WO2024114297A1

WO2024114297A1 - Power end housing for plunger pump and plunger pump comprising power end housing

Info

Publication number: WO2024114297A1
Application number: PCT/CN2023/129658
Authority: WO
Inventors: 姚君磊; 王�锋; 马骁; 姜一博
Original assignee: 烟台杰瑞石油服务集团股份有限公司
Priority date: 2022-11-30
Filing date: 2023-11-03
Publication date: 2024-06-06

Abstract

The present invention provides a power end housing for a plunger pump and a plunger pump comprising the power end housing. The power end housing comprises an integrated crankcase (100); the crankcase (100) comprises a plurality of bearing blocks (101) and a plurality of supporting vertical plates (102); the supporting vertical plates (102) are used for supporting the bearing blocks (101), and the supporting vertical plates (102) are spaced in the axis direction of the bearing blocks (101); the crankcase (100) comprises first reinforcing ribs (103) between the supporting vertical plates (102); the included angle between the direction of the maximum resultant force borne by the bearing blocks (101) and the axial direction of a plunger of a plunger pump is βmax, the included angle between the first reinforcing ribs (103) and the axial direction of the plunger is a first included angle, and the first included angle is greater than or equal to 0.8 βmax and less than or equal to 1.2 βmax. According to the present invention, the service life of the plunger pump is prolonged.

Description

一种用于柱塞泵的动力端壳体和包含该动力端壳体的柱塞泵A power end housing for a plunger pump and a plunger pump including the power end housing

相关申请的交叉引用CROSS-REFERENCE TO RELATED APPLICATIONS

本申请要求于2022年11月30日向中国国家知识产权局提交的第202211521034.6号中国专利申请、于2022年12月19日提交的第PCT/CN2022/140075号PCT专利申请、于2023年3月3日向中国国家知识产权局提交的第202310225825.2号中国专利申请、于2023年7月26日向中国国家知识产权局提交的第202310923050.6号中国专利申请、于2023年7月26日向中国国家知识产权局提交的第202310923013.5号中国专利申请的优先权和权益，所述申请公开的内容通过引用整体并入本文中。This application claims the priority and rights of Chinese Patent Application No. 202211521034.6 filed with the State Intellectual Property Office of China on November 30, 2022, PCT Patent Application No. PCT/CN2022/140075 filed on December 19, 2022, Chinese Patent Application No. 202310225825.2 filed with the State Intellectual Property Office of China on March 3, 2023, Chinese Patent Application No. 202310923050.6 filed with the State Intellectual Property Office of China on July 26, 2023, and Chinese Patent Application No. 202310923013.5 filed with the State Intellectual Property Office of China on July 26, 2023, and the contents disclosed in the said applications are incorporated herein by reference in their entirety.

技术领域Technical Field

本发明涉及油气开采技术领域，尤其涉及一种用于柱塞泵的动力端壳体，特别是一体式曲轴箱，以及包含该动力端壳体的柱塞泵。The present invention relates to the technical field of oil and gas exploitation, and in particular to a power end housing for a plunger pump, in particular an integrated crankcase, and a plunger pump comprising the power end housing.

背景技术Background technique

往复泵通常用于采矿和油田应用，例如水力压裂。在压裂过程中，压裂液(即水泥、泥浆、压裂砂和其他材料)在高压下被泵入井筒中使生产地层破裂。水力压裂中常用的一种泵是压裂泵，例如SPM的US 11,204,030B2和KERR的US 2022/0163034A1中所描述的。Reciprocating pumps are commonly used in mining and oilfield applications, such as hydraulic fracturing. During the fracturing process, fracturing fluid (i.e., cement, mud, fracturing sand, and other materials) is pumped into a wellbore at high pressure to fracture the producing formation. One type of pump commonly used in hydraulic fracturing is a fracturing pump, such as described in US 11,204,030 B2 to SPM and US 2022/0163034 A1 to KERR.

压裂泵作为可以提高油气产量的重要设备而在石油行业广泛应用。近年来，压裂设备使油田生产率不断提高。它在一些中后期的老油田增产中、开发新油田中以及在新兴页岩气开发中扮演着重要的角色。Fracturing pumps are widely used in the oil industry as important equipment that can increase oil and gas production. In recent years, fracturing equipment has continuously improved oil field productivity. It plays an important role in increasing production in some mid-to-late-stage old oil fields, developing new oil fields, and developing emerging shale gas.

压裂泵主要由动力端、液力端、齿轮减速箱这三大子***组成。动力端结构上负责连接减速箱与液力端阀箱两个子***，功能上负责将减速箱传递过来的旋转机械能转化为往复机械能，以驱动液力端的吸排液功能；液力端的功能是负责将低压流体加压到高压流体，输出到高压管汇；减速箱的功能是负责将动力源(包括但不限于柴油机、电机、涡轮机等)输入的高转速低扭矩经过多级减速转化为低转速高扭矩，然后输入到动力端。由于受到空间布置的限制且要方便拆装维修，压裂泵多数为卧式直列结构，即动力端往复运动部件中心线为水平布置，并与加压腔体中心轴平行。The fracturing pump is mainly composed of three subsystems: the power end, the hydraulic end, and the gear reducer. The power end is responsible for connecting the two subsystems of the reducer and the hydraulic end valve box. Functionally, it is responsible for converting the rotational mechanical energy transmitted by the reducer into reciprocating mechanical energy to drive the suction and discharge function of the hydraulic end; the function of the hydraulic end is to pressurize the low-pressure fluid into high-pressure fluid and output it to the high-pressure manifold; the function of the reducer is to convert the high-speed and low-torque input from the power source (including but not limited to diesel engines, motors, turbines, etc.) into low-speed and high-torque through multiple stages of reduction, and then input it to the power end. Due to the limitations of space layout and the need for easy disassembly and maintenance, most fracturing pumps are horizontal inline structures, that is, the center line of the reciprocating motion parts of the power end is horizontally arranged and parallel to the center axis of the pressurized chamber.

动力端总成主要由壳体、曲柄连杆总成、十字头拉杆总成及润滑***等组成。动力端壳体包括曲轴箱和十字头箱，曲轴箱与十字头箱的一端相连，十字头箱的另一端通过连接装置连接到液力端的泵头体。对于五缸压裂泵，曲轴常为六支撑五曲拐型式的整体式结构，由重型圆柱滚子轴承支撑，为超静定结构，在各曲拐处钻有相联通的油道，以润滑连杆轴瓦。The power end assembly is mainly composed of a housing, a crank-connecting rod assembly, a crosshead tie rod assembly and a lubrication system. The power end housing includes a crankcase and a crosshead case. The crankcase is connected to one end of the crosshead case, and the other end of the crosshead case is connected to the pump head body of the hydraulic end through a connecting device. For a five-cylinder fracturing pump, the crankshaft is usually a six-support five-crank type. The integral structure is supported by heavy cylindrical roller bearings. It is a statically indeterminate structure with interconnected oil passages drilled in each crank to lubricate the connecting rod bearing.

动力端壳体作为压裂泵的关键部件，用于搭载动力端所有零部件，并承载着动力端所有零部件在工作中所带来的所有荷载。因此，良好的壳体机械性能对压裂泵使用寿命有决定性影响。按照壳体结构组成方式不同，动力端壳体可分为整体式和分体式结构。As a key component of the fracturing pump, the power end housing is used to carry all the components of the power end and bear all the loads brought by all the components of the power end during operation. Therefore, good housing mechanical properties have a decisive influence on the service life of the fracturing pump. According to the different housing structure composition methods, the power end housing can be divided into integral and split structures.

当前市面上动力端整体式壳体常采用拼焊结构以满足压裂泵功能与性能的要求。其动力端壳体多采用高强度合金板焊接而成，通过点焊基本及整体框架，框架组对后预热加焊接，热处理(去应力退火)，粗加工，缺陷打磨，再次整体焊接及焊件热处理、检测后才算完成。At present, the integral power end housing on the market often adopts a welded structure to meet the requirements of the function and performance of the fracturing pump. The power end housing is mostly welded with high-strength alloy plates, and the basic and overall frames are spot welded. The frame assembly is preheated and welded, heat treated (stress relief annealing), rough machined, defect polished, and then the overall welding and weldment heat treatment and testing are completed.

对于动力端分体式壳体通常采用部分焊接制成。对于动力端分体式壳体，除了拼焊外，极少厂家采用分体铸造方式，如KERR的US 2022/0163034 A1采用分体式铸造的方式，但此种设计也有一些缺点：虽然采用了大量的减重设计，但未充分发挥铸造优势，整体壳体依旧太重，不便运输及组装。整泵支撑点位置及数量设计不妥，导致支撑点受力集中，整泵强度及刚度易失效。动力端部分跨度太大，组件较为分散，十字头结构设计体积较大，造成运行时动力端所受力矩较大，减少了压裂泵的使用寿命；动力端组件整体刚度大部分由多组螺栓和连杆提供，整体结构刚度差；整体动力端密封性较差，易产生油气泄露。The split housing of the power end is usually made by partial welding. For the split housing of the power end, in addition to welding, very few manufacturers use split casting. For example, KERR's US 2022/0163034 A1 adopts split casting, but this design also has some disadvantages: although a large number of weight reduction designs are adopted, the advantages of casting are not fully utilized, and the overall housing is still too heavy, which is inconvenient to transport and assemble. The position and number of support points of the entire pump are not properly designed, resulting in concentrated force on the support points, and the strength and rigidity of the entire pump are prone to failure. The span of the power end is too large, the components are relatively dispersed, and the crosshead structure is designed to be large in volume, resulting in a large torque on the power end during operation, reducing the service life of the fracturing pump; most of the overall rigidity of the power end components is provided by multiple sets of bolts and connecting rods, and the overall structural rigidity is poor; the overall power end has poor sealing, which is prone to oil and gas leakage.

良好的动力端总体结构及布局设计决定了泵的刚性及强度能够满足作业要求。在此基础上，液力端和减速箱才能平稳运行。A good overall structure and layout design of the power end determines that the rigidity and strength of the pump can meet the operating requirements. On this basis, the hydraulic end and the reduction box can operate smoothly.

