastener. Among them, the air blocking gap 408, the two-phase inflow pipe 407, and the pressure equalizing hole 409 constitute a friction reducing device in the module.

变角出管减摩预旋闭式高势比向心增压多级泵是一种新型离心泵，釆用模块化组合设计方法组合了对称端盖、高势比叶轮、向心导轮三大新型部件技术。其势动比高达 3〜9，级压力系数接近理论值，级导流损耗降低一个数量级。组合内减摩装置使轮盘摩擦损耗减小 82%〜95 %，可以进一步地提高效率。组合预旋器完全消除叶轮入口区的撞击湍流和气蚀问题，使全流程自适应变工况运行。这种泵在降低制造成本和方便用户安装使用方面也具有明显优势，其进出管角度可变的特点方便用户安装，还可以使离心泵的型系规格大为减少。其叶轮速度可达 20米 /秒左右，当流道当量直径加大时叶轮速度还可以提髙。增加多级泵的级数可以达到很高的扬程，或者进一步提高棼率。经数学规划的模块可以降低用户的总拥有成本。参照图 45，图中给出了模块化组合超减摩预旋闭式均速髙势比叶轮向心增压模块和对称端盖的多级离心泵结构。其中， 411是预旋器， 412是前端盖及其入管和中心蜗道， 413 是叶轮腔盖， 414是均速髙势比闭式叶轮， 415是带外壳的向心导轮， 416是叶轮前端腔阻气间隙， 417 是减摩驱动二相流入管， 418 是延伸包覆转移段流道截面叶轮腔部分的叶轮盖板， 419是后端腔减摩驱动介质入管， 420是后端盖及其出管和中心蜗道。本实例为对称盖变角出管超减摩闭式均速高势比叶轮向心增压多级离心泵，包含最多为 64个的多个超减摩预旋闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由带有延伸包覆转移段流道的叶轮盖 418的闭式均速高势比叶轮 414、预旋器 411、叶轮腔盖 413、向心导轮 415及阻气间隙 416、前端腔减摩驱动二相流入管 417、后端腔减摩驱动介质入管 419组成，后者分别用作前盖 412和后盖 420，通过轴系及紧固件连接组合。其中，阻气间隙 416、二相流入管 417是前端腔超减摩驱动部件，后端腔减摩驱动介质入管 419单独输入二相流或气体驱动后端腔减摩。 Variable angle outlet tube anti-friction pre-spinning high potential ratio centripetal booster multistage pump is a new type of centrifugal pump. It uses a modular combination design method to combine three symmetrical end caps, high potential ratio impellers, and centrifugal guide wheels. Big new component technology. Its potential-to-motion ratio is as high as 3 to 9, the stage pressure coefficient is close to the theoretical value, and the stage diversion loss is reduced by an order of magnitude. The combined anti-friction device can reduce the disc friction loss by 82% ~ 95%, which can further improve the efficiency. The combined pre-spinner completely eliminates the impact of turbulence and cavitation in the impeller inlet area, and enables the entire process to adapt to variable operating conditions. This pump also has obvious advantages in reducing manufacturing costs and facilitating installation and use by users. The variable inlet and outlet pipe angles are convenient for users to install, and the type specifications of centrifugal pumps can be greatly reduced. The impeller speed can reach about 20 meters per second, and the impeller speed can be increased when the equivalent diameter of the runner is increased. Increasing the number of stages of the multi-stage pump can achieve very high heads, or further increase the pumping rate. Mathematically planned modules can reduce the total cost of ownership for users. Referring to FIG. 45, a multi-stage centrifugal pump structure with a modular combination of over-friction, pre-spinning, closed-velocity average potential ratio impeller centrifugal booster module and symmetrical end cover is shown. Among them, 411 is a pre-rotator, 412 is a front end cover and its inlet tube and a central volute, 413 is an impeller cavity cover, 414 is an average speed closed potential impeller, 415 is a centripetal guide wheel with a casing, and 416 is an impeller Front-end cavity air-blocking gap, 417 is the anti-friction driving two-phase inflow tube, 418 is the impeller cover plate that covers the impeller cavity part of the runner section of the transfer section, 419 is the rear-end cavity anti-friction driving medium inlet tube, and 420 is the rear end cover With its outlet tube and central worm. This example is a centrifugal multistage centrifugal pump with centrifugal pump with centrifugal pump for super-reduced friction and closed closed-velocity high-potential ratio impeller with symmetrical cover and variable angle outlet pipe. Centrifugal booster module and 2 variable-angle outlet pipe symmetrical end cover modules. The former consists of a closed average speed high potential ratio impeller 414, a pre-rotator 411, and an impeller cavity with an impeller cover 418 that extends and covers the flow passage of the transfer section. The cover 413, the centripetal guide wheel 415 and the choke gap 416, the front-end cavity anti-friction driving two-phase inflow tube 417, and the rear-end cavity anti-friction driving medium inlet tube 419 are respectively used as the front cover 412 and the rear cover 420. Shaft system and fastener connection combination. Among them, the gas blocking gap 416 and the two-phase inflow pipe 417 are front-end cavity super-friction driving components, and the rear-end cavity anti-friction driving medium inlet pipe 419 is separately input to the two-phase flow or gas-driven rear-end cavity anti-friction.

变角出管超减摩预旋闭式高势比向心增压多级泵是一种新型离心泵，釆用模块化组合设计方法组合了对称端盖、高势比叶轮、向心导轮三大新型部件技术，其势动比高达 3〜9，级压力系数接近理论值，级导流损耗降低一个数量级。配置超减摩技术解决轮盘摩擦问题并降低转移段流道摩擦损耗，使轮盘摩擦损耗减小 82%〜95 %，使转移段流道损耗大幅度减小，可以进一步地提高效率。组合预旋器完全消除叶轮入口区的撞击湍流和气蚀问题，使全流程自适应变工况运行。这种泵在降低制造成本和方便用户安装使用方面也具有明显优势，其进出管角度可变的特点方便用户安装，还可以使离心泵的型系规格大为减少。其叶轮速度可达 20米 /秒左右，当流道当量直径加大时叶轮速度还可以提高。增加多级泵的级数可以达到很高的扬程，或者进一步提高效率。经数学规划的模块可以降低用户的总拥有成本。参照图 46，图中给出了模块化组合预旋双半开式向心增压模块和对称端盖模块的多级离心泵结构。其中， 421是前盖中心蜗道， 422是前端盖及其入管， 423是叶轮腔盖， 424 是半开式均速高势比叶轮， 425是带外壳的半开式向心导轮， 426是叶轮流道加速段， 427 是向心导轮增压流道， 428是径向籴流预旋器， 429是后端盖及其出管， 430是旋转曲面转向轴套。 Variable angle outlet pipe super friction reducing pre-spinning high potential ratio centrifugal booster multistage pump is a new type of centrifugal pump. The modular combination design method is used to combine symmetrical end caps, high potential ratio impellers and centripetal guide wheels. The three new component technologies have a potential-to-moment ratio of 3 to 9, a stage pressure coefficient close to the theoretical value, and stage diversion losses are reduced by an order of magnitude. Equipped with super friction reduction technology to solve the friction problem of the disk and reduce the friction loss of the flow channel in the transfer section, reducing the friction loss of the disk by 82% ~ 95%, greatly reducing the flow channel loss in the transfer section, which can further improve the efficiency. The combined pre-spinner completely eliminates the impact of turbulence and cavitation in the impeller inlet area, and enables the entire process to adapt to variable operating conditions. This pump also has obvious advantages in reducing manufacturing costs and facilitating installation and use by users. The variable inlet and outlet pipe angles are convenient for users to install, and the type specifications of centrifugal pumps can be greatly reduced. The impeller speed can reach about 20 meters per second, and the impeller speed can be increased when the equivalent diameter of the runner is increased. Increasing the number of stages of a multi-stage pump can achieve very high heads or further increase efficiency. Mathematically planned modules can reduce the total cost of ownership for users. Referring to FIG. 46, a multi-stage centrifugal pump structure with a modular combination of a pre-spinning double semi-open centripetal booster module and a symmetrical end cover module is shown. Among them, 421 is the central volute of the front cover, 422 is the front end cover and its inlet tube, 423 is the impeller cavity cover, 424 is a semi-open type average speed high potential ratio impeller, 425 is a semi-open centripetal guide wheel with a housing, 426 Is the impeller flow path acceleration section, 427 is the centrifugal guide wheel pressurized flow path, 428 is the radial flow pre-rotator, 429 is the rear end cover and its outlet pipe, and 430 is the rotating curved steering sleeve.

本实例为对称盖变角出管半开式叶轮向心增压多级离心泵，包含最多为 64个的多个预旋双半幵式均速高势比叶导轮向心增压模块和 2个变角度出管对称端盖模块，前者由半幵式均速髙势比叶轮 424、叶轮腔盖 423、半开式向心导轮 425和预旋器 428组成，后者分别用作前盖 422和后盖 429，通过轴系及紧固件连接组合。其中，预旋器可以釆用轴向来流的，装在叶轮吸入室中，或者改用径向来流预旋器，装在导轮中心（首级或者不改，或者缺省，末级可以缺省）。变角出管预旋双半开式向心增压多级泵采用预旋均速高势比双半开式轮模块作为赋能模块。该模块的半开式导轮只有环状大开口的后盖板，与圆环柱形外壳成一个整体，叶片紧固于后盖板上或者整体制^，后盖板开口，形成一个直径与叶轮入口相同的空腔，作为穿轴、吸入和安装预旋器的空间，导轮及其外壳与转轴同心地安装，其前盖板共用叶轮后盖轮盘底面。径向来流预旋器自带轴套，紧配合于转轴上，居于导轮中的空腔位置。半开式叶轮只有单边的后盖轮盘，叶片紧固于其上或者整体制造，叶轮通过轴套紧固在轴上。叶轮腔前盖通过导轮外壳定位安装在叶轮腔前侧。逐级串联装配双半开式向心增压模块，末级不装预旋器。配上前盖板和后盖模块，即完成组装。 This example is a centrifugal multi-stage centrifugal pump with centrifugal pump with centrifugal pressure and a semi-open impeller with symmetrical cover and variable angle outlet tube. Two variable-angle exit-tube symmetrical end-cap modules, the former consists of a half-shaft type uniform velocity pseudo-potential ratio impeller 424, an impeller cavity cover 423, a semi-open centripetal guide wheel 425, and a pre-spinner 428, the latter being used as The cover 422 and the rear cover 429 are connected and combined through a shaft system and a fastener. Among them, the pre-rotator can be used in the axial direction and installed in the suction chamber of the impeller, or the pre-rotator can be installed in the radial direction and installed in the center of the guide wheel (first stage or not changed, or default, the final stage can be (Default). The variable angle outlet pipe pre-spinning double semi-open centrifugal booster multistage pump adopts a pre-spinning average speed high-potential ratio double semi-opening wheel module as an enabling module. The semi-open guide wheel of this module has only a ring-shaped large back cover, which is integrated with the circular cylindrical shell, and the blades are fastened to the rear cover or made integrally. The rear cover is opened to form a diameter and The same cavity at the entrance of the impeller is used as the space for passing the shaft, sucking in and installing the pre-spinner. The guide wheel and its shell are concentrically installed with the rotating shaft. The front cover shares the impeller. Underside of the rear cover wheel. The radial inflow pre-spinner has its own sleeve, which fits tightly on the rotating shaft and is located in the cavity position in the guide wheel. The semi-open impeller only has a single-sided back cover wheel disc, and the blades are fastened on it or manufactured integrally. The impeller is fastened to the shaft through a shaft sleeve. The front cover of the impeller cavity is positioned and installed on the front side of the impeller cavity through a guide shell. The double semi-open centripetal booster module is assembled in series in stages, and the pre-rotator is not installed in the final stage. With the front cover and back cover modules, the assembly is complete.

上述双半开式多级方案是一种简易结构的均速高势比多级离心泵。其叶轮流道与导轮流道间共用叶轮后盖板作为转动的分隔结构，导轮流道与下一级叶轮流道间共用导轮后盖板作为静止的分隔结构，泵的轴向尺寸得以减小，却不产生显著的换向局部阻力损耗。 The above-mentioned double semi-open multi-stage solution is a simple structure of a multi-stage centrifugal pump with a uniform speed and high potential ratio. The impeller flow path and the guide wheel flow path share the impeller back cover as a rotating separation structure, and the guide wheel flow path and the next stage impeller flow path share the guide wheel back cover as a static separation structure. The axial size of the pump can be reduced. Is small, but does not produce significant commutation local resistance losses.

双半开式多级泵的叶轮没有端腔，无需减摩机构。由于导轮流道液流的圆周速度分量，叶轮后盖板的轮盘摩擦速度被减小一半左右，其摩擦损耗大约能减少 75 %。并且，这种摩擦还会对导流流道中的液流生成动量矩增量，从而产生叶轮外侧比功。叶轮前盖板的轮盘摩擦则与现有技术等量，考虑后盖摩擦的减少及其外侧比功的收益，其总的轮盘摩擦损失较之现有技术大约减少 40%左右。变角出管预旋双半开式向心增压多级泵是一种新型离心泵，釆用模块化组合设计方法组合了对称端盖、高势比叶轮、向心导轮三大新型部件技术。其势动比高达 3〜9，级压力系数接近理论值，级导流损耗降低一个数量级。组合预旋器完全消除 n†轮入口区的撞击湍流和气蚀问题，使全流程自适应变工况运行，其效率大幅度提高。这种泵在降低制造成本和方便用户安装使用方面也具有明显优势。其进出管角度可变的特点方便用户安装，还可以使离心泵的型系规格大为减少。其叶轮速度可达 20米 /秒左右，当流道当量直径加大时叶轮速度还可以提高。增加多级泵的级数可以达到很高的扬程，或者进一步提高效率。 The impeller of the double semi-open multistage pump has no end cavity and no friction reducing mechanism is needed. Due to the peripheral velocity component of the guide runner fluid flow, the disc friction speed of the rear cover of the impeller is reduced by about half, and its friction loss can be reduced by about 75%. In addition, this friction also generates a momentum moment increase for the liquid flow in the diversion channel, thereby generating the specific work on the outside of the impeller. The disc friction of the front cover of the impeller is equal to that of the prior art. Considering the reduction of the back cover friction and the benefits of the specific work on the outside, the total disc friction loss is reduced by about 40% compared with the prior art. The variable angle outlet pipe pre-spinning double semi-open centrifugal booster multistage pump is a new type of centrifugal pump. It uses a modular combination design method to combine three new components: a symmetrical end cap, a high potential ratio impeller, and a centrifugal guide wheel. technology. Its potential-to-motion ratio is as high as 3-9, the stage pressure coefficient is close to the theoretical value, and the stage conduction loss is reduced by an order of magnitude. The combined pre-spinner completely eliminates the impact of turbulence and cavitation in the entrance area of the n † wheel, making the whole process adaptively change the operating conditions, and its efficiency is greatly improved. This pump also has obvious advantages in reducing manufacturing costs and facilitating installation and use by users. Its variable inlet and outlet pipe features are convenient for users to install, and can also reduce the size of the centrifugal pump. The impeller speed can reach about 20 meters per second. When the equivalent diameter of the runner increases, the impeller speed can also increase. Increasing the number of stages of a multi-stage pump can achieve very high heads or further increase efficiency.

变角出管预旋双半开式向心增压多级泵的主要优势在于结构简单和制造成本较低。叶轮和导轮都用两合模成型工艺制造，其模具和加工成本都比较低。节省叶轮前盖板和轴向尺寸减小都是降低成本的重要因素。较之本发明的其他方案，双半开式方案的效率大约降低 2〜3 %，但其成本却是最低的。工业实用性 The main advantages of the variable angle outlet pipe pre-spinning double semi-open centrifugal booster multistage pump are simple structure and low manufacturing cost. Both the impeller and the guide wheel are manufactured by a two-clamp molding process, and their mold and processing costs are relatively low. Saving the impeller front cover and reducing the axial size are important factors in reducing costs. Compared with other schemes of the present invention, the efficiency of the double half-open scheme is reduced by about 2 to 3%, but its cost is the lowest. Industrial applicability

本发明公开的高势比叶轮能大幅度降低入导速度，同时消除大部分的叶轮损耗，具有使全程水力损耗降低一个数量级的潜力。并且，这种叶轮还具有特别实用的变工况适应性。这些因素使得实际压力系数损失大为减小，泵效率等主要性能参数大幅度改善。 The high-potential-ratio impeller disclosed by the present invention can greatly reduce the conduction speed, and at the same time eliminates most of the impeller losses, and has the potential to reduce the entire hydraulic loss by an order of magnitude. In addition, this impeller has particularly practical adaptability to changing conditions. These factors greatly reduce the actual pressure coefficient loss, and greatly improve the main performance parameters such as pump efficiency.

本发明公开的内减摩技术使离心泵的内机械损耗降低一个数量级，使总效率提高 5〜7 个百分点。 The internal friction reducing technology disclosed in the present invention reduces the internal mechanical loss of the centrifugal pump by an order of magnitude and improves the overall efficiency by 5 to 7 percentage points.

本发明的向心增压导流器和变角度出管对称端盖设计使泵的体积大为减小，在降低制造成本和提高使用方便度等方面具有突出的效果。变角度出管的功能在应用中可以满足难以预料的用户临场需要，可以节约场地和管道，可以减少弯头和提高管路效率。向心导轮和对称端盖可以用于现有技术离心泵的结构改造。其向心增压、变角度出管和体积大幅度减小等功能，均为突出的实质性特点和显著的进步。基于向心导轮和对称端盖的优势设计的模块化组合离心泵的方法，可以组合出许多种新型的离心泵。 The design of the centripetal pressure-increasing deflector and the variable-angle outlet pipe symmetrical end cap of the present invention greatly reduces the volume of the pump, and has prominent effects in reducing the manufacturing cost and improving the convenience of use. The function of variable angle outlet pipe can meet the unpredictable user's on-site needs in the application, can save space and pipes, can reduce elbows and improve pipeline efficiency. The centrifugal guide wheel and the symmetrical end cover can be used for the structural modification of the prior art centrifugal pump. Its functions such as centripetal pressurization, variable angle outlet pipe, and substantial reduction in volume are all outstanding substantive features and significant progress. Based on the advantages of centrifugal guide wheels and symmetrical end caps, the modular combination centrifugal pump method can combine many new types of centrifugal pumps.

当釆用模成型等现代制造工艺来实施本发明时，能大幅度提髙生产效率和降低生产成本，这是本发明的另一实用性优势。 When the present invention is implemented using a modern manufacturing process such as molding, it can greatly improve production efficiency and reduce production costs, which is another practical advantage of the present invention.

很高的运行效率、较小的体积、方便安装的管道连接适应性、扬程和流量改变时运行的高效性和稳定性等变工况适应性、气蚀特性的改善使产品寿命延长、以及适合于模成型工艺批量生产的结构和零部件设计等，体现了本发明良好的工业实用性。【定义】绝对速度——离心泵中流体质点相对于静止机壳的运动速度。 High operating efficiency, small size, easy to install pipe connection adaptability, high efficiency and stability of operation when head and flow rate are changed, adaptability to changing conditions, improved cavitation characteristics to extend product life, and suitable for The structure and component design for mass production of the molding process reflect the good industrial applicability of the present invention. [Definition] Absolute speed-the moving speed of the fluid particle in the centrifugal pump relative to the stationary casing.

相对速度——离心泵中流体质点相对于旋转叶轮的运动速度。 Relative speed-the speed of the fluid particle in the centrifugal pump relative to the rotating impeller.

牵连速度——离心泵中驱动流体运动的叶轮相对于静止机壳的运动速度。 Implication speed-the speed of the impeller driving fluid movement in the centrifugal pump relative to the stationary casing.

同步速度——离心泵流道中，圆周向分速度等于相同径向坐标处牵连速度的液流速度。比功——离心泵叶轮对流经叶槽的单位质量的流体所做的功。 Synchronous speed-the speed of the liquid flow in the centrifugal pump channel where the circumferential partial velocity is equal to the implication velocity at the same radial coordinate. Specific work—the work done by a centrifugal pump impeller on a unit of mass of fluid flowing through the bucket.

比能——单位质量的流体所具有的机械能，区别势能和动能时分称比势能和比动能。势扬程——流体在叶轮流道中所获压力增量与重力加速度之比，压力增量等于单位质量的流体所接受的离心力功与其自身相对运动动能减量的代数和。 Specific energy——The mechanical energy possessed by a unit mass of fluid. The difference between potential energy and kinetic energy is called specific potential energy and specific kinetic energy. Potential lift—the ratio of the pressure increase obtained by the fluid in the impeller flow path to the acceleration of gravity. The pressure increase is equal to the algebraic sum of the centrifugal force work and the relative kinetic energy reduction of the unit mass of fluid.

动扬程——单位质量的流体在叶轮流道中所获动能增量与重力加速度之比，该增量在导流器中完成压头转换，按静止坐标系中的绝对速度计算。 Dynamic head—the ratio of the increase in kinetic energy to the acceleration of gravity in the impeller flow channel per unit mass of fluid. This increment completes the conversion of the head in the deflector and is calculated as the absolute speed in the stationary coordinate system.

势动比——叶轮输出势扬程与输出动扬程之比，简称势比。 Potential ratio: The ratio of the impeller output potential head to the output dynamic head, referred to as the potential ratio.

反作用度——叶轮输出比势能与输送比功之比，与势动比互为单调增函数。 Reaction degree—the ratio of the impeller output specific potential energy to the specific power of the transmission, which is a monotonic increasing function with the potential ratio.

压力系数——叶轮输送的有效比功与依据叶轮圆周速度计算的比动能之比。 Pressure coefficient-The ratio of the effective specific work delivered by the impeller to the specific kinetic energy calculated from the impeller's peripheral speed.

比转数——输送单位比功和单位体积流量的几何相似单元叶轮的转速，又称相似性系数。相对涡旋——离心泵叶轮流道中流体相对于旋转坐标系的圆周面反向涡旋运动，是有限叶片弱剪切约束下的一种流体惯性运动形态，对相对速度场之分布有重大影响。局部激励——不可压縮流体在非约束方向受到作用面较小的冲量作用，在作用面邻域内发生非势流运动，例如以石击水、瀑布流、搅拌和液流截面陡扩等。 Specific number of revolutions—the rotational speed of a geometrically similar unit impeller conveying unit specific work and unit volume flow, also known as similarity coefficient. Relative vortex—the reverse vortex motion of the fluid in the flow path of the centrifugal pump impeller relative to the circumferential surface of the rotating coordinate system is a fluid inertial motion under the constraint of weak shear of the blade, which has a significant impact on the distribution of the relative velocity field . Local excitation—Incompressible fluid is subjected to a small impulse on the active surface in the unconstrained direction, and non-potential flow movements occur in the vicinity of the active surface, such as stone hitting water, waterfall flow, agitation, and steep expansion of liquid flow cross section.

完备约束——无局部激励可能性的流体约束，例如，具有自由或弱约束边界的不可压缩流体，其可能的作用面及前向邻域被与该作用面正交的刚性壁面所包围。附壁效应——当压力和壁面曲率合适时，一定流速的不可压缩流体贴附壁面流动，其不脱流条件为壁面绝对压力大于饱和气压。 Complete Constraints—Fluid constraints without the possibility of local excitation. For example, incompressible fluids with free or weakly constrained boundaries, their possible active surfaces and forward neighborhoods are surrounded by rigid wall surfaces orthogonal to the active surface. Coanda effect—When pressure and wall curvature are appropriate, incompressible fluid with a certain flow rate adheres to the wall surface, and its non-draining condition is that the absolute pressure on the wall surface is greater than the saturated air pressure.

高势比叶轮种高势动比输出的离心泵叶轮，其流道是完备约束的，具有流速低、抗相对涡旋、无回流和脱流、圆周柱面等速等压、动能反馈线性节流诸特性。反馈减速比——高势比叶轮反切向出口相对速度与叶轮圆周速度之比，又称反馈减功系数，叶轮比功和出口绝对速度均为其线性减函数。 Centrifugal pump impeller with high potential ratio and high potential-to-dynamic ratio output, its flow channel is fully constrained, with low flow rate, anti-relative vortex, no backflow and outflow, constant velocity and constant pressure on the circular cylindrical surface, kinetic energy feedback linear section Flowing characteristics. Feedback reduction ratio——The ratio of the relative velocity of the impeller in the tangential outlet of the high potential ratio to the peripheral speed of the impeller, also known as the feedback reduction coefficient. The specific work of the impeller and the absolute speed of the impeller are both linear reduction functions.

自适应预旋器——装有变迎角弹性流道的同轴预旋器，用于来流预旋和级联速度场整理。均速岔道——高势比叶轮的一种叶槽分叉结构，主要通过岔道出口面积的不均匀分配抗性遏制相对涡旋，使叶槽速度分布均匀化和低速层流化。 Adaptive pre-spinner-Coaxial pre-spinner equipped with variable angle of attack elastic flow channel for incoming pre-spin and cascade velocity field finishing. Uniform speed bifurcation-a bifurcated bifurcation structure of a high potential ratio impeller, which mainly suppresses relative vortices through the uneven distribution of the resistance at the exit area of the bifurcation, and makes the velocity distribution of the trough uniform and low-speed laminarization.

内减摩种提髙离心泵内机械效率的方法及设计，在叶轮端面与腔壁间动态充盈气相介质，其粘滞系数和比摩阻较液相介质减小两个数量级，简称减摩。 Internal friction reduction A method and design for improving the mechanical efficiency in a centrifugal pump. Dynamically filling the gas phase medium between the impeller end face and the cavity wall, its viscosity coefficient and specific friction are reduced by two orders of magnitude compared to liquid medium, referred to as friction reduction.

保守环量设计种保守液流动量矩惯性的离心泵流场设计，要求在叶轮连接流道中保持速度环量的连续性，包括同步正预旋和轴面换向带环量入导。向心导轮- -一种保守环量设计的内向涡旋型导流器，其增压流道完备约束，并按优化扩张率渐增截面积和渐减中线曲率半径，具有体积小、效率高的特点。 Conservative loop design This kind of centrifugal pump flow field design with conserved liquid flow moment and inertia requires the continuity of the velocity loop in the impeller connection channel, including synchronous positive pre-spinning and axial surface reversal with ring loop input guide. Centripetal guide wheel-An inward scroll type deflector with a conservative loop design. The booster flow path is fully constrained, and the cross-sectional area is gradually increased and the radius of curvature of the center line is gradually reduced according to the optimized expansion rate. It has a small volume and efficiency. High characteristics.