随着国内外油田开采工况朝着高压力和大排量的趋势发展，对压裂泵结构的可靠性、维护保养的便利性、设计的轻量化等方面提出了越来越高的要求。为适应未来压裂作业的发展趋势，压裂泵正在向高压力、大功率、大排量、结构紧凑、持续工作时间长、维护成本低等特点的方向发展。As domestic and foreign oilfield production conditions develop towards high pressure and large displacement, higher and higher requirements are put forward for the reliability of fracturing pump structure, convenience of maintenance, lightweight design, etc. In order to adapt to the development trend of future fracturing operations, fracturing pumps are developing in the direction of high pressure, high power, large displacement, compact structure, long continuous working time, and low maintenance cost.

通常，压裂泵的应用场景和运行环境非常恶劣，往返井场运输时路况复杂，车辆连续颠簸使壳体受到震动和冲击，在压裂作业的长时间高负载运行时，泵输送压力高达10000～20,000psi左右的流体或浆液，动力端壳体会受到高压力周期性脉冲载荷。由于这种极端的运行条件，同时焊接式动力端壳体抗冲击性能较差，极容易在焊缝附近产生裂纹，进而造成壳体开裂，最终导致支撑功能失效，影响压裂作业效率，甚至带来安全隐患。目前存在的焊接式动力端壳体寿命至多2000到3000小时，一次故障经返修后也难以超过***设计寿命(5000小时)。 Generally, the application scenarios and operating environments of fracturing pumps are very harsh. The road conditions are complicated when transporting to and from the well site, and the continuous bumping of the vehicle causes the shell to vibrate and impact. During the long-term high-load operation of the fracturing operation, the pump delivers fluid or slurry with a pressure of up to 10,000 to 20,000 psi, and the power end shell will be subjected to high-pressure periodic pulse loads. Due to such extreme operating conditions, and the poor impact resistance of the welded power end shell, it is very easy to crack near the weld, which in turn causes the shell to crack, and ultimately leads to the failure of the support function, affecting the efficiency of the fracturing operation, and even posing a safety hazard. The current life of the welded power end shell is at most 2,000 to 3,000 hours, and it is difficult to exceed the system design life (5,000 hours) after a single failure is repaired.

柱塞泵是油田泵注设备的核心部件之一，其通过柱塞在缸体内往复运动，使缸体内工作容积交替增加和缩小，以输送工作液体。The plunger pump is one of the core components of oilfield pumping equipment. The plunger reciprocates in the cylinder, causing the working volume in the cylinder to increase and decrease alternately to transport the working fluid.

随着目前油田工作要求越来越高，工况越来越恶劣，对柱塞泵的功率、压力、排量的要求不断提高，连续工作时间也在不断延长，因此相关技术中对可能影响柱塞泵使用寿命的柱塞泵的强度以及诸如部件之间的连接可靠性等柱塞泵的稳定性方面提出了越来越高的要求。例如，为了解决上面所描述的现有技术中所存在柱塞泵的强度不足，从而导致寿命不够长的问题，急需开发一种高强度、高稳定性和可靠性的新型柱塞泵来解决目前的作业需求。As the requirements for oil field work are getting higher and higher, and the working conditions are getting worse and worse, the requirements for the power, pressure, and displacement of the plunger pump are constantly increasing, and the continuous working time is also constantly extending. Therefore, the relevant technology has put forward higher and higher requirements on the strength of the plunger pump that may affect the service life of the plunger pump, as well as the stability of the plunger pump such as the reliability of the connection between components. For example, in order to solve the problem of insufficient strength of the plunger pump in the prior art described above, which leads to insufficient life, it is urgent to develop a new type of plunger pump with high strength, high stability and reliability to solve the current operation needs.

发明内容Summary of the invention

为了延长柱塞泵的使用寿命，需要进一步提高柱塞泵的稳定性和强度，特别是柱塞泵各组件之间的连接可靠性以及柱塞泵壳体的机械强度。特别地，在柱塞泵中，曲轴箱中的轴承座与所支撑的轴承之间的连接可靠性或支撑可靠性也是衡量柱塞泵的稳定性的一个重要方面。一方面，在轴承座的宽度大于所支撑的轴承的宽度时，较宽的轴承座会占用更多曲轴箱内部空间，同时还会使得曲轴箱整体重量增大，不利于柱塞泵轻量化设计的需求；另一方面，在轴承座的宽度小于所支撑的轴承的宽度时，轴承座不能可靠地支撑轴承，导致支撑可靠性较差。轴承座与所支撑的轴承之间需要合适的宽度设计才能使得其间的连接可靠性最大化。In order to extend the service life of the plunger pump, it is necessary to further improve the stability and strength of the plunger pump, especially the connection reliability between the various components of the plunger pump and the mechanical strength of the plunger pump housing. In particular, in the plunger pump, the connection reliability or support reliability between the bearing seat in the crankcase and the supported bearing is also an important aspect of measuring the stability of the plunger pump. On the one hand, when the width of the bearing seat is greater than the width of the supported bearing, the wider bearing seat will occupy more space inside the crankcase, and at the same time, it will increase the overall weight of the crankcase, which is not conducive to the demand for lightweight design of the plunger pump; on the other hand, when the width of the bearing seat is less than the width of the supported bearing, the bearing seat cannot reliably support the bearing, resulting in poor support reliability. A suitable width design is required between the bearing seat and the supported bearing to maximize the connection reliability between them.

为了解决上面提到的技术问题，提高柱塞泵的稳定性和强度，本申请的发明人设计了一种全新形式的压裂泵动力端壳体，其整体重量小、强度得到了很大提升、在关键配合部位变形小并且组件之间的连接可靠性得到了提高，使得抗弯扭、缓冲抗震性能较好、抗缺口敏感度低。另外，极大简化了制造工序，缩减了时间、人工和原材料成本。配合这种壳体改进优化各类泵组件，能够形成一种颠覆性的压裂泵设备。In order to solve the technical problems mentioned above and improve the stability and strength of the plunger pump, the inventor of this application has designed a new form of fracturing pump power end housing, which has a small overall weight, greatly improved strength, small deformation at key matching parts, and improved connection reliability between components, so that it has good bending and torsion resistance, buffering and shock resistance, and low sensitivity to notches. In addition, the manufacturing process is greatly simplified, reducing time, labor and raw material costs. With this housing, various pump components can be improved and optimized to form a subversive fracturing pump equipment.

根据本发明的第一方面，提供了一种用于柱塞泵的动力端壳体，包括：一体式曲轴箱，所述曲轴箱包括多个轴承座和多个支撑立板，所述支撑立板用于支撑所述轴承座，且所述支撑立板沿所述轴承座的轴线方向间隔排布，所述曲轴箱在各个所述支撑立板之间包括第一加强筋，其中所述轴承座所受最大合力的方向与所述柱塞泵的柱塞的轴向方向之间的夹角为βmax，并且所述第一加强筋与所述柱塞的轴向方向之间的夹角为第一夹角，所述第一夹角大于或等于0.8βmax，且小于或等于1.2βmax。According to a first aspect of the present invention, there is provided a power end housing for a plunger pump, comprising: an integrated crankcase, the crankcase comprising a plurality of bearing seats and a plurality of support plates, the support plates being used to support the bearing seats, and the support plates being arranged at intervals along the axial direction of the bearing seats, the crankcase comprising a first reinforcing rib between each of the support plates, wherein the angle between the direction of the maximum resultant force on the bearing seat and the axial direction of the plunger of the plunger pump is βmax, and the angle between the first reinforcing rib and the axial direction of the plunger is a first angle, and the first angle is greater than or equal to 0.8βmax and less than or equal to 1.2βmax.

进一步地，其中，所述第一加强筋至少设置于所述曲轴箱的前端面和/或后端面上，所述前端面是所述曲轴箱的与十字头箱连接侧的表面，并且所述后端面是所述前端面的相对侧的表面。Furthermore, wherein the first reinforcing rib is at least arranged on the front end surface and/or the rear end surface of the crankcase, the front end surface is the surface of the crankcase on the side connected to the crosshead case, and the rear end surface is the front end surface of the crankcase. The surface on the opposite side of the end face.

进一步地，其中，在所述前端面和所述后端面上分别设置有一组所述第一加强筋，并且每组内的所述第一加强筋相对于所述柱塞泵的柱塞的轴向方向彼此对称。Furthermore, a group of the first reinforcing ribs is respectively provided on the front end surface and the rear end surface, and the first reinforcing ribs in each group are symmetrical to each other with respect to the axial direction of the plunger of the plunger pump.

进一步地，其中，设置于所述前端面上的所述一组第一加强筋与设置于所述后端面上的所述一组第一加强筋相对于所述轴承座的垂直中心线彼此对称。Furthermore, the group of first reinforcing ribs arranged on the front end surface and the group of first reinforcing ribs arranged on the rear end surface are symmetrical to each other relative to the vertical center line of the bearing seat.

进一步地，其中，每组所述第一加强筋包括两个所述第一加强筋，所述两个第一加强筋的延伸方向之间的夹角大于或等于1.8βmax，且小于或等于2.2βmax。Furthermore, each group of the first reinforcing ribs includes two first reinforcing ribs, and the angle between the extension directions of the two first reinforcing ribs is greater than or equal to 1.8βmax and less than or equal to 2.2βmax.

进一步地，其中，所述曲轴箱还在各个所述支撑立板之间包括多个第二加强筋，并且所述第二加强筋的延伸方向通过所述轴承座的圆心。Furthermore, the crankcase further includes a plurality of second reinforcing ribs between each of the supporting vertical plates, and the extending direction of the second reinforcing ribs passes through the center of the bearing seat.

进一步地，其中，所述多个第二加强筋沿着所述轴承座的座孔对称布置。Furthermore, the plurality of second reinforcing ribs are symmetrically arranged along the seat hole of the bearing seat.

进一步地，其中，所述多个第二加强筋在所述轴承座的上下两侧布置，其中在上侧布置有三个上侧加强筋并且在下侧布置有两个下侧加强筋，所述两个下侧加强筋的位置分别位于底部回油口的两侧而不与所述底部回油口产生干扰。Furthermore, the plurality of second reinforcing ribs are arranged on the upper and lower sides of the bearing seat, wherein three upper reinforcing ribs are arranged on the upper side and two lower reinforcing ribs are arranged on the lower side, and the positions of the two lower reinforcing ribs are respectively located on both sides of the bottom oil return port without interfering with the bottom oil return port.