向心增压——向心导轮之压力分布特征，其流道压力随中线极半径的减小而单调增加。转移流道——叶轮出口与向心导轮增压流道间的液流通道，由叶轮腔壁之外沿曲面围成。超减摩种提髙内减摩向心增压离心泵导流效率的方法及设计，将叶轮前盖延伸并包含转移段流道的叶轮腔部分，前端腔减摩作用区也因而延伸到该部分。 Concentric pressurization——The pressure distribution characteristic of the concentric guide wheel. The pressure of the flow channel increases monotonously with the decrease of the centerline pole radius. Transfer channel—The liquid flow channel between the impeller outlet and the centrifugal guide wheel pressurized channel is surrounded by the curved surface outside the impeller cavity wall. The method and design of the super-anti-friction centrifugal centrifugal centrifugal centrifugal booster centrifugal pump to improve the flow efficiency of the centrifugal pump. The front cover of the impeller is extended to include the impeller cavity part of the flow channel of the transfer section. section.

对称端盖种前后通用、单多级通用的离心泵端盖，盖上有轴承座和分汇流中心蜗道及其吻接管道，装配时转动前后端盖可分别改变入出管角度。 Symmetrical end caps are universal front and rear, single and multi-stage universal centrifugal pump end caps, which are covered with bearing housings, sub-convergence center volutes, and their kissing pipes. The front and rear end caps can be rotated to change the inlet and outlet angles during assembly.

向心增压模块种主要由叶轮和向心导轮轴向组合的离心泵赋能增压单元，具有标准化的接口参数和装配尺寸，单多级通用，其互换性覆盖设计、生产和使用过程。模块化组合种用向心增压模块和对称端盖模块跨型号组合单级和多级离心泵的方法，各模块间釆用 "液流从近轴环形口带环量流入和流出" 的连接模式。二次型蜗道——由定长轴长半椭圆和定弦长大弓形两种截面段吻接而成的离心泵蜗道，其截面积为圆心角的二次型函数，能优化摩擦面和流场梯度，损耗较小。 The centrifugal booster module is mainly powered by a centrifugal pump with an axial combination of an impeller and a centrifugal guide wheel. It has standardized interface parameters and assembly dimensions, and is single and multi-stage universal. Its interchangeability covers the design, production and use processes. . Modular combination: A method of combining single-stage and multi-stage centrifugal pumps with a centripetal booster module and a symmetrical end cover module across models. The connection between each module is "liquid flow from the paraxial annular port with the inflow and outflow." mode. Quadratic worm trajectory-a centrifugal pump worm trajectory made up of two cross sections of a fixed-length semi-ellipse and a fixed-chord long bow. The cross-sectional area is a quadratic function of the center angle, which can optimize the friction surface and The flow field gradient, the loss is small.

梯形槽导环——截面为等腰梯形的离心泵导环，用作叶轮与蜗道间的过渡导流器，可避免局部激励，其入口和出口宽度分别等于叶轮出口和蜗道入口宽度。 Trapezoidal groove guide ring—a centrifugal pump guide ring with an isosceles trapezoidal cross-section, used as a transitional deflector between the impeller and the volute, to avoid local excitation, and its inlet and outlet widths are equal to the width of the impeller outlet and the worm inlet, respectively.

Claims

权利要求 Rights request

1、一种离心泵，由叶轮、导流器、机壳和轴系部件组成，其特征是：叶轮的叶槽流道尾部朝反切向弯曲并且截面积逐渐减小，流体在离心力做功的路径末端被加速和改变方向，最后以较大的相对速度和接近于 0的出口角流出叶轮，出口绝对速度相应减小，转向和加速过程产生的反作用力矩使转轴减功。 1. A centrifugal pump, consisting of an impeller, a deflector, a casing, and a shaft system component, which is characterized in that: the tail of the impeller's grooved channel is bent in the tangential direction and the cross-sectional area is gradually reduced; the path of the fluid doing work under centrifugal force The end is accelerated and changed direction, and finally flows out of the impeller at a relatively large relative speed and an exit angle close to 0. The absolute speed of the exit is correspondingly reduced. The reaction torque generated during the steering and acceleration processes reduces the work of the shaft.

2、一种离心泵，由叶轮、导流器、机壳和轴系部件组成，其特征是：闭式叶轮轮盘的前后端腔或半开式叶轮的后端腔置于气体循环或气液二相流循环流程中，端腔充盈不溶性气体，叶轮轮盘在气相介质中旋转，端腔气压在循环中动态地保持与端腔边沿旋转液流表面压力的平衡，并且等于或小于叶轮出口静压力。 2. A centrifugal pump is composed of an impeller, a deflector, a casing, and a shaft system component, and is characterized by: the front and rear cavity of the closed impeller disc or the rear cavity of the semi-open impeller is placed in a gas circulation or gas In the liquid two-phase flow circulation process, the end cavity is filled with insoluble gas, the impeller disk rotates in the gas phase medium, and the end cavity pressure dynamically maintains a balance with the surface pressure of the rotating liquid flow along the edge of the end cavity during the circulation, and is equal to or less than the impeller outlet Static pressure.

3、一种离心泵，由叶轮、导流器、机壳和轴系部件组成，其特征是：导流器为向心导轮，流道呈内向涡旋形，曲率半径逐渐减小而截面积渐扩，汇合于中心环腔转 90度轴向输出。 3. A centrifugal pump is composed of an impeller, a deflector, a casing, and a shaft system component, and is characterized in that: the deflector is a centrifugal guide wheel, the flow path is inwardly swirling, the radius of curvature is gradually reduced and cut off. The area gradually expands, converges in the central ring cavity and rotates 90 degrees to output axially.

4、一种离心泵模块化组合方法，不同型号规格的离心泵使用相同规格的赋能零部件，其特征是：基于向心导轮的空间周期性，据以构造带环量近轴环形口连接的叶导轮轴向组合向心增压模块，基于对称端盖的结构特性，将其作为带环量近轴环形口连接的端封结构模块，在两种模块的互相对应的规格系列中，同一种父规格的模块装配尺寸和基本接口参数相同而具有査表检验互换性，父规格下的同一种子规格的模块装配尺寸和所有接口参数相同而具有完全互换性，两种互换性定义在单级泵、多级泵、各种型号和不同内含技术包括使用髙势比或常势比叶轮的离心泵的大集合上，在规划和设计过程中定义互换性域，在设计之后的生产过程中和在生产之后的使用过程中互换性在定义域内成立，按照 "液流从近轴环形口带环量流入和流出" 的连接模式，将 1个或最多 64个串联的多个向心增压模块与 2个对称端盖模块组合，即构成模块化组合单级泵或多级泵。 4. A modular combination method of centrifugal pumps. Centrifugal pumps of different models and specifications use the same specifications of energized components, which are characterized by: based on the spatial periodicity of the centrifugal guide wheel, based on which a paraxial annular port with a ring quantity is constructed. The axially connected centrifugal booster module of the connected impeller is based on the structural characteristics of the symmetric end cap, and it is used as an end seal structural module with a ring-shaped paraxial ring mouth connection. In the corresponding specifications of the two modules, The assembly dimensions and basic interface parameters of the same parent specification are the same and have a look-up table to check the interchangeability. The module assembly dimensions of the same seed specification under the parent specification are the same as all interface parameters and are completely interchangeable. Two interchangeability definitions On a large set of single-stage pumps, multi-stage pumps, various models and different built-in technologies, including centrifugal pumps using pseudopotential ratio or constant potential ratio impellers, the interchangeability domain is defined during the planning and design process. After the design, In the production process and in the use process after production, the interchangeability is established within the definition domain, according to the connection of "liquid flow from the paraxial annular mouth with the inflow and outflow". In the connection mode, one or up to 64 concentric booster modules in series and two symmetrical end cap modules are combined to form a modular combination single-stage or multi-stage pump.

5、依据权利要求 1 所述的离心泵，，其特征是：叶轮流道出口为矩形或圆形，相邻出口之间的角距离等于 360度除以流道数，出口法面与流道垂直，前一出口内侧边到后一出口外侧边之间的连接为光滑的渐开弧线柱面或由深到浅的槽面，柱面或槽面与叶轮圆周柱面之间的单边约束流道截面积与圆心角成周期性线性关系，相离分布的出口流束经弧线柱面或槽面的附壁效应整理，在轮沿之出口间隔区形成向内弯曲的均布流线，流速的径向分量与切向分量不随圆心角改变，各流道出口面积之和等于设计体积流量与设计出口相对速度之比，该速度等于叶轮圆周速度与反馈减速比 K的乘积。 5. The centrifugal pump according to claim 1, wherein the outlet of the impeller flow channel is rectangular or circular, and the angular distance between adjacent outlets is equal to 360 degrees divided by the number of flow channels, and the normal surface of the outlet and the flow channel Vertical, the connection between the inner side of the previous exit to the outer side of the next exit is a smooth involute arc cylinder surface or a groove surface from deep to shallow, between the cylinder surface or the groove surface and the impeller circumferential cylinder surface The cross-sectional area of the unilaterally constrained flow channel has a periodic linear relationship with the center angle. The separated exit flow bundles are arranged by the Coanda effect of the arc cylinder or the groove surface, and an inwardly curved uniformity is formed in the exit interval of the wheel rim. The distribution line, the radial and tangential components of the flow velocity do not change with the center angle. The sum of the outlet area of each flow channel is equal to the ratio of the design volume flow rate and the design outlet relative speed. The speed is equal to the product of the impeller peripheral speed and the feedback reduction ratio K. .

6、依据权利要求 5所述的离心泵，其特征是：叶轮叶片呈 L形，其前中部分别为直线段，呈径向走势，其肘部和尾部经恰当曲率半径过渡朝反切向弯曲，尾部具有隔离内外压差的机械强度和尖锐的末端，恰当曲率半径过渡包括内外两侧的造形变化，尾部内侧作为加速段外侧约束边与叶片肘部之间的距离满足流道加速段截面变化要求，尾部外侧满足附壁效应整理的走向角变化要求，肘部外侧曲率半径满足不脱流条件。 6. The centrifugal pump according to claim 5, characterized in that: the impeller blades are L-shaped, the front and middle portions are respectively straight line segments, and they move in a radial direction; The tail has mechanical strength and sharp ends to isolate the internal and external pressure difference. The proper curvature radius transition includes the shaping changes on both the inside and outside. , The outside of the tail meets The change of strike angle required by the Coanda effect requires that the radius of curvature of the outside of the elbow meet the condition of no flow.

7、依据权利要求 1或 5或 6所述的离心泵，其特征是：叶轮吸入室或前级导流器出口装有一个与叶轮同轴旋转的轴向或径向来流自适应预旋器，预旋器由由弹性帆式叶片、轮圈和刚性肋条组成，其叶片数少于叶轮叶片数，叶片由复合材料制成，具有由前端到***逐渐增大的拉伸弹性系数，被径向固定于轮圈之等角度分布的装配位置上，轮圈自由地套在转轴或叶轮轴套上，叶片前端悬挂于入口处的刚性肋条上，叶片之间构成预旋流道，其中，轴向来流预旋器的刚性肋条布设于入口圆周面上的径向位置，径向来流预旋器的刚性肋条布设于入口圆柱面上与转轴平行的位置。 7. The centrifugal pump according to claim 1 or 5 or 6, characterized in that: the impeller suction chamber or the outlet of the fore-stage deflector is equipped with an axial or radial self-flow adaptive pre-rotator coaxially rotating with the impeller. The pre-spinner is composed of elastic sail blades, rims and rigid ribs. The number of blades is less than the number of blades of the impeller. The blades are made of composite material. It has a tensile elastic coefficient that gradually increases from the front end to the root. At the assembly position fixed at equal angular distribution on the rim, the rim is freely sleeved on the rotating shaft or the impeller sleeve, and the front end of the blade is suspended on a rigid rib at the entrance, and a pre-spinning flow channel is formed between the blades, wherein the shaft The rigid ribs of the forward flow pre-rotator are arranged at a radial position on the circumferential surface of the inlet, and the rigid ribs of the radial flow pre-rotator are arranged at a position parallel to the rotation axis on the cylindrical surface of the inlet.

8、依据权利要求 1或 5或 6所述的离心泵，其特征是：在叶轮叶槽中布设遏制相对涡旋的均速岔道，每个叶槽流道被 1〜3片均速梳叶纵向分割，形成 2〜4个岔道，岔道入口接近而未达到叶槽入口，其截面积均匀分配，岔道出口接近而未达叶槽出口，其截面积是依据所叠加的相对涡旋的动力分布及给定的速度分布确定的、或经试验优化的经验数据分配的。 8. The centrifugal pump according to claim 1 or 5 or 6, characterized in that: a uniform-speed bifurcation to curb relative vortex is arranged in the impeller impeller, and each of the impeller flow channels is combed by 1 to 3 blades of uniform velocity. It is divided longitudinally to form 2 to 4 branch roads. The branch road entrances are close to the leaf trough entrance, and their cross-sectional areas are evenly distributed. The branch road exits are close to the leaf trough exit. The cross-sectional area is based on the superimposed relative vortex dynamic distribution. And a given speed distribution or experimentally optimized empirical data allocation.

9、依据权利要求 2所述的离心泵，其特征是：包括给减摩端腔充气的射流器，射流器的驱动压力液体由泵之出口分流，其引射口通过调节阀接气源或通大气，其出口从静止壁面近轴处接入减摩端腔，二相流在腔中分离，气体被离心力场之向心浮力约束于腔中，液体和多余的气体从轮沿侧隙中排入导流器，前端腔通吸入室的泄漏间隙改成阻气间隙，或加装分离分流二相流的阻气 V形环槽，加装二相流润滑的软挡圈，或直接用压力液体封堵，叶轮出口处的腔壁母线或者还做成具有引射减压作用的形状使端腔压力降到出口静压力以下。 9. The centrifugal pump according to claim 2, comprising: a jet device for inflating the friction reducing end cavity, and the driving pressure liquid of the jet device is divided by the outlet of the pump, and its ejection port is connected to the air source through a regulating valve or Through the atmosphere, its outlet is connected to the anti-friction end cavity from the stationary wall near the axis. The two-phase flow is separated in the cavity. The gas is confined in the cavity by the centripetal buoyancy of the centrifugal force field. The liquid and excess gas pass from the side clearance of the wheel. Discharge into the deflector, change the leakage gap between the front end cavity and the suction chamber to a gas blocking gap, or install a gas blocking V-ring groove that separates the split two-phase flow, install a two-phase flow lubricated soft stop ring, or use it directly The pressure liquid is plugged, and the cavity wall generatrix at the impeller outlet is also made into a shape with ejective decompression effect to reduce the end cavity pressure to below the outlet static pressure.

10、依据权利要求 2所述的离心泵，其特征是：釆用压力罐装气体经减压阀降压和调节阀调节流量后，用管路连通到减摩端腔静止壁注入，并从泵出口分流一小流量液体，用管路直接注入机械密封腔及前端腔泄漏间隙，分别冷却轴封和封堵泄漏间隙，或者，将压力罐装气体经减压阀降压和调节陶调节流量后的气流直接注入泵之出口引出的回流管中构成二相流，分别连接到后端腔静止壁面和前端腔静止壁面近轴阻气间隙处，分别密封进入，气体和液体的流量分别调节，液体流量调节阀串联在引自泵出口的回流管中。 10. The centrifugal pump according to claim 2, characterized in that: (1) after the pressure is adjusted by the pressure reducing valve and the regulating valve to adjust the flow rate of the gas in the pressure tank, the pipeline is connected to the static wall of the anti-friction end cavity for injection, and A small flow of liquid is split at the pump outlet, and the pipeline is directly injected into the leakage gap of the mechanical seal cavity and the front end cavity to cool the shaft seal and seal the leakage gap, respectively. Alternatively, the pressure canned gas is depressurized by a pressure reducing valve and adjusted to adjust the flow rate. The subsequent airflow is directly injected into the return pipe leading from the outlet of the pump to form a two-phase flow, which is respectively connected to the rear wall static wall surface and the front cavity static wall surface near the axial gas-blocking gap, and is sealed in. The gas and liquid flows are adjusted separately. The liquid flow regulating valve is connected in series in the return pipe leading from the pump outlet.

11、依据权利要求 3所述的离心泵，其特征是：向心导轮流道转移段由叶轮出口柱面、叶轮腔前壁曲面和导轮前底面外沿曲面围成，其截面分为叶轮腔部分和导轮部分，两部分装配吻接合一，其合成截面的位置周期性地向导轮方向转移，其截面积随导流圆心角的增大而周期性地线性增大，其周期等于一个导流流道对应的圆心角，其增大比例系数等于叶轮转过单位角度的体积排量设计值与液流出口绝对速度设计值之比，或者还乘以一个大于 1而小于导轮增压流道最小扩张率的扩张系数。 11. The centrifugal pump according to claim 3, characterized in that: the centrifugal guide wheel flow passage transfer section is surrounded by the impeller exit cylindrical surface, the curved surface of the front wall of the impeller cavity and the curved surface of the front bottom surface of the guide wheel, and the cross section is divided into impellers The cavity part and the guide wheel part, the two parts are assembled and joined together. The position of the composite cross section is periodically shifted in the direction of the guide wheel, and its cross-sectional area increases linearly and periodically with the increase of the diversion center angle. The period is equal to one. The increase of the center angle corresponding to the diversion channel is equal to the ratio of the design value of the volumetric displacement of the impeller through a unit angle to the design value of the absolute velocity of the liquid outlet, or it is multiplied by a value greater than 1 and less than the pressure of the guide wheel The expansion coefficient of the minimum expansion rate of the flow channel.

12、依据权利要求 3所述的离心泵，其特征是：采用中心涡道汇流变角度出管对称端盖作前后轴向封装，'该端盖由带装配止口的承压盖板和与盖板一体化制造的中心结构及连通管道组成，其中心结构包括轴套、轴套***的中心蜗道、蜗道围护结构支撑的轴承腔和轴孔，承压盖板的承压面为平面或与向心导轮开口面吻合的旋转曲面，其近轴部位有一个与蜗道连通的环形开口，中心蜗道是一种径向渐幵轴向平移的三维蜗道，其始端是环形开口平面上的隔舌，其末端在增加了径向和轴向坐标的隔舌下方，蜗道截面积与圆心角成正比，比例系数等于叶轮转过单位角度的体积排量与液流平均速度之比，以开口圆平面为基准，随着截面积的线性增加，蜗道底部中心线的径向坐标和轴向坐标逐渐增加，形成一个蜗底斜坡，转过 360度后进入隔舌下方，随后与管道吻接，蜗道截面形状亦随圆心角改变，从隔舌直线段开始，首先为长轴在开口平面上的变短半轴长半椭圆，成为半圆后逐渐下沉并光滑地加大下部的曲率半径，沿一足以绕开轴承腔支承结构的曲率变化率适当的渐开弧线延伸，成为曲边四边形加半圆形状，直到进入隔舌下方，然后保持截面积地变形为圆截面与管道吻接。 12. The centrifugal pump according to claim 3, characterized in that: a symmetrical end cap with a central vortex confluent angle outlet pipe is used for front and rear axial packaging, and the end cap is composed of a pressure-containing cover plate with an assembly stop and a Central structure and connection The central structure includes a shaft sleeve, a central volute around the shaft sleeve, a bearing cavity and a shaft hole supported by the volute envelope structure, and the pressure bearing surface of the pressure-bearing cover plate is a flat surface or an open surface with a centripetal guide wheel. An anatomic rotating surface has a ring-shaped opening communicating with the worm in the paraxial part. The center worm is a three-dimensional worm that moves in a radial and gradually axial translation. The starting end is the tongue on the plane of the ring-shaped opening. Below the tongue with increased radial and axial coordinates, the cross-sectional area of the worm is proportional to the center angle, and the proportionality factor is equal to the ratio of the volume displacement of the impeller through a unit angle to the average speed of the liquid flow, based on the open circular plane. With the linear increase of the cross-sectional area, the radial and axial coordinates of the centerline of the bottom of the worm gradually increase, forming a worm bottom slope. After 360 degrees, it enters the lower part of the tongue and then meets the pipe. The worm section The shape also changes with the center angle. Starting from the straight segment of the tongue, the first is the shortened semi-axis and semi-ellipse with the long axis on the opening plane. After becoming a semi-circle, it gradually sinks and smoothly increases the radius of curvature of the lower part. A sufficient curvature change rate bypass chamber suitable bearing support structure extending involute arc, become plus tetragonal semicircular curved sides until the tongue enters below and deformed cross-sectional area to maintain a circular cross-section duct anastomosis.

13、依据权利要求 6所述的离心泵，其特征是：叶轮为一个带有轴孔（2)、轴套（3)、叶片（5 ) .和叶槽流道（6) 的半开式圆盘形零件，轴套外面是环形吸入室（4) ，其底面或者是使液流连续转向的旋转曲面，或者是平面，后者为备装预旋器型，预旋器轮圈表面有一造形相同的转向曲面，叶片（5) 为 L形，前中部呈径向走势，尾部朝反切向弯曲，尾部外侧为光滑的渐开弧线柱面或槽面， 6〜12片完全相同的 L形叶片在轮盘上均匀分布，其间形成均布的叶槽流道，流道入口（7) 和中部（6 ) 较为宽阔，在到达出口（8 )之前截面积逐渐减小并转向。 13. The centrifugal pump according to claim 6, characterized in that the impeller is a semi-open type with a shaft hole (2), a shaft sleeve (3), a blade (5), and a blade groove flow channel (6). Disk-shaped parts, the outside of the sleeve is a ring-shaped suction chamber (4), the bottom surface of which is either a rotating curved surface or a flat surface, the latter is equipped with pre-rotator type, the surface of the pre-rotator wheel has a The same turning curved surface is formed, the blade (5) is L-shaped, the front and middle part is in a radial direction, the tail is curved in the reverse tangential direction, and the outer side of the tail is a smooth involute arc cylinder or groove surface. 6 ~ 12 identical L The shaped blades are evenly distributed on the wheel disc, forming uniformly distributed channel flow channels. The flow channel inlet (7) and the middle (6) are relatively wide, and the cross-sectional area gradually decreases and turns before reaching the outlet (8).

14、依据权利要求 13所述的离心泵，其特征是：采用闭式叶轮，是在半幵式高势比叶轮的基础上加装前盖（10)封闭而成的，前盖板具有与半开式轮盘密配合的内表面和旋转曲面外表面，半开式基础结构每片 L形叶片之肘部宽阔处开有 2〜3个与轮盘垂直的铆钉孔或螺钉孔，盖板是用沉头或扁平头铆钉（9)铆紧或用螺钉防松紧固连接于轮盘上的，或者，前盖板采用点焊工艺与轮盘连接。 14. The centrifugal pump according to claim 13, characterized in that: a closed impeller is adopted and closed by adding a front cover (10) on the basis of a half-height high potential ratio impeller, and the front cover has The inner surface of the semi-open type disc is closely matched with the outer surface of the rotating curved surface, and the elbow of each L-shaped blade of the semi-open type foundation structure has 2 to 3 rivet holes or screw holes perpendicular to the disc, and a cover plate It is riveted with countersunk or flat head rivets (9) or screwed to prevent loosening and fastened to the wheel, or the front cover is connected to the wheel by spot welding.

16、依据权利要求 7所述的离心泵，其特征是：叶轮中装有轴向来流预旋器，由两节轮圈和片数少于叶轮的弹性帆式叶片组成，轮圈（14)和（15)滑套在叶轮吸入室轴套上，能各自独立转动，其表面互相吻接成使液流转向的旋转曲面，帆式叶片（16)成曲边三角形，其前沿直线边悬挂于刚性肋条（20)上，肋条径向固定在叶轮叶片或前盖入口处，叶片曲线边上与两轮圈之下底面接近的两点（18)和（19)分别固定在该两底面圆周上，当预旋器安装在半开式叶轮（31 )上时，刚性肋条（34)径向紧固在叶片根部之入口面上。 16. The centrifugal pump according to claim 7, characterized in that: the impeller is provided with an axial inflow pre-spinner, which is composed of two rims and elastic sail-type blades with a smaller number of blades than the impeller, and the rim (14 ) And (15) are sleeved on the impeller suction chamber shaft sleeve, which can rotate independently, and their surfaces kiss each other to form a rotating curved surface to turn the liquid flow. The sail blade (16) forms a curved edge triangle, and its leading edge is suspended on a straight line. On the rigid rib (20), the rib is fixed radially at the impeller blade or the front cover entrance, and two points (18) and (19) on the curved edge of the blade that are close to the bottom surface under the two rims are respectively fixed on the circumference of the bottom surfaces. When the pre-spinner is installed on the semi-open impeller (31), the rigid ribs (34) are radially fastened on the entrance surface of the blade root.

17、依据权利要求 7所述的离心泵，其特征是：径向来流预旋器由带轴套的圆盘形肋条支架及轴套（25) 、下轮圈（21 ) 、上轮圈（22)和数量少于等于叶轮叶片数的刚性肋条（23)及弹性帆式叶片（24)装配而成，叶片为曲边三角形，其前沿直线边悬挂于肋条上，肋条固定在支架上，支架轴套静配合在转轴上，叶片曲线边上与两轮圈之上底面接近的点（27) 、 (29)分别固定在该两底面圆周上，两轮圈滑套在支架轴套上，其表面互相吻接成使液流转向的旋转曲面。 17. The centrifugal pump according to claim 7, characterized in that the radial inflow pre-spinner is composed of a disc-shaped rib support with a sleeve, a sleeve (25), a lower rim (21), and an upper rim ( 22) Assembled with rigid ribs (23) and elastic sail blades (24), the number of which is less than or equal to the number of impeller blades. The blades are curved triangles, and the leading edge of the blades is suspended on the ribs. The shaft sleeve is statically fitted on the rotating shaft, and the points (27) and (29) on the curved edge of the blade that are close to the bottom surface of the two rims are respectively fixed on the circumference of the two bottom surfaces, and the two rims are slid on the bracket shaft sleeve, Surface mutual Kissing into a curved surface that turns the flow.

18、依据权利要求 8所述的离心泵，其特征是：高势比叶轮是半开式部件，或者是使用该部件作基础轮盘的闭式结构，轮沿为圆形或锯齿形，轮盘上有 L形叶片（36) ，叶槽前中部宽阔处设均速梳叶（37) ，形成均速岔道（38 )、 ( 39) ，梳叶前中部亦呈径向走势，形成岔道入口（41 ) 接近而未达到叶槽入口，梳叶尾部光滑转向，顺流线方向指向叶槽加速段，形成岔道出口（40)接近而未达到叶槽出口，岔道出口面积从近压力面到近吸力面渐减。 18. The centrifugal pump according to claim 8, characterized in that: the high potential ratio impeller is a semi-open type component, or a closed structure using the component as a base wheel, and the wheel edge is round or zigzag. There are L-shaped blades (36) on the plate, and a constant speed combing blade (37) is set in the wide middle part of the front of the blade groove to form a uniform speed bifurcation (38), (39). The middle part of the front of the comb blade also shows a radial trend, forming a bifurcation entrance (41) Approaching without reaching the inlet of the blade groove, the tail of the comb leaves turns smoothly, and the downstream direction points to the acceleration section of the blade groove, forming a branch outlet. (40) Approaching without reaching the outlet of the blade groove, the area of the outlet from the near pressure surface to near The suction surface decreases.