进一步地，其中，所述第一加强筋和/或所述第二加强筋与所述支撑立板之间设置有过渡坡口，并且所述坡口与所述支撑立板之间具有过渡圆角。Furthermore, a transition groove is provided between the first reinforcing rib and/or the second reinforcing rib and the supporting vertical plate, and a transition fillet is provided between the groove and the supporting vertical plate.

根据本发明的第二方面，提供了一种用于柱塞泵的动力端壳体，包括：一体式曲轴箱，所述曲轴箱包括多个轴承座和多个支撑立板，所述支撑立板用于支撑所述轴承座，且所述支撑立板沿所述轴承座的轴线方向间隔排布，其中所述轴承座的宽度由施加在所述轴承座上的轴承的宽度限定。According to a second aspect of the present invention, a power end housing for a plunger pump is provided, comprising: an integrated crankcase, the crankcase comprising a plurality of bearing seats and a plurality of support plates, the support plates being used to support the bearing seats, and the support plates being arranged at intervals along the axial direction of the bearing seats, wherein the width of the bearing seats is limited by the width of the bearings applied to the bearing seats.

进一步地，其中，所述轴承座包括位于所述曲轴箱的两端的两个端部轴承座以及若干个中段轴承座，所述中段轴承座位于所述两个端部轴承座之间，其中各个所述中段轴承座的宽度大于所述两个端部轴承座中的每一个的宽度。Furthermore, the bearing seat includes two end bearing seats located at both ends of the crankcase and a plurality of middle bearing seats, wherein the middle bearing seat is located between the two end bearing seats, wherein the width of each middle bearing seat is greater than the width of each of the two end bearing seats.

进一步地，其中，所述两个端部轴承座中的位于所述曲轴箱的减速箱连接侧的一个端部轴承座的宽度比所述两个端部轴承座中的另一个端部轴承座的宽度宽。Furthermore, the width of one of the two end bearing seats, which is located at the reduction gearbox connection side of the crankcase, is wider than the width of the other end bearing seat of the two end bearing seats.

进一步地，其中，所述支撑立板之间的间距不同，并且相对于所述曲轴箱的长度方向的中心，所述支撑立板之间的间距设置成对称，所述长度方向与所述轴承座的轴线方向平行。Furthermore, the spacings between the support vertical plates are different, and are symmetrical relative to the center of the length direction of the crankcase, and the length direction is parallel to the axial direction of the bearing seat.

进一步地，根据本发明的第一方面和第二方面的动力端壳体，在所述支撑立板上设置有减重凹槽。Further, according to the power end housing of the first aspect and the second aspect of the present invention, a weight-reducing groove is provided on the supporting vertical plate.

进一步地，根据本发明的第一方面和第二方面的动力端壳体，在所述支撑立板的顶部设置有吊点凸台，并且所述吊点凸台与所述曲轴箱的箱体连接处设置有过渡圆角。Further, according to the power end housing of the first aspect and the second aspect of the present invention, a hanging point boss is provided on the top of the supporting vertical plate, and a transition is provided at the connection between the hanging point boss and the crankcase body. Rounded corners.

进一步地，根据本发明的第一方面和第二方面的动力端壳体，所述曲轴箱的底部包括支脚，所述支脚用于支撑所述曲轴箱。Further, according to the power end housing of the first aspect and the second aspect of the present invention, the bottom of the crankcase includes feet, and the feet are used to support the crankcase.

进一步地，根据本发明的第一方面和第二方面的动力端壳体，在所述曲轴箱的靠近十字头箱侧的表面上设置有多个第一螺纹孔，所述第一螺纹孔用于通过第一螺栓将所述曲轴箱与所述十字头箱连接。Further, according to the power end housing of the first and second aspects of the present invention, a plurality of first threaded holes are provided on the surface of the crankcase close to the crosshead case side, and the first threaded holes are used to connect the crankcase to the crosshead case by first bolts.

进一步地，根据本发明的第一方面和第二方面的动力端壳体，所述曲轴箱是一体铸造成型的。Further, according to the power end housing of the first aspect and the second aspect of the present invention, the crankcase is integrally cast.

根据本发明的第三方面，提供了一种柱塞泵，所述柱塞泵包括上述根据本发明的第一方面和第二方面的动力端壳体。According to a third aspect of the present invention, there is provided a plunger pump, the plunger pump comprising the power end housing according to the first and second aspects of the present invention.

进一步地，柱塞泵还包括液力端壳体，并且所述动力端壳体还包括十字头箱，所述液力端壳体、所述十字头箱和曲轴箱依次连接，其中第一螺纹孔能够从所述液力端壳体贯穿到所述曲轴箱，并且第一螺栓能够通过所述第一螺纹孔将所述液力端壳体、所述十字头箱和曲轴箱连接在一起。Furthermore, the plunger pump also includes a hydraulic end housing, and the power end housing also includes a crosshead box, the hydraulic end housing, the crosshead box and the crankcase are connected in sequence, wherein a first threaded hole can pass through the hydraulic end housing to the crankcase, and a first bolt can connect the hydraulic end housing, the crosshead box and the crankcase together through the first threaded hole.

本发明采用的技术方案能够达到以下有益效果：The technical solution adopted by the present invention can achieve the following beneficial effects:

根据本发明公开的动力端壳体，能够提高轴承座和所支撑的轴承之间的连接可靠性和支撑可靠性，提高了柱塞泵的稳定性，能够有效地抵抗柱塞泵对曲轴箱的冲击力，进而避免支撑立板发生相对变形的风险，促使动力端壳体具有较高的强度和刚度。根据本发明公开的动力端壳体的使用寿命超过8000小时，甚至能够超过10000小时，是现有技术中动力端壳体使用寿命的两倍左右或两倍以上。The power end housing disclosed in the present invention can improve the connection reliability and support reliability between the bearing seat and the supported bearing, improve the stability of the plunger pump, and effectively resist the impact force of the plunger pump on the crankcase, thereby avoiding the risk of relative deformation of the supporting vertical plate, and promoting the power end housing to have higher strength and rigidity. The service life of the power end housing disclosed in the present invention exceeds 8,000 hours, and can even exceed 10,000 hours, which is about twice or more than twice the service life of the power end housing in the prior art.

附图说明BRIEF DESCRIPTION OF THE DRAWINGS

此处所说明的附图用来提供对本发明的进一步理解，构成本发明的一部分，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。在附图中：The drawings described herein are used to provide a further understanding of the present invention and constitute a part of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

图1示出了根据本发明一个实施例的一体式曲轴箱的立体图，其中示出了曲轴箱的前端面；FIG1 is a perspective view of an integrated crankcase according to an embodiment of the present invention, wherein the front end face of the crankcase is shown;

图2示出了根据本发明一个实施例的一体式曲轴箱的另一个立体图，其中示出了曲轴箱的后端面；FIG2 shows another perspective view of the integrated crankcase according to one embodiment of the present invention, showing the rear end face of the crankcase;

图3示出了安装有曲轴的曲轴箱的截面图；FIG3 shows a cross-sectional view of a crankcase with a crankshaft installed;

图4示出了安装有曲轴的曲轴箱的部分切割立体图； FIG4 shows a partially cutaway perspective view of a crankcase with a crankshaft installed;

图5示出了两端轴承座和主轴承的受力曲线图；FIG5 shows a force curve diagram of the bearing seats at both ends and the main bearing;

图6示出了中段轴承座和主轴承的受力曲线图；FIG6 shows a force curve diagram of the middle bearing seat and the main bearing;

图7示出了曲轴箱的立体图，其中示出了吊点凸台和油气分离器凸台；FIG7 shows a perspective view of the crankcase, showing the suspension point boss and the oil-gas separator boss;

图8示出了吊点凸台部分的局部放大图；FIG8 shows a partial enlarged view of the suspension point boss portion;

图9是示出了曲轴箱的显示了工艺通孔和轴承挡板螺纹孔的位置的立体图；9 is a perspective view showing the crankcase showing the position of the process through hole and the threaded hole of the bearing baffle;

图10是示出了曲轴箱的在支撑立板的截面上显示了工艺通孔和轴承挡板螺纹孔的位置的立体图；10 is a perspective view showing the position of the process through hole and the threaded hole of the bearing baffle on the cross section of the support plate of the crankcase;

图11示出了支撑立板之间的一个加强筋的局部放大图；FIG11 shows a partial enlarged view of a reinforcing rib between supporting uprights;

图12示出了曲轴和柱塞的运动结构简化的曲柄连杆结构的示意图和受力分析图；FIG12 shows a schematic diagram and a force analysis diagram of a crank-connecting rod structure with a simplified kinematic structure of a crankshaft and a plunger;

图13示出了加强筋的布置以及连杆摆角的图示；FIG13 shows the arrangement of the reinforcing ribs and a diagram of the swing angle of the connecting rod;

图14是示出了曲轴箱的前端面以及连杆通孔和排油通孔的平面图以及排油通孔的放大图；14 is a plan view showing the front end surface of the crankcase and the connecting rod through-hole and the oil drain through-hole and an enlarged view of the oil drain through-hole;

图15是示出了曲轴箱与十字头箱一起连接在底橇上的立体图，其中示出了曲轴箱的多个支脚；FIG15 is a perspective view showing a crankcase connected to a bottom skid together with a crosshead case, showing a plurality of legs of the crankcase;

图16是示出了在一个支撑立板底部布置了多个支脚的曲轴箱的部分立体图；FIG16 is a partial perspective view showing a crankcase with a plurality of legs arranged at the bottom of a support plate;

图17是示出了横向一体式支脚和纵向一体式支脚的曲轴箱的立体图；17 is a perspective view of a crankcase showing a lateral integral support leg and a longitudinal integral support leg;

图18示出了支脚的局部放大图；FIG18 shows a partial enlarged view of the support foot;

图19是曲轴箱的示出了整个轴承座孔的一侧的截面图；Fig. 19 is a cross-sectional view of one side of the crankcase showing the entire bearing seat bore;

图20示出了曲轴箱的切割立体图，其中示出了在曲轴箱的顶部设置的多个油气分离器凸台的部分切割图；FIG20 shows a cutaway perspective view of a crankcase, showing a partial cutaway view of a plurality of oil-gas separator bosses disposed on the top of the crankcase;

图21示出了从下方看到的曲轴箱的立体图；Fig. 21 shows a perspective view of the crankcase seen from below;

图22示出了曲轴箱和回油口盖板未安装状态的立体图；FIG22 shows a perspective view of the crankcase and the oil return port cover plate in an unmounted state;

图23和图24分别示出了曲轴箱上的各个工艺窗；Figures 23 and 24 show the various process windows on the crankcase respectively;

图25示出了曲轴箱的后端面安装了盖板的状态；FIG25 shows a state where a cover plate is installed on the rear end surface of the crankcase;

图26示出了曲轴箱与十字头箱将要通过螺栓进行连接之前的立体图；FIG26 shows a perspective view of the crankcase and the crosshead case before being connected by bolts;

图27示出了曲轴箱与十字头箱将要通过螺栓进行连接之前的从另一个角度看到的立体图；FIG27 shows a perspective view from another angle before the crankcase and the crosshead case are connected by bolts;

图28是曲轴箱100的在截面中示出了两道螺纹孔的侧面图以及两道螺纹孔的局部放大图；FIG28 is a side view of the crankcase 100 showing two threaded holes in cross section and a partial enlarged view of the two threaded holes;

图29示出了曲轴箱与十字头箱通过两道螺栓连接在一起的截面图；Fig. 29 shows a cross-sectional view of the crankcase and the crosshead case connected together by two bolts;

图30示出了图29所示的两道螺栓连接的局部放大图； FIG30 shows a partial enlarged view of the two bolt connections shown in FIG29 ;

图31示出了两道螺栓一对一布置的局部图；FIG31 shows a partial view of two bolts arranged one to one;

图32示出了两道螺栓一对二布置的局部图；Fig. 32 shows a partial view of a one-to-two arrangement of two bolts;

图33示出了两道螺栓布置位置之间的关系的平面图Figure 33 shows a plan view of the relationship between the two bolt arrangement positions

图34示出了在曲轴箱与十字头箱的连接端面上设置的密封槽；FIG34 shows a sealing groove provided on the connecting end surface of the crankcase and the crosshead case;

图35为曲轴转角与主轴承压力角的示意图；FIG35 is a schematic diagram of the crankshaft angle and the main bearing pressure angle;

图36为曲轴转角与主轴承合力的示意图；FIG36 is a schematic diagram of the crankshaft angle and the main bearing force;

图37为压力角与主轴承合力的示意图。Figure 37 is a schematic diagram of the pressure angle and the main bearing force.

附图标记列表：
100：曲轴箱；200：十字头箱；101：轴承座；102：支撑立板；103,103’：加强
筋；104：顶部；105：底部；106：前端面；107：后端面；109：减重凹槽；110：吊点凸台；111：吊点；112：工艺通孔；113：螺纹孔；114：铝塞；115：过渡坡口；116：过渡圆角；117：连杆通孔；118：排油通孔；119,119’,119”：支脚；120：坡口；121：减重凹槽；122：盖板；123：支脚底部接触面；124：地脚螺纹孔；125：油气分离器凸台；126：回油口；127：回油盖板安装凸台；128：一体式盖板；129,129’：工艺窗；130：凹台；131：第一螺栓；132：第二螺栓；133：密封槽；141：第一螺纹孔；142：第二螺纹孔；211：十字头瓦腔；500：底橇。List of reference numerals:
100: crankcase; 200: crosshead case; 101: bearing seat; 102: support plate; 103, 103': reinforcement rib; 104: top; 105: bottom; 106: front face; 107: rear face; 109: weight reduction groove; 110: hanging point boss; 111: hanging point; 112: process through hole; 113: threaded hole; 114: aluminum plug; 115: transition groove; 116: transition fillet; 117: connecting rod through hole; 118: oil drain through hole; 119, 119', 119" : Support foot; 120: Bevel; 121: Weight reduction groove; 122: Cover plate; 123: Contact surface of bottom of support foot; 124: Threaded hole of anchor; 125: Oil-gas separator boss; 126: Oil return port; 127: Oil return cover plate mounting boss; 128: Integrated cover plate; 129, 129': Process window; 130: Concave platform; 131: First bolt; 132: Second bolt; 133: Sealing groove; 141: First threaded hole; 142: Second threaded hole; 211: Crosshead bearing cavity; 500: Bottom skid.

具体实施方式Detailed ways

为使本发明的目的、技术方案和优点更加清楚，下面将结合本发明具体实施例及相应的附图对本发明技术方案进行清楚、完整地描述。显然，所描述的实施例仅是本发明一部分实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本发明保护的范围。In order to make the purpose, technical solution and advantages of the present invention clearer, the technical solution of the present invention will be clearly and completely described below in combination with the specific embodiments of the present invention and the corresponding drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

以下结合附图，详细说明本发明各个实施例公开的技术方案。为了简要的目的，各个部件的附图标记不一定在各个附图中都示出。通常，为了强调的目的，有些附图仅示出了在说明书中参照该附图所描述的相关部件的附图标记，而省略了其他部件的相关标记，但是在不同的附图中对于相同的部件相同的附图标记是通用。相同或相似的部件有时候为了加以区分以方便说明会给该附图标记加上单引号的右上标后缀，这只是为了便于说明，并且在无需区分它们时，可以省略该后缀。The technical solutions disclosed in various embodiments of the present invention are described in detail below in conjunction with the accompanying drawings. For the purpose of brevity, the figure marks of each component are not necessarily shown in each figure. Usually, for the purpose of emphasis, some figures only show the figure marks of the relevant components described with reference to the figure in the specification, and omit the relevant marks of other components, but the same figure marks are universal for the same components in different figures. Sometimes, in order to distinguish the same or similar components for the convenience of description, a single quotation mark superscript suffix is added to the figure mark, which is only for the convenience of description, and the suffix can be omitted when there is no need to distinguish them.

本发明的实施例公开了一种用于柱塞泵的动力端壳体，动力端壳体是柱塞泵的动力端的安装基础。柱塞泵的动力端负责连接减速箱与液力端阀箱，以将减速箱传递的旋转机械能转换为往复机械能，以驱动液力端的吸排液功能。所公开的动力端壳体包括曲轴箱100。当然所述动力端壳体还可以包括十字头箱200。The embodiment of the present invention discloses a power end housing for a plunger pump, which is the installation base of the power end of the plunger pump. The power end of the plunger pump is responsible for connecting the reduction box and the hydraulic end valve box to transfer the hydraulic pressure transmitted by the reduction box to the hydraulic pressure of the plunger pump. The rotary mechanical energy is converted into reciprocating mechanical energy to drive the suction and discharge functions of the hydraulic end. The disclosed power end housing includes a crankcase 100. Of course, the power end housing may also include a crosshead housing 200.

曲轴箱100用于安装和支撑曲轴，曲轴在曲轴箱100内转动。十字头箱200开设有十字头瓦腔，十字头瓦腔内安装有十字头，柱塞带动十字头在十字头瓦腔内进行往复运动。The crankcase 100 is used to install and support the crankshaft, and the crankshaft rotates in the crankcase 100. The crosshead case 200 is provided with a crosshead bearing cavity, in which a crosshead is installed, and a plunger drives the crosshead to reciprocate in the crosshead bearing cavity.

具体地，减速箱内的传动齿轮与曲轴箱100连接，减速箱内的传动齿轮驱动曲轴旋转，曲轴带动柱塞作往复运动，十字头随着柱塞在十字头瓦腔内作往复运动，从而驱动液力端的吸排液。上述的十字头与柱塞可以相当于同一部件。Specifically, the transmission gear in the reduction box is connected to the crankcase 100, the transmission gear in the reduction box drives the crankshaft to rotate, the crankshaft drives the plunger to reciprocate, and the crosshead reciprocates with the plunger in the crosshead bearing cavity, thereby driving the suction and discharge of liquid at the hydraulic end. The above-mentioned crosshead and plunger can be equivalent to the same component.

图1示出了根据本发明一个实施例的一体式曲轴箱100的立体图，特别地示出了曲轴箱100的与十字头箱200连接侧的前端面106；图2示出了根据本发明一个实施例的一体式曲轴箱100的另一个立体图，特别地示出了曲轴箱100的与十字头箱200连接侧的相对侧的后端面107。FIG1 shows a stereoscopic view of an integrated crankcase 100 according to an embodiment of the present invention, and in particular shows a front end face 106 of the crankcase 100 on the side connected to the crosshead case 200; FIG2 shows another stereoscopic view of the integrated crankcase 100 according to an embodiment of the present invention, and in particular shows a rear end face 107 of the crankcase 100 on the opposite side to the side connected to the crosshead case 200.