19、依据权利要求 18所述的离心泵，其特征是：采用预旋均速高势比叶轮，叶槽中有均速岔道（45) ，吸入室为圆环柱形，其中装有预旋器，其两节轮圈（46)、 (47) 由自润滑材料制成，滑套在叶轮轴套（50)上，其弹性帆式叶片（48)挂在刚性肋条如（49) 上，肋条悬挂于叶轮叶片根部入口处。 19. The centrifugal pump according to claim 18, characterized in that: a pre-spinning average speed high-potential ratio impeller is used, and a constant-speed bifurcation (45) is arranged in the blade groove; the suction chamber is a circular column shape, and the pre-spinning is installed therein; Device, its two sections of rims (46), (47) are made of self-lubricating material, the sliding sleeve is on the impeller shaft sleeve (50), and its elastic sail blades (48) are hung on rigid ribs such as (49), The ribs are suspended at the entrance of the impeller blade root.

20、依据权利要求 8或 18或 19所述的离心泵，其特征是：由均速高势比叶轮（54)、预旋器（55) 、机械轴封（56) 、带二次型蜗道 ( 52) 曲面的前盖（58) 和后盖（59) 及悬臂轴等组成预旋均速高势比二次型蜗道旋臂泵。 20. The centrifugal pump according to claim 8 or 18 or 19, characterized in that: the average speed high potential ratio impeller (54), the pre-spinner (55), the mechanical shaft seal (56), with a secondary worm The curved front cover (58), rear cover (59), and cantilever shaft make up a pre-spinning average speed high-potential ratio secondary type worm-type spiral-arm pump.

21、依据权利要求 2或 9或 10所述的离心泵，其特征是：在泵之出轴端，或者用环形盖板（68) 隔开轴封腔，形成抱轴环形开口（69) 与端腔相通，二相流入管（64) 接入轴封腔内，，在吸入端，或者在腔壁近轴处设环形槽，纳入随叶轮旋转的小动环（74) ，将其隔成顶端远轴的 V形环槽，其一侧间隙（72) 连通前端腔（71 ) ，另一侧间隙（74) 连通吸入室，成为气液分离分流的 V形槽阻气间隙，二相流入管（75) 连通间隙（72) ，部分液体从 V形槽底部入间隙（74) 返回吸入室（77 ) ，气体在间隙（72) 中浮升到近轴处同其余液体一道流入前端腔（71 ) 。 21. The centrifugal pump according to claim 2 or 9 or 10, characterized in that: at the shaft end of the pump, or a ring cover (68) is used to separate the shaft sealing cavity to form a shaft-holding ring-shaped opening (69) and The end cavities are in communication, and the two-phase inflow tube (64) is inserted into the shaft seal cavity. An annular groove is provided at the suction end or near the shaft of the cavity wall to incorporate a small moving ring (74) that rotates with the impeller to separate it. The V-ring groove at the top far axis has a gap (72) on one side connected to the front cavity (71) and a gap (74) on the other side connected to the suction chamber, which becomes a V-shaped gas blocking gap for gas-liquid separation and shunting. Two-phase inflow The tube (75) communicates with the gap (72). Part of the liquid enters the gap (74) from the bottom of the V-shaped groove and returns to the suction chamber (77). The gas floats in the gap (72) to the paraxial position and flows into the front-end cavity together with the remaining liquid ( 71).

22、依据权利要求 2或 9所述的离心泵，其特征是：半开式叶轮悬臂泵的内减摩驱动装置由压力液体调节阀（79) 、射流器（81 ) 、引射气体调节阀（80) 及连接细管组成，当泵之出口压力比叶轮输出静压力高 0. 05MPa以上时，压力液体从该出口分流引出，使用空气时其入端通大气，输出二相流接入轴封腔，冷却轴封（82)后，从环形盖板出口（83) 流入后端腔。 22. The centrifugal pump according to claim 2 or 9, characterized in that the internal friction reducing driving device of the semi-open impeller cantilever pump is composed of a pressure liquid regulating valve (79), a jet (81), and an ejection gas regulating valve. (80) and connecting thin tube, when the outlet pressure of the pump is higher than the output static pressure of the impeller by more than 0.05 MPa, the pressure liquid is diverted from this outlet, and the air is used to enter the atmosphere at the inlet end, and the output two-phase flow is connected to the shaft Seal the cavity, cool the shaft seal (82), and then flow into the rear cavity from the annular cover outlet (83).

23、依据权利要求 2或 9所述的离心泵，其特征是：闭式叶轮离心泵的内减摩驱动装置由压力液体调节阀（92) 、射流器（90) 、引射气体调节阀（91 ) 、流量分配管（87) 和（88 )及前端腔阻气间隙（93)组成，当泵之出口压力比叶轮输出静压力高 0. 05MPa以上时，压力液体从该出口分流引出，输出二相流通过流量分配管（88) 和（87)控制前后端腔的稳态流量分配，其中（87)接入轴封腔，冷却轴封（85) 后，从环形盖板出口流入后端腔，（88 )接入前端腔，经阻气间隙（93) 阻气以防逃逸，阻气间隙（93) 或者不是 V形环槽而是置于同一位置的软挡圈，用二相流润滑。 23. The centrifugal pump according to claim 2 or 9, characterized in that the internal friction reducing driving device of the closed impeller centrifugal pump is composed of a pressure liquid regulating valve (92), a jet (90), and an ejection gas regulating valve ( 91), flow distribution pipes (87) and (88) and front-end cavity air gap (93), when the pump outlet pressure is higher than the static pressure of the impeller output by 0.05 MPa or more, the pressure liquid is diverted from this outlet and output The two-phase flow controls the steady-state flow distribution of the front and rear chambers through flow distribution pipes (88) and (87), where (87) is connected to the shaft seal chamber, and after cooling the shaft seal (85), it flows into the rear end from the annular cover outlet The cavity (88) is connected to the front cavity, and is prevented from escaping through the air-blocking gap (93). The air-blocking gap (93) is not a V-ring groove but a soft retaining ring at the same position. Two-phase flow is used. lubricating.

24、依据权利要求 3所述的离心泵，其特征是：向心导轮由圆环柱形外壳（101 ) 、基板（103 ) 、轴套（104) 以及曲率半径逐渐减小的导叶（106 ) 组成，外壳上带有转移段流道腔（107) ，导叶间为减速增压流道（109) ，其导叶数少于叶轮叶片数，其全程减速增压比等于入出口截面积的反比，各流道汇流于中心环腔，经轴套旋转曲面约束，液流转 90度轴向输出，或者，中心环腔中安有径向入流预旋器，由其轮圈构成转向约束面。 24. The centrifugal pump according to claim 3, characterized in that the centripetal guide wheel is formed by a circular cylindrical shell (101), The base plate (103), the shaft sleeve (104), and the guide vane (106) with a gradually decreasing radius of curvature, the casing is provided with a transfer section flow passage cavity (107), and the guide vanes are decelerated and pressurized runners (109) The number of guide vanes is less than the number of impeller blades, and the full deceleration and pressure increase ratio is equal to the inverse ratio of the cross-sectional area of the inlet and outlet. A radial inflow pre-rotator is installed in the central ring cavity, and the steering constraining surface is formed by its rim.

25、依据权利要求 11所述的离心泵，其特征是：以导流流道入口段截止隔舌（118) 出现为起迄点，以隔舌间距圆心角为周期，向心导轮转移段流道合成截面的形状和面积随圆心角周期性变化，其变化规律为： a、截面积线性增大，两部分分两段分别变化，从起点到前一流道增压段正位点（117) ，叶轮腔部分从最小值线性增到最大值，导轮部分为 0，从该点到终点，叶轮腔部分从最大值线性减到最小值，导轮部分从 0线性增到最大值； b、上述合成截面积最小值等于叶轮腔部分最小值，即等于隔舌出现位置（118) 、曲线（119)和叶轮圆柱面母线构成的曲边三角形的面积，曲线（119) 由两段椭圆弧与中间一段圆弧吻接而成，合成截面积的最大值等于其最小值加上导轮部分截面积的最大值，后者等于合成截面积增大比例系数与圆心角周期的乘积，叶轮腔部分截面积最大值等于隔舌出现位置（118 )、曲线（120)和叶轮圆柱面母线构成的曲边三角形的面积，曲线（120) 是汇流截面最大边际，由两段椭圆弧吻接而成，由端点坐标和入口段截止期间合成截面积的增量确定； c、两部分形状分两段分别变化，叶轮腔部分在面积增大期间呈曲边三角形，其曲线边为从曲线（119) 开始到曲线（120) 为止的系列中间曲线，导轮部分在面积增大期间，形状由起始直线段（118 ) 开始，经历如下变化：以（118 ) 为长轴的长半椭圆而短半轴渐增，成为半圆后连续前移而后接矩形，前移至（116 ) 位置时隔舌出现而成为增压段； d、成为增压段后，边际线（116) 和（118 ) 继续变形和前向移动，形成隔舌的最小物理宽度后，后向侧边际线由隔舌前向边际直线段变为向后弯曲的长半椭圆，短半轴渐增，成为半圆后改为平移，移至流道底面（117) 止，前半圆亦连续前移，移至与底面（115) 相切时，改为连续压缩为长半椭圆，最后变为直线，截面前移变形期间，截面积按减速增压要求扩张，其中心线的径向坐标或者也发生变化。 25. The centrifugal pump according to claim 11, characterized in that the cut-off tongue (118) of the inlet section of the diversion channel is taken as the starting point and the center of the tongue-spacing interval is used as a period to transfer the section to the centrifugal guide wheel. The shape and area of the composite cross section of the flow channel change periodically with the center angle. The change law is as follows: a. The cross-sectional area increases linearly, and the two parts change separately in two sections. From the starting point to the positive point of the supercharging section of the former channel (117 ), The impeller cavity portion linearly increases from the minimum value to the maximum value, and the guide wheel portion is 0. From this point to the end point, the impeller cavity portion linearly decreases from the maximum value to the minimum value, and the guide wheel portion linearly increases from 0 to the maximum value; b The minimum value of the above composite cross-sectional area is equal to the minimum value of the impeller cavity part, that is, the area of the curved triangle formed by the appearance position of the tongue (118), the curve (119) and the generatrix of the cylindrical surface of the impeller. The curve (119) consists of two elliptical arcs. It is formed by kissing the middle arc. The maximum value of the composite cross-sectional area is equal to its minimum value plus the maximum value of the cross-sectional area of the guide wheel. The latter is equal to the ratio of the increase of the composite cross-sectional area to the center angle period. By product, the maximum cross-sectional area of the impeller cavity is equal to the area of the curved triangle formed by the location of the tongue (118), the curve (120), and the generatrix of the impeller cylindrical surface. The curve (120) is the maximum margin of the confluence cross section and consists of two elliptical arcs. It is formed by the matching of the endpoint coordinates and the increase of the combined cross-sectional area during the cut-off period of the entrance section; c. The shape of the two parts is changed in two sections, and the impeller cavity part is a curved triangle during the increase of the area. The series of intermediate curves from curve (119) to curve (120). During the increase of the area of the guide wheel, the shape starts from the initial straight line (118) and undergoes the following changes: (118) is the long half of the long axis The ellipse and the short semi-axis gradually increase, becoming a semicircle and then moving forward and then followed by a rectangle. When moving forward to the position (116), the tongue appears and becomes the supercharging section; d. After becoming the supercharging section, the marginal line (116) and ( 118) After continuing to deform and move forward to form the minimum physical width of the tongue, the backward side marginal line changes from a straight forward segment of the tongue to a long semi-ellipse bent backward, and the short semi-axis gradually After increasing to become a semicircle, it will be translated to the bottom of the runner (117), and the front semicircle will also move forward continuously. When it moves to tangent to the bottom (115), it will be continuously compressed into a long semi-ellipse, and finally become a straight line During the section's forward deformation, the cross-sectional area expands according to the requirements of deceleration and supercharging, and the radial coordinate of its centerline may also change.

26、依据权利要求 11所述的离心泵，其特征是：向心导轮的导叶具有与圆周腔壁吻接的变曲率起点，该起点是转移之后的增压流道正位点，由该点决定转移段流道中心的径向坐标，转移段流道截面分为叶轮腔部分和导轮部分，两部分装配吻接合一，截面的叶轮腔部分被叶轮盖包裹于叶轮中，具有固定的面积和形状，由其承担轴面速度分量的转向调整，截面的导轮部分是两个相邻隔舌之间的一段与叶轮腔连通的空间的横断面，该截面独. 立控制汇流和切向及轴向运动过程，随着导流圆心角的增加，截面的导轮部分以隔舌为起点和终点周期性地变化，一个周期内的变化规律是： a、截面积从 0线性增大到最大值，增大比例系数等于叶轮转过单位角度排出的液流体积设计值除以液流出口绝对速度设计值，或者还乘以一个大于 1而小于导轮增压流道最小扩张比的扩张系数，截面积最大值等于增大比例系数乘以流道入口段对应的圆心角，当增大比例系数包含扩张系数因子时，转移段流道具有减速增压功能； b、截面由起始直线段（128 ) 开始，经历多种形状变化，首先是以（1.28 ) 为长轴的长半椭圆，其短半轴逐渐增大；成为半圆后，改为半圆边际连续前移，形成前半圆后接矩形的截面；当隔舌出现时，半圆移到（126 ) 位置，转移段流道与叶轮腔隔开而成为增压流道； c、隔舌出现和隔离叶轮腔后，（126 ) 和（128 ) 限定的流道成为增压流道，仍继续前移和变形，在少量前移留下隔舌的最小物理宽度后，其后向侧边际线由直线段变为向后弯曲的长半椭圆，其短半轴连续加长，成为半圆后再改为平移，直到最后点进入流道底面（127) 为止，该过程中，其前向边际半圆连续前移，直到与导轮底平面 125相切时，改为连续压缩半圆为半椭圆，最后变为直线与底平面贯通，上述轮廓线或质心移动的速度应该大于汇流期间的相应移动速度一个恰当的百分比，例如大于 50%，以使隔舌的截面积和强度能够连续增加，增压流道截面前移正位期间，其面积按减速增压要求变化。 26. The centrifugal pump according to claim 11, characterized in that: the guide vanes of the centripetal guide wheel have a starting point of variable curvature that is in contact with the wall of the circumferential cavity, and the starting point is the positive position of the booster flow channel after the transfer. This point determines the radial coordinates of the center of the flow channel of the transfer section. The section of the flow channel of the transfer section is divided into the impeller cavity part and the guide wheel part. The two parts are assembled and joined together. The area and shape are adjusted by the steering of the axial surface velocity component. The cross section of the guide wheel is a cross section of a space between two adjacent tongues that communicates with the impeller cavity. The cross section is independent. In the tangential and axial movement process, with the increase of the diversion center angle, the section of the guide wheel periodically changes with the tongue as the starting point and the end point. The change law within a cycle is: a. The cross-sectional area increases linearly from 0. When it reaches the maximum value, increasing the proportionality factor is equal to the design value of the volume of the liquid flow discharged by the impeller through a unit angle divided by the design value of the absolute speed of the liquid flow outlet, or it is multiplied by a pressure greater than 1 and smaller than the booster flow path The expansion coefficient of the smallest expansion ratio, the maximum cross-sectional area is equal to the increase of the proportionality coefficient multiplied by the circle center angle corresponding to the inlet section of the flow channel. The moving channel has the function of decelerating and supercharging; b. The cross section starts from the initial straight line (128) and undergoes various shape changes. First, the long semi-ellipse with (1.28) as the long axis, and the short semi-axis gradually increases. After becoming a semicircle, the semicircle margin is moved forward continuously to form a rectangular cross section followed by a front semicircle; when the tongue appears, the semicircle moves to the position (126), and the flow passage of the transfer section is separated from the impeller cavity to become a pressurized flow. C. After the tongue appears and isolates the impeller cavity, the flow channel defined by (126) and (128) becomes a pressurized flow channel, and continues to move forward and deform, leaving a minimum physical width of the tongue after a small amount of forward movement The rear side marginal line changes from a straight line segment to a long curved semi-ellipse that is curved backwards. The short semi-axis is continuously lengthened to become a semicircle and then changed to translation until the last point enters the bottom surface of the runner (127). Its forward marginal semicircle continues to move forward until it is tangent to the bottom plane 125 of the guide wheel. Instead, it continuously compresses the semicircle into a semi-ellipse, and finally becomes a straight line penetrating the bottom plane. The contour line or center of mass should move faster than the confluence. period A moving speed corresponding appropriate percentage, such as greater than 50%, so that the cross-sectional area and strength of the tongue can be continuously increased during anteroposterior supercharged forward flow passage cross section area of which changes according to the deceleration required supercharging.

27、依据权利要求 12所述的离心泵，同时釆用权利要求 4所述的离心泵模块化组合方法进行技术扩充，其特征是：对称端盖模块由带装配止口（141 ) 的承压盖板（142 ) 、盖板上的三维蜗道（146 ) 及其环形出入口（143 ) 、与蜗道（146 ) 吻接的直线段管道、蜗道结构体支承的轴套（149 )和轴承腔（145 ) 等结构组成，其蜗道具有截面积与圆心角成正比、摩擦面和加速度均已优化的约束特征，目的性扩充并规范其功能设计和用途用法，内容包括： a、利用其环形接口及三维蜗道内部兼容和约束三维运动的特性，构造或自适应生成叶轮和导轮多流道工作的分流、汇流、旋转、轴面转向等连接边界条件，既满足叶轮入口连接要求，又满足向心导轮出口连接要求，使之对于单级泵和多级泵具有普遍性，据以用作单级泵和多级泵通用的流场边界模块，以支持所述的保守环量连接模式； b、利用其环形接口及兰维蜗道内部兼容和约束三维运动的特性，扩展为流入流出方向亙反的、分流汇流性质互反的技术设计兼容性，据以用作在保守环量连接模式下前后通用的流场对称边界模块； c、利用其环形接口及三维蜗道内部的方向兼容性和三维运动的连续性，限制和优化流速的空间和时间变化率，使之最小化，据以用作具有稳定性和低损耗特性的流场边界模块，以取得保守环量连接模式下的高性能； d、利用其环形接口和装配止口的旋转对称性，以及所带蜗道和引出管基于隔舌相对角定位的特点，据以构造前后盖各自独立变角度出管的功能，以支持模块化组合所需的装配结构和功能扩展设计； e、利用其带承压 27. The centrifugal pump according to claim 12, and at the same time using the centrifugal pump modular combination method of claim 4 for technical expansion, characterized in that: the symmetrical end cover module is pressurized by the assembly stop (141) The cover plate (142), the three-dimensional volute (146) on the cover plate and its annular entrance and exit (143), the linear section pipe that is in contact with the worm channel (146), the shaft sleeve (149) supported by the worm structure and the bearing The cavity (145) is composed of structures such as a worm. The worm trajectory has a constraint feature that the cross-sectional area is proportional to the center angle, and the friction surface and acceleration are optimized. The purpose is to expand and standardize its functional design and usage. The contents include: a. The ring interface and the three-dimensional wormway are internally compatible and constrained by the characteristics of three-dimensional motion, and construct or adaptively generate the boundary conditions of shunts, confluences, rotations, and axial surface steering of the impeller and guide wheel in the multi-flow channel, which not only meet the impeller inlet connection requirements, It also meets the requirements for the connection of the centrifugal guide wheel outlet, making it universal for single-stage and multi-stage pumps, and is used as a common flow field boundary for single-stage and multi-stage pumps. Block to support the described conservative loop connection mode; b. Use its ring interface and Lanwei volute internal compatibility and constraints of three-dimensional motion to expand into the inflow and outflow direction of the reverse design, the characteristics of the shunting and reversing technology design Compatibility, which is used as a symmetrical boundary module of the flow field before and after in the conservative loop connection mode; c. Utilizing the circular interface and the direction compatibility within the three-dimensional volute and the continuity of the three-dimensional motion to limit and optimize the flow velocity. Spatial and temporal change rates are minimized and used as a flow field boundary module with stability and low loss characteristics to achieve high performance in conservative loop connection mode; d. Utilize its ring interface and assembly stop The rotational symmetry of the worm, and the characteristics of the worm and the lead-out tube based on the relative angle positioning of the tongue, so as to construct the function of the independently variable-angle outlet tube of the front and rear covers to support the assembly structure and functional expansion design required by the modular combination. E. Use its belt to bear pressure

板、轴承座等一体化结构特点，在技术及工艺设计上确定为可模成型的单一零件功能部件，蕴含上述技术扩充后，据以构造支持所述连接模式的装配尺寸和接口参数可标准化的端盖模块，扩大其体积小、设计简单、成本低、功能强的价值运用范围。 Integrated structural features such as plates and bearing housings are identified as moldable single-part functional components in terms of technology and process design. After the expansion of the above technology, the assembly dimensions and interface parameters that support the connection mode can be standardized. The end cap module expands the value application range of its small size, simple design, low cost and strong function.

28、依据权利要求 3或 11或 24或 25或 26所述的离心泵，釆用权利要求 4所述的模块化组合方法组合， '其特征是：包含向心增压模块，该模块由向心导轮、叶轮和叶轮腔盖板轴向组合而成，或者还配有其他功能附件，具有标准化的接口参数和装配尺寸，向心导轮是模成型一体化制造的，其腔侧平面或旋转曲面与叶轮形成间隙配合，腔侧外沿有依据叶轮参数设计的转移段流道前向边际曲面，其级段式外壳上有装配止口，与外壳相连的中隔板作为导叶支承基板，同时起隔离叶轮腔和导轮腔并承受其间压差的作用，叶轮腔盖板为模成型减重结构零件，其腔侧旋转曲面与叶轮形成间隙配合，腔侧外沿有依据叶轮参数设计的转移段流道后向边际曲面，使转移段流道得到完备约束，并与增压流道串联，装配时，顺序装入导轮、.叶轮和叶轮腔盖板，三者分别通过外壳止口、转轴和导轮之叶轮腔定位，运行时，液流从模块入口带环量轴向流入旋转的叶轮流道，从中接受叶片法向力功沿途加速并积分离心力功增加比能，经转移段流道流入导轮，在其中减速增压后，转 90度从近轴环形口带环量流出模块。 28. The centrifugal pump according to claim 3 or 11 or 24 or 25 or 26, which is combined with the modular combination method according to claim 4, 'characterized in that: it comprises a centripetal booster module, which is provided by The core guide wheel, the impeller and the impeller cavity cover are axially combined, or are equipped with other functional accessories with standardized interface parameters and assembly dimensions. The wheel is integrally manufactured by molding. The cavity side plane or rotating surface forms a clearance fit with the impeller. The outer edge of the cavity side has a forward marginal curved surface of the transfer section flow channel designed according to the parameters of the impeller. The middle partition plate connected to the shell serves as the guide vane support substrate, and simultaneously isolates the impeller cavity from the impeller cavity and withstands the pressure difference between them. The impeller cavity cover plate is a molded weight-reducing structural part. The impeller forms a clearance fit, and the outer edge of the cavity side has a backward marginal curved surface of the transfer section flow channel designed according to the parameters of the impeller, so that the transfer section flow channel is fully constrained and connected in series with the booster flow channel. When assembling, it is sequentially loaded into the guide wheel, The impeller and the impeller cavity cover plate are respectively positioned by the casing stop, the rotating shaft and the impeller cavity of the guide wheel. During operation, the liquid flow flows from the module inlet into the rotating impeller flow channel axially and receives the blade normal direction. The force work is accelerated along the way and the centrifugal force work is integrated to increase the specific energy, flow into the guide wheel through the flow passage of the transfer section, decelerate and pressurize it, and then rotate 90 degrees out of the module with a ring-shaped annular mouth.

29、依据权.利要求 28所述的离心泵，其特征是：包含半开式叶轮向心增压模块，该模块由向心导轮（157) 、半开式叶轮（154) 和叶轮腔盖板（152) 轴向组合而成。 29. The centrifugal pump according to claim 28, comprising: a centrifugal booster module with a semi-open impeller, which is composed of a centrifugal guide wheel (157), a semi-open impeller (154), and an impeller cavity. The cover plate (152) is assembled axially.

30、依据权利要求 28所述的离心泵，其特征是：包含闭式叶轮向心增压模块，该模块由向心导轮（167) 、闭式叶轮（164) 和叶轮腔盖板（162) 轴向组合而成，其中，叶轮腔盖（162) 上挖去了叶轮盖所占据的空间，以使叶槽流道与出口流道吻接。 30. The centrifugal pump according to claim 28, comprising a centrifugal booster module with a closed impeller, the module is composed of a centrifugal guide wheel (167), a closed impeller (164) and an impeller cavity cover plate (162). ) Axially combined, wherein the space occupied by the impeller cover (162) is excavated from the impeller cavity cover (162) so as to make the impeller flow passage and the outlet flow passage kiss.

31、依据权利要求 28所述的离心泵，其特征是：包含减摩闭式叶轮向心增压模块，该模块由向心导轮 .（179) 、闭式叶轮（180) 和叶轮腔盖（175 ) 以及 V形槽阻气间隙环形盖板（171 ) 、 V形槽动环（172) 、充气驱动二相流入管（174) 、前盖固定铆钉中的前后端腔均压孔（177)等内减摩零件或结构组合而成，其中，叶轮腔盖（175) 上挖去了叶轮盖所占据的空间，以使叶槽流道与出口外流道吻接，均压孔（177) 使前后端腔连通，叶轮腔盖板（175) 上的环槽、环形盖板（171 ) 和旋转动环（172) 构成 V形槽阻气间隙。 31. The centrifugal pump according to claim 28, comprising: a centrifugal booster module for reducing friction of a closed impeller, the module is composed of a centrifugal guide wheel (179), a closed impeller (180) and an impeller cavity cover (175) and V-shaped groove air-blocking gap cover plate (171), V-shaped groove moving ring (172), inflatable driving two-phase inflow pipe (174), pressure equalization holes in the front and rear cavity of the front cover fixing rivet (177 ) And other internal friction reducing parts or structures, in which the space occupied by the impeller cover (175) is excavated from the impeller cover (175), so that the flow path of the blade groove is in contact with the outer flow channel of the outlet, and the pressure equalizing hole (177) The front and rear cavities are communicated, and the ring groove on the impeller cavity cover plate (175), the ring cover plate (171) and the rotating movable ring (172) form a V-shaped air gap.