如图1和图2所示，根据本发明一个实施例的一体式曲轴箱100包括多个轴承座101、顶部104、底部105、多个支撑立板102以及位于支撑立板102之间的至少一个(例如多个)加强筋103，其中还示出了曲轴箱100的前端面106和后端面107，前端面106是曲轴箱100的与十字头箱100连接侧的表面，并且后端面107是前端面106的相对侧的表面。该一体式曲轴箱100可以通过铸造形成。顶部104和底部105分别在曲轴箱100的高度方向Z上的上下两侧沿着曲轴箱100的长度方向X从一端延伸到另一端，该前端面106和后端面107分别在曲轴箱100的宽度方向Y上的前后两侧沿着曲轴箱100的长度方向Y从一端延伸到另一端。各个支撑立板102用于支撑各个轴承座101，支撑立板102沿轴承座101的轴线方向间隔排布，支撑立板102的数量和轴承座101的数量与柱塞泵的缸数有关，轴承座101的厚度大于支撑立板102的厚度。支撑立板102用于支撑轴承座101，轴承座101上安装有主轴承，主轴承套装在曲轴上。因此，曲轴将柱塞泵对其的反作用力施加在主轴承上，并通过主轴承施加至轴承座101和多个支撑立板102上。因此，主轴承所受的合力即为轴承座101所受的合力。柱塞泵对曲轴的反作用力由液力端施加至柱塞泵。轴承座101用于承受主轴承的径向载荷，因此将轴承座101的宽度设置为与轴承宽度近似，以保证可靠支撑。柱塞泵有各种不同的规格，因此所使用的轴承的规格也各种各样。不同的轴承需要匹配不同的轴承座，由此轴承座101的宽度由所支撑的轴承的宽度来限定。支撑立板102作为整个曲轴箱100的核心框架，其合理布置能保证柱塞泵壳体刚度均匀，各轴承座101被可靠支撑，进而保证主轴承和曲轴连杆机构的稳定运行。关于支撑立板102的具体合理布置方案，将在下文中详细说明。As shown in Figures 1 and 2, an integrated crankcase 100 according to an embodiment of the present invention includes a plurality of bearing seats 101, a top 104, a bottom 105, a plurality of support plates 102, and at least one (e.g., a plurality of) reinforcing ribs 103 located between the support plates 102, wherein a front end face 106 and a rear end face 107 of the crankcase 100 are also shown, the front end face 106 being the surface of the crankcase 100 on the side connected to the crosshead case 100, and the rear end face 107 being the surface on the opposite side of the front end face 106. The integrated crankcase 100 can be formed by casting. The top 104 and the bottom 105 extend from one end to the other end along the length direction X of the crankcase 100 at the upper and lower sides in the height direction Z of the crankcase 100, respectively, and the front end face 106 and the rear end face 107 extend from one end to the other end along the length direction Y of the crankcase 100 at the front and rear sides in the width direction Y of the crankcase 100, respectively. Each support plate 102 is used to support each bearing seat 101. The support plates 102 are arranged at intervals along the axial direction of the bearing seat 101. The number of support plates 102 and the number of bearing seats 101 are related to the number of cylinders of the plunger pump. The thickness of the bearing seat 101 is greater than the thickness of the support plates 102. The support plates 102 are used to support the bearing seat 101. The main bearing is installed on the bearing seat 101, and the main bearing is sleeved on the crankshaft. Therefore, the crankshaft applies the reaction force of the plunger pump to it on the main bearing, and applies it to the bearing seat 101 and multiple support plates 102 through the main bearing. Therefore, the resultant force on the main bearing is the resultant force on the bearing seat 101. The reaction force of the plunger pump on the crankshaft is applied to the plunger pump by the hydraulic end. The bearing seat 101 is used to bear the radial load of the main bearing, so the width of the bearing seat 101 is set to be similar to the bearing width to ensure reliable support. There are various specifications of plunger pumps, so the specifications of the bearings used are also various. Different bearings need to be matched with different bearing seats, so the width of the bearing seat 101 is limited by the width of the supported bearing. The support plate 102 is the core frame of the entire crankcase 100. Its reasonable arrangement can ensure the uniform stiffness of the plunger pump housing, and each bearing seat 101 is reliably supported, thereby ensuring the stable operation of the main bearing and the crankshaft connecting rod mechanism. The layout plan will be described in detail below.

各支撑立板102之间的间距可以相同，该间距取决于泵组件的尺寸；或曲轴箱100在长度方向Y上的两端的端部支撑立板102之间的间距与中段支撑立板102之间的间距不同，中段支撑立板102位于两端的端部支撑立板102之间，例如，端部支撑立板102之间的间距指的是在曲轴箱100的长度方向Y上的两端分别最靠外侧的两个支撑立板102之间的间距；或者相对于所述曲轴箱100的长度方向Y的中心，支撑立板102之间的间距设置成对称，长度方向Y与轴承座101的轴线的延伸方向平行；支撑立板102的合理设置能有效提高曲轴箱100的整体抗弯刚度，抑制柱塞泵壳体变形。The spacing between each support vertical plate 102 can be the same, and the spacing depends on the size of the pump assembly; or the spacing between the end support vertical plates 102 at both ends of the crankcase 100 in the length direction Y is different from the spacing between the middle support vertical plates 102, and the middle support vertical plates 102 are located between the end support vertical plates 102 at both ends. For example, the spacing between the end support vertical plates 102 refers to the spacing between the two outermost support vertical plates 102 at both ends of the crankcase 100 in the length direction Y; or relative to the center of the crankcase 100 in the length direction Y, the spacing between the support vertical plates 102 is set to be symmetrical, and the length direction Y is parallel to the extension direction of the axis of the bearing seat 101; the reasonable setting of the support vertical plates 102 can effectively improve the overall bending stiffness of the crankcase 100 and suppress the deformation of the plunger pump housing.

各支撑立板102在轴承座101沿轴线方向的两侧均沿轴承座101的圆周铸出若干减重凹槽109；减重凹槽109的深度按设计需求而定，减重凹槽109的起始边缘和终止边缘具有过渡圆角，其中从支撑立板102的表面开始切割减重凹槽109的位置为起始边缘，减重凹槽109切割完成形成的边缘为终止边缘；减重凹槽109的具体形状和范围受加强筋103,103’布置的影响，例如以柱塞泵的柱塞轴线为中心上下对称或非对称布置均可，如上所述的加强筋103,103’是铸造在支撑立板102之间的(参见图1)，减重凹槽109开在支撑立板102上的位置要避开加强筋103,103’间隔布置。如上所述，本发明的一体式曲轴箱100能够一体铸造成型，如此减重凹槽109也在曲轴箱100的一体铸造成型中制备。采用一体式铸造成型减重凹槽109能极大缩减机加工工序，减重凹槽109的位置和形状不受加工方式的限制，可灵活布置。Each support plate 102 has a plurality of weight-reducing grooves 109 cast along the circumference of the bearing seat 101 on both sides of the bearing seat 101 along the axial direction; the depth of the weight-reducing groove 109 is determined according to the design requirements, and the starting edge and the ending edge of the weight-reducing groove 109 have transition fillets, wherein the position where the weight-reducing groove 109 is cut from the surface of the support plate 102 is the starting edge, and the edge formed after the weight-reducing groove 109 is cut is the ending edge; the specific shape and range of the weight-reducing groove 109 are affected by the arrangement of the reinforcing ribs 103, 103', for example, the arrangement can be symmetrical or asymmetrical with the plunger axis of the plunger pump as the center, the reinforcing ribs 103, 103' as described above are cast between the support plates 102 (see Figure 1), and the position where the weight-reducing grooves 109 are opened on the support plates 102 should avoid the reinforcing ribs 103, 103' and be arranged at intervals. As described above, the one-piece crankcase 100 of the present invention can be cast in one piece, so the weight-reducing grooves 109 are also prepared in the one-piece casting of the crankcase 100. The use of one-piece casting to form the weight-reducing groove 109 can greatly reduce the machining process. The position and shape of the weight-reducing groove 109 are not limited by the machining method and can be flexibly arranged.

轴承座101的直径取决于施加在该轴承座101上的轴承外圈的尺寸，本发明一个实施例中各轴承座101的直径相同；或位于曲轴箱100长度方向Y两端的轴承座101的座孔可大于中段轴承座101的座孔，中段轴承座101位于两端的轴承座101之间，根据设计能保证各轴承外圈冷却收缩后能从两侧顺利安装至对应轴承位即可，外圈回温膨胀后与轴承支撑面形成过盈配合。轴承座101与轴承外圈的接触面需要额外的机加工工序，包括但不限于镗铣加工等，来保证各轴承座101的形位公差和表面粗糙度要求，进而确保各轴承和曲轴的正常旋转。The diameter of the bearing seat 101 depends on the size of the outer ring of the bearing applied to the bearing seat 101. In one embodiment of the present invention, the diameters of the bearing seats 101 are the same; or the seat holes of the bearing seats 101 at both ends of the crankcase 100 in the length direction Y can be larger than the seat holes of the middle bearing seat 101. The middle bearing seat 101 is located between the bearing seats 101 at both ends. According to the design, it can be ensured that the outer rings of each bearing can be smoothly installed to the corresponding bearing position from both sides after cooling and shrinking, and the outer rings will form an interference fit with the bearing support surface after warming up and expanding. The contact surface between the bearing seat 101 and the outer ring of the bearing requires additional machining processes, including but not limited to boring and milling, to ensure the shape and position tolerances and surface roughness requirements of each bearing seat 101, thereby ensuring the normal rotation of each bearing and crankshaft.

在本发明的一个实施例中，参见图3和图4，其分别示出了安装有曲轴的曲轴箱100的截面图和部分切割立体图，其中各中段轴承座101的宽度t1相同，两端轴承座101的宽度t2,t3小于中段轴承座101的宽度t1，这是由于曲轴两侧主轴颈1,6承受的单侧曲柄销上连杆的载荷(约600kN)远小于中段轴颈2-5需要承受的双侧连杆载荷(约1200kN)。为了尽量减轻柱塞泵壳体的重量而将两侧主轴颈1,6的厚度设计得更小，因此支撑曲轴两侧主轴颈1,6的轴承和轴承座101的宽度小于中段轴承和轴承座 101的宽度。关于两端主轴承和中段主轴承的受力情况，具体参见图5和图6的受力曲线图。这里，由于轴颈与各主轴承一一对应，因此为了方便，对与各轴颈相对应的主轴承赋予相同的附图标记，详见图5和图6。In one embodiment of the present invention, referring to FIG3 and FIG4, a cross-sectional view and a partially cut stereoscopic view of a crankcase 100 with a crankshaft installed thereon are shown, respectively, wherein the width t1 of each middle section bearing seat 101 is the same, and the widths t2 and t3 of the bearing seats 101 at both ends are smaller than the width t1 of the middle section bearing seat 101. This is because the load of the connecting rod on the single-sided crank pin borne by the main journals 1, 6 on both sides of the crankshaft (about 600kN) is much smaller than the double-sided connecting rod load (about 1200kN) that the middle section journals 2-5 need to bear. In order to minimize the weight of the plunger pump housing, the thickness of the main journals 1, 6 on both sides is designed to be smaller, so the width of the bearings and bearing seats 101 supporting the main journals 1, 6 on both sides of the crankshaft is smaller than the width of the middle section bearings and bearing seats. The width is 101. For the stress conditions of the main bearings at both ends and the middle section, please refer to the stress curves of Figures 5 and 6. Here, since the journals correspond to the main bearings one by one, for convenience, the main bearings corresponding to the journals are given the same reference numerals, see Figures 5 and 6 for details.

值得注意的是，两端轴承座101的宽度t2,t3之间也略有不同，减速箱侧端部轴承座101需要额外的定位销孔和螺纹孔以定位和固定减速箱体连接法兰，需要承受减速箱的扭矩和载荷，如扭矩及其扭转冲击载荷，减速箱的部分重力，减速箱平行级和行星级啮合的振动冲击载荷。因此，此处轴承座101的厚度设计为t2>t3，具体差值可以根据壳体强度和刚度设计计算以及静力学、疲劳分析确定。尽量保证各轴承座101及其所在立板的形变值相近，考虑等刚度设计概念，保证壳体整体刚度以及配合间隙的稳定性和一致性。或根据设计需求调整各轴承座101宽度，能稳定支撑主轴承即可。It is worth noting that the widths t2 and t3 of the bearing seats 101 at both ends are slightly different. The bearing seat 101 at the side end of the gearbox requires additional locating pin holes and threaded holes to locate and fix the gearbox connecting flange. It needs to withstand the torque and load of the gearbox, such as torque and its torsional impact load, partial gravity of the gearbox, and vibration impact load of the parallel stage and planetary stage meshing of the gearbox. Therefore, the thickness of the bearing seat 101 here is designed to be t2>t3, and the specific difference can be determined based on the shell strength and stiffness design calculations as well as statics and fatigue analysis. Try to ensure that the deformation values of each bearing seat 101 and the vertical plate on which it is located are similar, consider the concept of equal stiffness design, and ensure the stability and consistency of the overall stiffness of the shell and the fitting clearance. Or adjust the width of each bearing seat 101 according to design requirements so that it can stably support the main bearing.

另外，参见图7，其示出了曲轴箱100的立体图。支撑立板102的顶部设置有用于吊点111的吊点凸台110，其截面形状不限，其中图8示出了吊点凸台110部分的局部放大图。为了满足吊装平衡需求，吊点凸台110靠两端侧的支撑立板102布置，数量大于等于两个，吊点凸台110与曲轴箱100的箱体连接处设置有大尺寸过渡圆角，有利于提高吊点凸台110的根部强度，同时满足铸造工艺性；或者也可以不设置吊点凸台110，而是铸出局部加厚的结构，能满足吊装条件即可。不设置吊点凸台110是指不在吊点处铸出规则的台或柱状，仅通过局部材料堆积加厚(可不规则)来保证吊点的强度。吊点凸台110的高度和厚度与吊环螺栓的尺寸有关，箱体重量越大就需要越大型号的吊环螺栓来提高抗拉强度，进而需要铸出更高更宽的吊环凸台。同时，整泵各吊点凸台110的上表面在同一平面上，保证吊装平稳，不发生倾倒。In addition, see FIG. 7 , which shows a three-dimensional view of the crankcase 100 . A hanging point boss 110 for a hanging point 111 is provided on the top of the support vertical plate 102 , and its cross-sectional shape is not limited, wherein FIG. 8 shows a partial enlarged view of the hanging point boss 110 . In order to meet the hoisting balance requirements, the hanging point boss 110 is arranged close to the support vertical plates 102 on both ends, and the number is greater than or equal to two. A large-sized transition fillet is provided at the connection between the hanging point boss 110 and the crankcase 100 body, which is conducive to improving the root strength of the hanging point boss 110 and meeting the casting processability; or the hanging point boss 110 may not be provided, but a locally thickened structure may be cast to meet the hoisting conditions. Not providing the hanging point boss 110 means that a regular table or column is not cast at the hanging point, and the strength of the hanging point is only ensured by local material accumulation and thickening (which may be irregular). The height and thickness of the lifting point boss 110 are related to the size of the eyebolt. The heavier the box is, the larger the size of the eyebolt is needed to improve the tensile strength, and thus the higher and wider lifting point boss needs to be cast. At the same time, the upper surfaces of the lifting point bosses 110 of the whole pump are on the same plane to ensure stable lifting and prevent tipping.

另一方面，曲轴箱100长度方向Y上的两端的端部支撑立板102上设置有沿轴承座101的轴线在圆周方向上布置的工艺通孔112，用于加工中段轴承外圈挡板螺纹孔113，参见图9图10，其分别示出了曲轴箱100的显示了工艺通孔112和轴承挡板螺纹孔113的位置的立体图和曲轴箱100的在支撑立板102的截面上显示了工艺通孔112和轴承挡板螺纹孔113的位置的立体图。工艺通孔112的位置和数量由轴承挡板的布置方案决定：为保证压紧定位可靠，每个轴承挡板由至少两个螺栓固定，轴承外圈一侧由至少三个轴承挡板固定。同时要保证各轴承挡板靠近两侧工艺窗，以便于安装。因此对应地，至少两个工艺通孔112为一组，对应一处挡板，圆周方向上至少布置三组工艺通孔112，各组工艺通孔112之间的位置尽量保证均匀布置并且靠近两侧工艺窗。为保证曲轴箱100内油气密封，各工艺通孔112需要使用铝塞114塞紧密封；或可替换为任意可塞入通孔内并能保证密封但不破坏本体的材质，包括但不限于橡胶、塑料等。On the other hand, process through holes 112 arranged in the circumferential direction along the axis of the bearing seat 101 are provided on the end support vertical plates 102 at both ends of the crankcase 100 in the length direction Y, which are used to process the threaded holes 113 of the outer ring baffle of the middle section bearing, see Figures 9 and 10, which respectively show the three-dimensional view of the crankcase 100 showing the positions of the process through holes 112 and the threaded holes 113 of the bearing baffle and the three-dimensional view of the crankcase 100 showing the positions of the process through holes 112 and the threaded holes 113 of the bearing baffle on the cross section of the support vertical plates 102. The position and number of the process through holes 112 are determined by the arrangement scheme of the bearing baffle: to ensure reliable clamping and positioning, each bearing baffle is fixed by at least two bolts, and one side of the bearing outer ring is fixed by at least three bearing baffles. At the same time, it is necessary to ensure that each bearing baffle is close to the process windows on both sides for easy installation. Therefore, correspondingly, at least two process through holes 112 form a group, corresponding to one baffle, and at least three groups of process through holes 112 are arranged in the circumferential direction, and the positions between the process through holes 112 are arranged as evenly as possible and close to the process windows on both sides. To ensure the oil and gas sealing in the crankcase 100, each process through hole 112 needs to be tightly sealed with an aluminum plug 114; or it can be replaced with any material that can be inserted into the through hole and can ensure sealing without damaging the body, including but not limited to rubber, Plastic, etc.

另外，在各支撑立板102之间沿轴承座101的圆周布置有若干加强筋103,103’，参见图1，其用于限制各支撑立板102的变形和位移。如上所述，曲轴箱100可以一体成型，例如一体铸造成型，因此加强筋103,103’也可以在曲轴箱100的一体铸造工艺中一体成型。一体铸造的加强筋103,103’与拼接式加强筋相比抗弯扭强度高、缓冲吸振性好，因此相较拼接式加强筋具有更稳定的支撑能力，能显著提高整体曲轴箱100的刚度，抑制壳体变形和振动。In addition, a plurality of reinforcing ribs 103, 103' are arranged along the circumference of the bearing seat 101 between the support vertical plates 102, see FIG1, which are used to limit the deformation and displacement of the support vertical plates 102. As described above, the crankcase 100 can be integrally formed, such as integrally cast, so the reinforcing ribs 103, 103' can also be integrally formed in the integral casting process of the crankcase 100. Compared with the spliced reinforcing ribs, the integrally cast reinforcing ribs 103, 103' have higher bending and torsional strength and better buffering and vibration absorption, so compared with the spliced reinforcing ribs, they have more stable supporting capacity, can significantly improve the rigidity of the overall crankcase 100, and suppress shell deformation and vibration.

另外，参见图11，其示出了支撑立板102之间的一个加强筋103的局部放大图，其中加强筋103与支撑立板102之间设置有过渡坡口115，坡口115与柱塞泵壳体，例如支撑立板102，之间具有过渡圆角116，其主要目的是提高加强筋103根部的抗弯强度，同时设置坡口115有利于满足铸造工艺性；坡口115的形式不限，可根据需求设置斜角或弧形(等曲率或变曲率)。In addition, refer to Figure 11, which shows a partial enlarged view of a reinforcing rib 103 between the supporting plates 102, wherein a transition groove 115 is arranged between the reinforcing rib 103 and the supporting plate 102, and a transition fillet 116 is arranged between the groove 115 and the plunger pump housing, such as the supporting plate 102, the main purpose of which is to improve the bending strength of the root of the reinforcing rib 103, and at the same time, the setting of the groove 115 is conducive to meeting the casting processability; the form of the groove 115 is not limited, and an oblique angle or an arc (equal curvature or variable curvature) can be set according to needs.

下面参照图12和图13对加强筋103,103’的布置进行详细说明，其中图12示出了曲轴和柱塞的运动结构简化的曲柄连杆结构的示意图和受力分析图；图13示出了加强筋103,103’的布置以及连杆摆角的图示。曲轴驱动柱塞作往复运动，因此可以将动力端的曲轴和柱塞的运动过程简化为如图12右侧图所示的受力分析图，根据图12右侧图中的受力分析可得主轴承所受合力Flⁿ＝F+F_c，其中F代表柱塞轴向所受的液压力+往复惯性力+摩擦力的合力，F_c代表柱塞垂直方向的支撑力。合力F1ⁿ的方向与柱塞轴向的夹角即为β。最大合力F1ⁿ的方向与柱塞轴向的夹角为βmax。根据图12右侧图所示，通过分解A点、B点和O点的受力，获得主轴承所受合力的公式Flⁿ＝F+F_c。The arrangement of the reinforcing ribs 103, 103' is described in detail below with reference to Fig. 12 and Fig. 13, wherein Fig. 12 shows a schematic diagram of the crank-connecting rod structure and a force analysis diagram of the simplified motion structure of the crankshaft and the plunger; Fig. 13 shows the arrangement of the reinforcing ribs 103, 103' and a diagram of the swing angle of the connecting rod. The crankshaft drives the plunger to reciprocate, so the motion process of the crankshaft and the plunger at the power end can be simplified into a force analysis diagram as shown in the right figure of Fig. 12. According to the force analysis in the right figure of Fig. 12, the resultant force Fl ⁿ =F+F _c on the main bearing can be obtained, where F represents the resultant force of the hydraulic pressure + reciprocating inertia force + friction force on the axial direction of the plunger, and F _c represents the vertical support force of the plunger. The angle between the direction of the resultant force F1 ⁿ and the axial direction of the plunger is β. The angle between the direction of the maximum resultant force F1 ⁿ and the axial direction of the plunger is βmax. According to the right figure of Fig. 12, by decomposing the forces at points A, B and O, the formula for the resultant force on the main bearing is obtained, Fl ⁿ =F+F _c .