32、依据权利要求 28所述的离心泵，其特征是：包含半开式均速高势比叶轮向心增压模块，该模块由向心导轮（188) 、半开式均速高势比叶轮（183)和叶轮腔盖板 ( 182) 轴向组合而成， 32. The centrifugal pump according to claim 28, comprising a centrifugal booster module with a half-open average speed high potential ratio impeller, which is composed of a centripetal guide wheel (188) and a half-open average speed high potential. The impeller (183) and the impeller cavity cover (182) are axially combined,

33、依据权利要求 28所述的离心泵，其特征是：包含闭式均速高势比叶轮向心增压模块，该模块由向心导轮（198 ) 、半开式均速高势比叶轮（193) 和叶轮腔盖板（192) 轴向组合而成，其中，叶轮腔盖（192) 上挖去了叶轮盖所占据的空间，叶槽流道与出口外流道吻接。 33. The centrifugal pump according to claim 28, comprising: a closed-type average speed high-potential ratio impeller centripetal booster module, which is composed of a centripetal guide wheel (198), a semi-open type average speed high-potential ratio The impeller (193) and the impeller cavity cover plate (192) are axially combined. The impeller cavity cover (192) is cut out of the space occupied by the impeller cover, and the blade groove flow channel is in contact with the outlet outer flow channel.

34、依据权利要求 28所述的离心泵，其特征是：包含预旋闭式均速高势比叶轮向心增压模块，该模块由向心导轮（208) 、均速高势比闭式叶轮（204) 、预旋器（201 ) 和叶轮腔盖板（202)轴向组合而成，其中，叶轮腔盖（192)上挖去了叶轮盖所占据的空间。 34. The centrifugal pump according to claim 28, comprising: a pre-spinning closed-speed high-potential ratio impeller centrifugal booster module, which is closed by a centripetal guide wheel (208) and an average-speed high-potential ratio block. The impeller (204), the pre-rotator (201), and the impeller cavity cover plate (202) are axially combined, and the space occupied by the impeller cover is cut out from the impeller cavity cover (192).

35、依据权利要求 28所述的离心泵，其特征是：包含减摩闭式均速高势比叶轮向心增压模块，该模块由向心导轮（219) 、闭式均速髙势比叶轮（220) 、叶轮腔盖板（215) 以及 V形槽阻气间隙环形盖板（211 ) 、 V形槽动环（212) 、二相流入管（214) 、前盖铆钉中的前后端腔均压孔（217) 组合而成，其中，叶轮腔盖（215) 上挖去了叶轮盖所占据的空间。 35. The centrifugal pump according to claim 28, comprising: a centrifugal booster module for reducing friction, a closed-type, constant-velocity, high-potential ratio impeller; Than the impeller (220), the impeller cavity cover (215), the V-shaped groove air-gap annular cover (211), the V-shaped groove moving ring (212), the two-phase inflow pipe (214), the front cover rivets The end cavity pressure equalizing hole (217) is combined, wherein the impeller cover (215) is dug out and occupied by the impeller cover. Space.

36、依据权利要求 28所述的离心泵，其特征是：包含预旋减摩闭式均速高势比叶轮向心增压模块，该模块由向心导轮（228)、闭式均速高势比叶轮（230)、叶轮腔盖板（225) 及轴向来流预旋器（221 ) 和 V形槽动环阻气结构（222) 、二相流入管（223) 、前后端腔连通均压孔（227) 组成。 36. The centrifugal pump according to claim 28, comprising: a centrifugal booster module with a pre-spinning friction-reducing closed-type average speed high-potential ratio impeller, which is composed of a centrifugal guide wheel (228) and a closed-type average speed. High potential ratio impeller (230), impeller cavity cover plate (225), axial inflow pre-rotator (221), V-groove dynamic ring gas blocking structure (222), two-phase inflow pipe (223), front and rear cavity Composed of pressure equalizing holes (227).

37、依据权利要求 28所述的离心泵，其特征是：包含超减摩预旋闭式均速高势比叶轮向心增压模块，该模块含有向心导轮（240 ) 、带延伸并包含转移段流道叶轮腔截面部分的叶轮盖板（234) 的闭式均速高势比叶轮（236 ) 、叶轮腔盖板（235 ) 及轴向来流预旋器（231 ) 和超减摩组件（232) 、二相流入管（233) 组件。 37. The centrifugal pump according to claim 28, comprising: a centrifugal supercharging module with an ultra-reduced pre-rotational closed-type high-potential ratio impeller, which includes a centripetal guide wheel (240), with an extension and Closed average speed high potential ratio impeller (236), impeller cavity cover (235), axial flow prerotator (231), and super-reduction Friction assembly (232), two-phase inflow pipe (233) assembly.

38、依据权利要求 12或 27所述的离心泵，采用权利要求 4所述的模块化组合方法，其特征是：包含 2个变角度出管对称端盖模块和 1个向心增压模块，两种模块依据对应的子规格各具完全互换性，或者依据对应的父规格经查表检验介质、最高转速、最高温度、最高耐压等参数互换性成立，按 "液流从近轴环形口带环量流入和流出"连接模式将 3个模块轴向组合，即构成具有模块互换性的对称盖变角出管向心增压单级离心泵，组合是指设计中的连接配合、生产中的装配和使用中的修配，互换性覆盖这些过程。 38. The centrifugal pump according to claim 12 or 27, which adopts the modular combination method according to claim 4, comprising: 2 variable-angle outlet pipe symmetrical end cover modules and 1 centripetal booster module, The two modules are fully interchangeable according to the corresponding child specifications, or the parameters of the medium, the maximum speed, the maximum temperature, and the maximum pressure resistance are verified by checking the table according to the corresponding parent specifications. "Circular mouth with ring-shaped inflow and outflow" connection mode combines three modules axially, that is, a symmetrical cover with variable angle and outlet tube centrifugal booster single-stage centrifugal pump with module interchangeability. The combination refers to the connection and coordination in the design. , Assembly in production and repair in use, interchangeability covers these processes.

39、依据权利要求 29与 38所述的离心泵，其特征是：包含 1个半开式叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由半开式叶轮（245) 、叶轮腔盖（243) 和向心导轮（247) 组成，后者分别用作前盖（241 ) 和后盖（250) ，轴向组合成具有模块互换性的对称盖变角出管半开式叶轮向心增压单级离心泵。 39. The centrifugal pump according to claim 29 and 38, comprising: a semi-open impeller centripetal booster module and two variable angle outlet tube symmetrical end cover modules, the former being a semi-open impeller (245 ), The impeller cavity cover (243) and the centrifugal guide wheel (247), the latter is used as the front cover (241) and the rear cover (250), respectively, axially combined to form a symmetrical cover with modular interchangeability. Tube semi-open impeller centrifugal single-stage centrifugal pump.

40、依据权利要求 30与 38所述的离心泵，其特征是：包含 1个闭式叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式叶轮（255) 、叶轮腔盖（253) 和向心导轮（257) 组成，后者分别用作前盖（251 ) 和后盖 ( 260) ，轴向组合成具有模块互换性的对称盖变角出管闭式叶轮向心增压单级离心泵。 40. The centrifugal pump according to claim 30 and 38, comprising: a closed impeller centripetal booster module and two variable angle outlet pipe symmetrical end cover modules, the former being a closed impeller (255), The impeller cavity cover (253) and the centrifugal guide wheel (257) are used, the latter is used as the front cover (251) and the rear cover (260), respectively, axially combined into a symmetrical cover with modular interchangeability and variable angle outlet pipe closure. Centrifugal pump with centrifugal impeller.

41、依据权利要求 31与 38所述的离心泵，其特征是：包含 1个减摩闭式叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式叶轮（268 ) 、叶轮腔盖（265) 、向心导轮（267)及阻气间隙（263) 、二相流入管（264) 、前后端腔连通均压孔（266) 组成，后者分别用作前盖（261 )和后盖（270) ，轴向组合成具有模块互换性的对称盖变角出管减摩闭式叶轮向心增压单级离心泵。 41. The centrifugal pump according to claim 31 and 38, comprising: a friction-reducing closed-type impeller centrifugal booster module and two variable-angle outlet pipe symmetrical end cover modules, the former being a closed-type impeller (268 ), Impeller cavity cover (265), centripetal guide wheel (267) and choke gap (263), two-phase inflow tube (264), front and rear cavity communication pressure equalization holes (266), the latter are used as front The cover (261) and the back cover (270) are axially combined to form a symmetrical cover variable angle outlet tube friction reducing closed impeller single-stage centrifugal pump with modular interchangeability.

42、依据权利要求 32与 38所述的离心泵，其特征是：包含 1个半开式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由半开式均速高势比叶轮（274) 、叶轮腔盖（273) 、向心导轮（277) 组成，后者分别用作前盖（271 ) 和后盖（280) ，轴向组合成具有模块互换性的对称盖变角出管半开式均速高势比叶轮向心增压单级离心泵。 42. The centrifugal pump according to claim 32 and 38, comprising: a semi-open type constant speed high potential ratio impeller centrifugal booster module and two variable angle outlet pipe symmetrical end cover modules, the former consists of half Open type average speed high potential ratio impeller (274), impeller cavity cover (273), centripetal guide wheel (277), the latter is used as the front cover (271) and the rear cover (280) respectively, axially combined to have Module interchangeable symmetrical cover variable angle outlet pipe semi-open type uniform speed high potential ratio centrifugal single-stage centrifugal booster pump with centrifugal boost.

43、依据权利要求 33与 38所述的离心泵，其特征是：包含 1个闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮（284) 、叶轮腔盖（283 ) 、向心导轮（287 ) 组成，后者分别用作前盖（281 ) 和后盖（290) ，轴向组合成具有模块互换性的对称盖变角出管闭式均速高势比叶轮向心增压单级离心泵。 43. The centrifugal pump according to claim 33 and 38, comprising: a closed-type high-potential ratio impeller centripetal booster module and two variable-angle outlet-tube symmetrical end-cap modules, the former being a closed type Impeller (284) with high average potential It consists of a wheel cavity cover (283) and a centripetal guide wheel (287). The latter is used as the front cover (281) and the rear cover (290) respectively. The axial combination is a symmetrical cover with modular interchangeability and variable angle outlet pipe closure. Single-stage centrifugal pump with centrifugal booster and centrifugal pressure booster.

44、依据权利要求 34与 38所述的离心泵，其特征是：包含 1个预旋闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮（295 )、装在叶轮吸入室中的预旋器（293 ) 、叶轮腔盖（294) 、向心导轮（297 ) 组成，后者分别用作前盖 ( 291 )和后盖（300) ，轴向组合成具有模块互换性的对称盖变角出管预旋闭式均速高势比叶轮向心增压单级离心泵。 44. The centrifugal pump according to claim 34 and 38, comprising: a pre-spin closed closed-velocity high-potential ratio impeller centrifugal booster module and two variable-angle outlet pipe symmetrical end cover modules, the former by It consists of a closed average speed high potential ratio impeller (295), a pre-rotator (293) installed in the impeller suction chamber, an impeller cavity cover (294), and a centripetal guide wheel (297). The latter is used as a front cover ( 291) and the rear cover (300), which are axially combined to form a symmetrical cover variable angle outlet pipe with a module interchangeability.

45、依据权利要求 35与 38所述的离心泵，其特征是：包含 1个减摩闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮（308 )、叶轮腔盖（305 ) 、向心导轮（307) 及阻气间隙（303 ) 、二相流入管（304) 、前后端腔均压孔（306 ) 组成，后者分别用作前盖（301 ) 和后盖（310) ，轴向组合成具有模块互换性的对称盖变角出管减摩闭式均速高势比叶轮向心增压单级离心泵。 45. The centrifugal pump according to claim 35 and 38, comprising: a friction-reducing closed-type constant-velocity high-potential-ratio impeller centrifugal booster module and two variable-angle outlet pipe symmetrical end cover modules, the former by Closed average speed high potential ratio impeller (308), impeller cavity cover (305), centripetal guide wheel (307) and choke gap (303), two-phase inflow pipe (304), front and rear cavity pressure equalization holes (306 ), The latter is used as the front cover (301) and the rear cover (310) respectively, axially combined to form a symmetrical cover with variable modules, variable angle outlet tube, reduced friction, closed average speed, high potential ratio, impeller, and centrifugal pressure increase Single-stage centrifugal pump.

46、依据权利要求 36与 38所述的离心泵，其特征是：包含 1个减摩预旋闭式均速高势比叶轮向心增压模块和 2 个变角度出管对称端盖模块，前者由式均速高势比叶轮 ( 318 ) 、叶轮腔盖（315 ) 、向心导轮（317 ) 、预旋器（312) 及阻气间隙（313) 、二相流入管 ( 314)、前后端腔均压孔 ( 316)组成，后者分别用作前盖（311 )和后盖 ( 320)，轴向组合成具有模块互换性的对称盖变角出管减摩预旋闭式均速高势比叶轮向心增压单级离心泵。 46. The centrifugal pump according to claim 36 and 38, comprising: a friction-reducing pre-spinning type average speed high potential ratio impeller centrifugal booster module and two variable-angle outlet pipe symmetrical end cover modules, The former consists of impeller (318), impeller cavity cover (315), centripetal guide (317), pre-rotator (312) and choke gap (313), two-phase inflow pipe (314), The front and rear chambers are composed of pressure equalizing holes (316), the latter being used as the front cover (311) and the rear cover (320), which are axially combined to form a symmetrical interchangeable cover with variable interchangeability and modular anti-friction pre-rotation closure. Centrifugal single-stage centrifugal pump with uniform speed and high potential ratio and impeller.