图中的各点含义为：O—曲轴中心；A—连杆小头孔中心(十字头销旋转中心)；B—连杆大头孔中心(曲柄销旋转中心)。The meanings of the points in the figure are: O—crankshaft center; A—connecting rod small end hole center (crosshead pin rotation center); B—connecting rod big end hole center (crank pin rotation center).

各个力的含义：A点：F—柱塞轴向所受的液压力+往复惯性力+摩擦力的合力；F_c—柱塞(曲柄销)垂直方向的支撑力；F_l—连杆正压力；The meaning of each force: Point A: F—the combined force of the hydraulic pressure on the plunger axial direction + the reciprocating inertia force + the friction force; _Fc —the vertical support force of the plunger (crank pin); _Fl —the positive pressure of the connecting rod;

B点：F_t—连杆切向力；F_n—连杆径向力；F_l’—连杆正压力→转换到O点为轴承座101所受合力F₁ ⁿ。连杆正压力F_l经连杆杆身传递到曲柄销上为F_l’，在B点沿曲柄销和曲轴旋转中心连线方向及其垂向分解为连杆径向力F_n和连杆切向力F_t，传递为O点为F_n’和F_t’，合力即为F₁ ⁿ。Point B: _Ft - tangential force of connecting rod; _Fn - radial force of connecting rod; _Fl ' - positive pressure of connecting rod → converted to point O as the resultant ^force _F1n on bearing seat 101. The positive pressure _Fl of connecting rod is transmitted to crank pin through connecting rod body as _Fl ', and is decomposed into connecting rod radial force _Fn and connecting rod tangential force _Ft along the line connecting crank pin and crankshaft rotation center and its vertical direction at point B, and transmitted to point O as _Fn ' and _Ft ', and the resultant force ^is _F1n .

关于A、B、O三点的力和运动进行以下补充说明：The following additional explanations are given about the forces and motions at points A, B, and O:

柱塞沿轴向往复运动，传递给十字头的合力F在A点(十字头销)沿十字头的垂直方向和连杆方向分解为柱塞垂直方向的支撑力F_c和连杆正压力F₁；柱塞垂直方向的支撑力F_c转换到O点即为轴承座受到的支撑反作用力F_c’，柱塞轴向合力F转换到O点即为轴承座受到的柱塞轴向力F’，F_c’和F’两者在O点的合力即为轴承座所受合力F₁ ⁿ，即F₁ ⁿ＝F+F_c。The resultant force F transmitted to the crosshead by the axial reciprocating motion of the plunger is decomposed into the vertical support force _Fc of the plunger and the positive pressure _F1 of the connecting rod along the vertical direction of the crosshead and the connecting rod at point A (crosshead pin); The support force _Fc converted to point O is the support reaction force _Fc ' received by the bearing seat. The plunger axial force F converted to point O is the plunger axial force F' received by the bearing seat. The resultant force of _Fc ' and F' at point O is the resultant ^{force F1n} _received by the bearing seat, that is ^, _F1n = F+ _Fc .

A点的连杆正压力F_l经连杆杆身传递到曲柄销上为F_l’，在B点沿曲柄销和曲轴旋转中心连线方向及其垂直方向分解为连杆径向力F_n和连杆切向力F_t，传递到O点为F_n’和F_t’，合力即为F₁ ⁿ。The connecting rod positive pressure _Fl at point A is transmitted to the crank pin through the connecting rod body as _Fl ', and is decomposed into connecting rod radial force _Fn and connecting rod tangential force _Ft at point B along the direction of the line connecting the crank pin and the crankshaft rotation center and in the vertical direction, and is transmitted to point O as _Fn ' and _Ft ^' , and the resultant force is _F1n .

具体地，根据动力端的曲轴和柱塞的运动过程，将曲轴和柱塞的运动结构简化为曲柄连杆结构，如图12的左侧图所示，再构建三角函数等式，运动方程中连杆摆角其中，为曲轴旋转角。连杆摆角的极值大小取决于曲柄径与连杆长度的比值λ，λ即为曲轴的轴径与柱塞的长度的比值，因此λ为常数。根据计算，得出柱塞的位移方程
Specifically, according to the motion process of the crankshaft and plunger at the power end, the motion structure of the crankshaft and plunger is simplified to a crank-connecting rod structure, as shown in the left figure of Figure 12, and then the trigonometric function equation is constructed. The swing angle of the connecting rod in the motion equation is in, is the crankshaft rotation angle. The extreme value of the connecting rod swing angle depends on the ratio of the crank diameter to the connecting rod length λ, which is the ratio of the crankshaft diameter to the plunger length, so λ is a constant. According to the calculation, the displacement equation of the plunger is obtained:

然后根据柱塞的位移方程导出液力端对柱塞的压力波动方程：
Then, the pressure fluctuation equation of the hydraulic end on the plunger is derived according to the displacement equation of the plunger:

其中，p表示液力端的腔内压力，p_in表示液力端入口供液压力；p_out表示液力端排出压力；s表示冲程，这里的s为柱塞泵由上止点运动至下止点的位移，也就是图12左侧图中A′点到上止点A″的距离；x表示柱塞位移，这里是指柱塞的移动位移；pr表示液体在某一压力下的可压缩百分比；η表示容积效率；β_up表示液力端腔内压力从低压到高压建立时所对应的曲轴转角；β_down表示液力端腔内压力从高压到低压泄压过程所对应的曲轴转角；α表示上止点角度，这里的上止点可以为附图12左侧图中B″所示的位置。根据上述公式能够得到液力端对柱塞的反作用力，因此根据液力端的腔内压力p得到柱塞轴向所受的液压力，然后根据公式力F_l ⁿ＝F+F_c计算主轴承所受合力，可以得出主轴承所受合力的方向，进而得到主轴承所受合力的方向与柱塞轴向的夹角，继而得到β。Among them, p represents the pressure in the cavity of the hydraulic end, p_in represents the liquid supply pressure at the inlet of the hydraulic end; p_out represents the discharge pressure of the hydraulic end; s represents the stroke, where s is the displacement of the plunger pump from the top dead center to the bottom dead center, that is, the distance from point A′ to the top dead center A″ in the left figure of Figure 12; x represents the plunger displacement, which refers to the movement displacement of the plunger; pr represents the compressibility percentage of the liquid under a certain pressure; η represents the volumetric efficiency; β_up represents the crankshaft angle corresponding to the establishment of the pressure in the cavity of the hydraulic end from low pressure to high pressure; β_down represents the crankshaft angle corresponding to the pressure relief process from high pressure to low pressure in the cavity of the hydraulic end; α represents the top dead center angle, where the top dead center can be the position shown by B″ in the left figure of Figure 12. According to the above formula, the reaction force of the hydraulic end on the plunger can be obtained. Therefore, the hydraulic pressure on the axial direction of the plunger can be obtained according to the pressure p in the cavity of the hydraulic end. Then, the resultant force on the main bearing can be calculated according to the formula force F _l ⁿ =F+F _c . The direction of the resultant force on the main bearing can be obtained, and then the angle between the direction of the resultant force on the main bearing and the axial direction of the plunger can be obtained, and then β can be obtained.

再根据矩形截面中心的惯性矩公式可知，b为矩形截面的宽度，h为矩形结构面的高度，当矩形截面长度方向与受力方向接近时，矩形梁的弯矩值最大。根据惯性矩积分公式及仿真结果，矩形梁的惯性矩在旋转角度±20％之内下降仍然不明显。因此在进行曲轴箱100的加强设计时，第一加强筋103的延伸方向与柱塞的轴向方向的夹角大于或等于0.8βmax，小于或等于1.2βmax。βmax是轴承座所受最大合力的方向与柱塞泵的柱塞的轴向方向之间的夹角。According to the formula of the moment of inertia of the center of the rectangular section It can be seen that b is the width of the rectangular section, h is the height of the rectangular structural surface, and when the length direction of the rectangular section is close to the force direction, the bending moment value of the rectangular beam is the largest. According to the moment integral formula and simulation results, the moment of inertia of the rectangular beam does not decrease significantly within the rotation angle of ±20%. Therefore, when strengthening the crankcase 100, the angle between the extension direction of the first reinforcing rib 103 and the axial direction of the plunger is greater than or equal to 0.8βmax and less than or equal to 1.2βmax. βmax is the angle between the direction of the maximum resultant force on the bearing seat and the axial direction of the plunger of the plunger pump.

如上所述，曲轴将柱塞泵对其的反作用力施加在主轴承上，并通过主轴承施加至轴承座101和多个支撑立板102上。因此主轴承所受的合力即为轴承座101所受的合力，该合力与柱塞轴向的夹角为β，连杆摆角的最大值为βmax。加强筋103,103’的布置类型分为两种，第一种为第一加强筋103的延伸方向不通过轴承座101圆心，与柱塞的轴向方向之间的夹角大于或等于0.8βmax，且小于或等于1.2βmax，沿轴承座101的座孔在上下左右各处布置，即设置有多个第一加强筋103，能够有效地抵抗柱塞泵对曲轴箱100的冲击力，提高支撑立板102的强度和刚度，加强支撑立板102与轴承座101之间的刚度和强度，从而降低曲轴箱100开裂的风险。As described above, the crankshaft applies the reaction force of the plunger pump to the main bearing, and applies it to the bearing seat 101 and multiple support plates 102 through the main bearing. Therefore, the resultant force on the main bearing is the resultant force on the bearing seat 101, and the angle between the resultant force and the axial direction of the plunger is β, and the maximum value of the connecting rod swing angle is βmax. There are two types of arrangement types of reinforcing ribs 103, 103'. The first type is that the extension direction of the first reinforcing rib 103 does not pass through the center of the bearing seat 101, and the angle between the first reinforcing rib 103 and the axial direction of the plunger is greater than or equal to 0.8βmax, and less than or equal to 1.2βmax. It is arranged at various places along the seat hole of the bearing seat 101, that is, multiple first reinforcing ribs 103 are provided, which can effectively resist the impact force of the plunger pump on the crankcase 100, improve the strength and rigidity of the support plate 102, and strengthen the rigidity and strength between the support plate 102 and the bearing seat 101, thereby reducing the risk of cracking of the crankcase 100.