47、依据权利要求 37与 38所述的离心泵，其特征是：包含 1个超减摩预旋闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由带有延伸包覆转移段流道的叶轮盖（326 ) 的闭式均速髙势比叶轮（327) 、叶轮腔盖（325 ) 、向心导轮（329 )、预旋器（322 )及阻气间隙（323 ) 、前端腔二相流入管（324) 、后端腔二相流入管（328 ) 组成，后者分别用作前盖（321 ) .和后盖（330 ) ，轴向组合成具有模块互换性的对称盖变角出管超减摩预旋闭式均速高势比叶轮向心增压单级离心泵。 47. The centrifugal pump according to claim 37 and 38, comprising: a super-reduction anti-friction pre-rotational closed-velocity high-potential ratio impeller centrifugal booster module and two variable-angle outlet pipe symmetrical end cover modules The former consists of a closed average velocity pseudopotential ratio impeller (327), an impeller cavity cover (325), a centripetal guide wheel (329), and a pre-rotator ( 322), the air-blocking gap (323), the front-end cavity two-phase inflow tube (324), and the back-end cavity two-phase inflow tube (328), the latter being used as the front cover (321) and the rear cover (330), respectively. The axial combination is a symmetrical single-stage centrifugal pump with a modular interchangeability, a variable cover, a variable angle outlet tube, a super-friction reduction, a pre-spinning, and a high-potential ratio impeller.

48、依据权利要求 12或 27所述的离心泵，釆用权利要求 4所述的模块化组合方法，其特征是：包含 2个变角度出管对称端盖模块和最多为 64个的多个向心增压模块，两种模块依据对应的子规格各具完全互换性，或者依据对应的父规格经査表检验介质、最高转速、最高温度、最高耐压等参数互换性成立，其中最高耐压的互换性或者是轴向分段成立的，按照 "液流从近轴环形口带环量流入和流出"的连接模式，将对称端盖模块分作前后盖，将向心增压模块依次轴向串联，全部模块轴向组合，即构成具有模块互换性的对称盖变角出管向心增压多级离心泵，组合是指设计中的连接配合、生产中的装配和使用中的修配，互换性覆盖这些过程。 48. The centrifugal pump according to claim 12 or 27, wherein the modular combination method according to claim 4 is used, comprising: 2 variable-angle outlet pipe symmetrical end cover modules and a plurality of 64 at most. Centripetal booster module, the two modules are fully interchangeable according to the corresponding sub-specification, or the parameters of the medium, the maximum speed, the maximum temperature, and the maximum withstand pressure are verified according to the corresponding parent specifications through a look-up table, of which the highest The interchangeability of pressure resistance or axial segmentation is established. According to the connection mode of "liquid flow flowing in and out from the paraxial annular mouth with annular flow", the symmetrical end cap module is divided into front and rear caps, which will pressurize centripetally. The modules are axially connected in series in sequence, and all the modules are axially combined, that is, a symmetrical cover with variable angles and a centrifugal multi-stage centrifugal booster pump with modular interchangeability are formed. The combination refers to the connection and coordination in the design, assembly and use in production. Interchangeability, interchangeability covers these processes.

49、依据权利要求 29与 48所述的离心泵，其特征是：包含多个半开式叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由半开式叶轮（334) 、叶轮腔盖（333 ) 和向心导轮（335) 组成，后者分别用作前盖（332) 和后盖（340) ，轴向组合成具有模块互换性的对称盖变角出管半开式叶轮向心增压多级离心泵。 49. The centrifugal pump according to claim 29 and 48, comprising: a plurality of semi-open impeller centrifugal booster modules and two variable angle outlet tube symmetrical end cover modules, the former being a semi-open impeller (334 ), Impeller cavity cover (333), and It is composed of a heart guide wheel (335), which is used as a front cover (332) and a rear cover (340), respectively. The axial combination is a symmetrical cover with a modular interchangeability. Centrifugal pump.

50、依据权利要求 30与 48所述的离心泵，其特征是：包含多个闭式叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式叶轮（344) 、叶轮腔盖（343)和向心导轮（345) 组成，后者分别用作前盖（342) 和后盖（349) ，轴向组合成具有模块互换性的对称盖变角出管闭式叶轮向心增压多级离心泵。 50. The centrifugal pump according to claim 30 and 48, comprising: a plurality of closed impeller centrifugal booster modules and two variable-angle outlet pipe symmetrical end cover modules, the former by a closed impeller (344), The impeller cavity cover (343) and the centrifugal guide wheel (345) are used, the latter is used as the front cover (342) and the rear cover (349), respectively, axially combined into a symmetrical cover with modular interchangeable variable angle outlet pipe closure Centrifugal multi-stage centrifugal pump with centrifugal impeller.

51、依据权利要求 31与 48所述的离心泵，其特征是：包含多个减摩闭式叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式叶轮（353) 、叶轮腔盖（352)和向心导轮（354) 及阻气间隙（355) 、二相流入管（356) 、前后端腔连通均压孔（358) 组成，后者分别用作前盖（342)和后盖（349) ，轴向组合成具有模块互换性的对称盖变角出管减摩闭式叶轮向心增压多级离心泵。 51. The centrifugal pump according to claim 31 and 48, comprising: a plurality of anti-friction closed-type impeller centrifugal booster modules and two variable-angle outlet pipe symmetrical end cover modules, the former being a closed impeller (353 ), The impeller cavity cover (352), the centripetal guide wheel (354), the choke gap (355), the two-phase inflow pipe (356), the front and rear cavity communication pressure equalization holes (358), the latter is used as the front The cover (342) and the back cover (349) are axially combined to form a symmetrical cover variable angle outlet tube friction reducing closed impeller multi-stage centrifugal pump with modular interchangeability.

52、依据权利要求 32与 48所述的离心泵，其特征是：包含多个半开式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由半开式均速高势比叶轮（364)、叶轮腔盖（363) 和向心导轮（365) 组成，后者分别用作前盖（362) 和后盖（369) ，轴向组合成具有模块互换性的对称盖变角出管半开式均速高势比叶轮向心增压多级离心泵。 52. The centrifugal pump according to claim 32 and 48, comprising: a plurality of semi-open type constant velocity high-potential ratio impeller centrifugal booster modules and two variable-angle outlet pipe symmetrical end cover modules, the former consists of half Open type average speed high potential ratio impeller (364), impeller cavity cover (363) and centripetal guide wheel (365), the latter is used as the front cover (362) and the rear cover (369) respectively, axially combined to have Module interchangeable symmetrical cover variable angle outlet pipe semi-open type uniform speed high-potential ratio multi-stage centrifugal pump with centrifugal booster.

53、依据权利要求 33与 48所述的离心泵，其特征是：包含多个闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮（374) 、叶轮腔盖（373) 和向心导轮（375) 组成，后者分别用作前盖（372) 和后盖（379) ，轴向组合成具有模块互换性的对称盖变角出管闭式均速高势比叶轮向心增压多级离心泵。 53. The centrifugal pump according to claim 33 and 48, comprising: a plurality of closed-type high-potential ratio impeller centrifugal booster modules and two variable-angle outlet-tube symmetrical end-cap modules, the former being a closed type The uniform speed high potential ratio impeller (374), the impeller cavity cover (373) and the centripetal guide wheel (375), the latter is used as the front cover (372) and the rear cover (379), which are axially combined to have module mutual Multi-stage centrifugal pump with centrifugal pump and centrifugal pump with centrifugal pump, closed-end, closed-velocity, high-potential than the impeller.

54、依据权利要求 34与 48所述的离心泵，其特征是：包含多个预旋闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮（384) 、预旋器（386) 、叶轮腔盖（383)和向心导轮（385) 组成，后者分别用作前盖（382) 和后盖（389) ，轴向组合成具有模块互换性的对称盖变角出管预旋闭式均速高势比叶轮向心增压多级离心泵。 54. The centrifugal pump according to claim 34 and 48, comprising: a plurality of pre-spinning closed-velocity high-potential ratio impeller centrifugal booster modules and two variable-angle outlet pipe symmetrical end cover modules, the former by Closed average speed high potential ratio impeller (384), pre-rotator (386), impeller cavity cover (383) and centrifugal guide wheel (385), the latter is used as the front cover (382) and the rear cover (389 ), Axially combined into a symmetrical cover with variable interchangeability, with a modular cover, a pre-spinning closed-type high-potential ratio centrifugal pump with centrifugal booster.

55、依据权利要求 35与 48所述的离心泵，其特征是：包含多个减摩闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由闭式均速高势比叶轮（394) 、叶轮腔盖（393) 、向心导轮（395) 及阻气间隙（396) 、二相流入管（397) 、前后端腔连通均压孔（398) 组成，后者分别用作前盖（392) 和后盖（399) ，轴向组合成具有模块互换性的对称盖变角出管减摩闭式均速高势比叶轮向心增压多级离心泵。 55. The centrifugal pump according to claim 35 and 48, comprising: a plurality of friction-reducing closed-type high-potential-ratio impeller centrifugal booster modules and two variable-angle outlet-tube symmetrical end-cap modules, the former consists of Closed average speed high potential ratio impeller (394), impeller cavity cover (393), centripetal guide wheel (395) and choke gap (396), two-phase inflow pipe (397), front and rear cavity communication pressure equalization holes ( 398), the latter is used as the front cover (392) and the rear cover (399) respectively, axially combined to form a symmetrical cover with variable modules, variable angle outlet tube, reduced friction, closed average speed, higher potential than the impeller. Pressure multistage centrifugal pump.

56、依据权利要求 36与 48所述的离心泵，其特征是：包含多个减摩预旋闭式均速高势比叶轮向心增压模块和 2 个变角度出管对称端盖模块，前者由闭式均速高势比叶轮 (406) 、预旋器（404) 、叶轮腔盖（403) 、向心导轮（405) 及阻气间隙（408) 、二相流入管（407) 、前后端腔连通均压孔（409) 组成，后者分别用作前盖（402) 和后盖 (410) ，轴向组合成具有模块互换性的对称盖变角出管减摩预旋闭式均速髙势比叶轮向心增压多级离心泵。 56. The centrifugal pump according to claim 36 and 48, comprising: a plurality of friction-reducing pre-spinning type average speed high potential ratio impeller centrifugal booster modules and two variable-angle outlet pipe symmetrical end cover modules, The former consists of a closed-type average speed high potential ratio impeller (406), a prerotator (404), an impeller cavity cover (403), a centripetal guide wheel (405) and an air gap (408), and a two-phase inflow pipe (407). The front and rear chambers are connected by pressure equalizing holes (409). The latter are used as the front cover (402) and the rear cover (410), respectively, and are axially combined to form a symmetrical cover with variable interchangeability. Closed average velocity pseudopotential ratio Cardiac multi-stage centrifugal pump.

57、依据权利要求 37与 48所述的离心泵，其特征是：包含多个超减摩预旋闭式均速高势比叶轮向心增压模块和 2个变角度出管对称端盖模块，前者由带有延伸包覆转移段流道的叶轮盖（418 ) 的闭式均速高势比叶轮（414) 、预旋器（411 ) 、叶轮腔盖（413) 、向心导轮（415) 及阻气间隙（416) 、前端腔减摩驱动二相流入管（417) 、后端腔减摩驱动介质入管（419 ) 组成，后者分别用作前盖（412) 和后盖（420) ，轴向组合成具有模块互换性的对称盖变角出管超减摩预旋闭式均速高势比叶轮向心增压多级离心泵。 57. The centrifugal pump according to claim 37 and 48, comprising: a plurality of super-friction pre-rotational closed-speed high-potential ratio impeller centrifugal booster modules and two variable-angle outlet pipe symmetrical end cover modules The former consists of a closed average speed high potential ratio impeller (414), a pre-rotator (411), an impeller cavity cover (413), and a centripetal guide wheel (414 415) and the air gap (416), the front cavity antifriction driving two-phase inflow pipe (417), the rear cavity antifriction driving medium inlet pipe (419), the latter is used as the front cover (412) and the rear cover ( 420), axially combined into a modular cover interchangeable symmetric cover variable angle outlet tube super friction reduction pre-spin closed uniform speed high potential ratio impeller centrifugal booster multi-stage centrifugal pump.

58、依据权利要求 48所述的离心泵，其特征是：包含多个预旋双半开式均速高势比叶导轮向心增压模块和 2 个变角度出管对称端盖模块，前者由半开式均速高势比叶轮 58. The centrifugal pump according to claim 48, comprising: a plurality of pre-spinning double-half-opening average speed high-potential ratio guide wheel centrifugal booster modules and two variable-angle outlet pipe symmetrical end cover modules, The former consists of a half-open type average speed high potential ratio impeller

(424) 、叶轮腔盖（423) 、半开式向心导轮（425) 和预旋器（428) 组成，后者分别用作前盖（422)和后盖（429) ，轴向组合成具有模块互换性的对称盖变角出管双半开式均速高势比叶导轮向心增压多级离心泵。 (424), impeller cavity cover (423), semi-open centripetal guide wheel (425) and pre-spinner (428), the latter is used as the front cover (422) and the rear cover (429), respectively, axial combination It has a modular interchangeable symmetric cover variable angle outlet pipe double semi-open type uniform speed high potential ratio vane guide wheel centrifugal booster multi-stage centrifugal pump.