本申请公开的方案中，在轴承座101所受合力的方向与柱塞泵的柱塞的轴向方向之间的夹角的一定范围内设置第一加强筋103，能够有效地抵抗柱塞泵对曲轴箱100的冲击力，进而避免支撑立板102发生相对变形的风险，促使动力端壳体具有较高的强度和刚度。In the solution disclosed in the present application, a first reinforcing rib 103 is provided within a certain range of the angle between the direction of the resultant force on the bearing seat 101 and the axial direction of the plunger of the plunger pump, which can effectively resist the impact force of the plunger pump on the crankcase 100, thereby avoiding the risk of relative deformation of the supporting plate 102, and enabling the power end housing to have higher strength and rigidity.

另外，第一加强筋103的延伸方向相对于曲轴所受的最大合力方向在±20％角度之内，因此增加了加强筋截面惯性矩，进而降低了支撑立板102之间的相对变形，进一步降低了对主轴承内外圈的挤压破坏或滚子磨损的风险。In addition, the extension direction of the first reinforcing rib 103 is within an angle of ±20% relative to the direction of the maximum resultant force on the crankshaft, thereby increasing the moment of inertia of the reinforcing rib section, thereby reducing the relative deformation between the supporting plates 102, and further reducing the risk of extrusion damage to the inner and outer rings of the main bearing or roller wear.

图35为曲轴转角与主轴承压力角的示意图，主轴承的压力角即为上文中的β。从图36可以看出曲轴转角在0°至180°范围内，压力角在负方向，且在90°时最大。而180°至360°范围内压力角为正值，且在270°时最大。Figure 35 is a schematic diagram of the crankshaft angle and the main bearing pressure angle. The main bearing pressure angle is β mentioned above. Figure 36 shows that when the crankshaft angle is in the range of 0° to 180°, the pressure angle is in the negative direction and is the largest at 90°. When the crankshaft angle is in the range of 180° to 360°, the pressure angle is positive and is the largest at 270°.

图36为曲轴转角与主轴承合力的示意图，从附图可以看出，主轴承合力在曲轴转角为0°至40°以及180°至200°之间有明显的突变。FIG36 is a schematic diagram of the crankshaft angle and the resultant force of the main bearing. It can be seen from the figure that the resultant force of the main bearing has an obvious mutation when the crankshaft angle is between 0° and 40° and between 180° and 200°.

图37为压力角与主轴承合力的示意图，压力角在0°至10°之间其主轴承合力较大。FIG37 is a schematic diagram of the pressure angle and the resultant force of the main bearing. When the pressure angle is between 0° and 10°, the resultant force of the main bearing is relatively large.

基于此，图35、图36和图37可以得出，压力角可以为10°，第一加强筋的延伸方向与柱塞的轴向方向的夹角可以大于或等于8°，小于或等于12°。当然，压力角还可以为其他角度，本文不作限制。Based on this, it can be concluded from Figures 35, 36 and 37 that the pressure angle can be 10°, and the angle between the extension direction of the first reinforcing rib and the axial direction of the plunger can be greater than or equal to 8° and less than or equal to 12°. Of course, the pressure angle can also be other angles, which are not limited in this article.

进一步地，如图13所示，在另一种可选的实施例中，在前端面106和后端面107上分别设置有一组第一加强筋103，并且每组内的第一加强筋103相对于柱塞泵的柱塞的轴向方向彼此对称。进一步地，设置于前端面106上的一组第一加强筋103与设置于后端面107上的一组第一加强筋103相对于轴承座101的垂直中心线彼此对称。具体地，在曲轴箱100的前端面106上的一组第一加强筋103包括两个前端加强筋103，他们分布于柱塞泵的曲轴轴线的上下两侧并且相对于柱塞泵的柱塞的轴向方向彼此对称，使得他们的延伸方向之间的夹角为第二夹角，其可以大于或等于1.8βmax，且小于或等于2.2βmax。这里的第二夹角即为附图13中的θ角。类似地，在曲轴箱100的后端面107上的一组第一加强筋103包括两个后端加强筋103，他们分布于柱塞泵的曲轴轴线的上下两侧并且相对于柱塞泵的柱塞的轴向方向彼此对称，并且他们的延伸方向之间的夹角也为第二夹角，第二夹角可以大于或等于1.8βmax，且小于或等于2.2βmax。如此，能够更好的抵抗柱塞对主轴承外圈的作用力，进而避免造成主轴承外圈被挤压破坏或滚子被磨损的风险，因此进一步提高了动力端壳体的安全性和可靠性。例如，两个前端加强筋103和两个后端加强筋103可以相对于轴承座101的垂直中心线对称地设置。也就是说，多个第一加强筋103包括在轴承座101的前端面106上的两个前端加强筋103，两个前端加强筋103相对于柱塞泵的柱塞的轴向方向彼此对称；并且多个第一加强筋103还包括在轴承座101的后端面107上的两个后端加强筋103，两个后端加强筋103相对于柱塞泵的柱塞的轴向方向也彼此对称，其中前端面106是曲轴箱100的与十字头箱200连接侧的表面，并且后端面107是前端面106的相对侧的表面。优选地，两个前端加强筋103与两个后端加强筋103相对于所述轴承座101的垂直中心线彼此对称。Further, as shown in FIG13 , in another optional embodiment, a group of first reinforcing ribs 103 are respectively provided on the front end face 106 and the rear end face 107, and the first reinforcing ribs 103 in each group are symmetrical with respect to the axial direction of the plunger of the plunger pump. A group of first reinforcing ribs 103 disposed on the rear end face 107 are symmetrical to each other relative to the vertical center line of the bearing seat 101. Specifically, a group of first reinforcing ribs 103 on the front end face 106 of the crankcase 100 includes two front end reinforcing ribs 103, which are distributed on the upper and lower sides of the crankshaft axis of the plunger pump and are symmetrical to each other relative to the axial direction of the plunger of the plunger pump, so that the angle between their extension directions is a second angle, which can be greater than or equal to 1.8βmax and less than or equal to 2.2βmax. The second angle here is the angle θ in Figure 13. Similarly, a group of first reinforcing ribs 103 on the rear end face 107 of the crankcase 100 includes two rear end reinforcing ribs 103, which are distributed on the upper and lower sides of the crankshaft axis of the plunger pump and are symmetrical to each other relative to the axial direction of the plunger of the plunger pump, and the angle between their extension directions is also a second angle, which can be greater than or equal to 1.8βmax and less than or equal to 2.2βmax. In this way, the force of the plunger on the outer ring of the main bearing can be better resisted, thereby avoiding the risk of the outer ring of the main bearing being squeezed and damaged or the roller being worn, thereby further improving the safety and reliability of the power end housing. For example, the two front end reinforcing ribs 103 and the two rear end reinforcing ribs 103 can be symmetrically arranged relative to the vertical center line of the bearing seat 101. That is, the plurality of first reinforcing ribs 103 include two front end reinforcing ribs 103 on the front end face 106 of the bearing seat 101, and the two front end reinforcing ribs 103 are symmetrical to each other relative to the axial direction of the plunger of the plunger pump; and the plurality of first reinforcing ribs 103 also include two rear end reinforcing ribs 103 on the rear end face 107 of the bearing seat 101, and the two rear end reinforcing ribs 103 are also symmetrical to each other relative to the axial direction of the plunger of the plunger pump, wherein the front end face 106 is the surface of the crankcase 100 on the side connected to the crosshead case 200, and the rear end face 107 is the surface on the opposite side of the front end face 106. Preferably, the two front end reinforcing ribs 103 and the two rear end reinforcing ribs 103 are symmetrical to each other relative to the vertical center line of the bearing seat 101 .

注意，虽然这里为了便于说明使用了第一加强筋103、前端加强筋103和后端加强筋103的不同表述以进行区分，但这并不意味着它们有实质性差别，在不需要区分它们时，它们可以被统称为第一加强筋103。Note that although different expressions of the first reinforcing rib 103, the front end reinforcing rib 103 and the rear end reinforcing rib 103 are used here to distinguish them for the sake of convenience, this does not mean that there are substantial differences between them. When there is no need to distinguish them, they can be collectively referred to as the first reinforcing rib 103.

根据上述论述可知，主轴承受力方向与柱塞运动方向之间的夹角在0至βmax之间波动，因此为了增加曲轴箱100在曲轴运动过程中的抗弯刚度。在另一种可选的实施例中，动力端壳体还可以包括多个103’，第二加强筋103’的延伸方向通过轴承座101的圆心O，如图13所示。多个第二加强筋103’可以沿轴承座101的座孔上下对称布置，数量不限，但是需要避开左右工艺窗、十字头箱200和底部回油口位置，用于提高轴承座101的刚度，防止滚子轴承承受过大的轴向力。理论来说第二加强筋103’的数量不限，但从支撑强度、受力及重量上考虑，第二加强筋103’与第一加强筋103整体上均匀布置。在本示例中，第二加强筋103’设计成在轴承座101的上侧为3个上侧加强筋103’，而下侧为2个下侧加强筋103’，其中2个下侧加强筋103’可以分别设置在底部回油口的两侧而不与所述底部回油口产生干扰，这是为了规避底部回油口。 According to the above discussion, the angle between the force direction of the main bearing and the movement direction of the plunger fluctuates between 0 and βmax, so in order to increase the bending stiffness of the crankcase 100 during the crankshaft movement. In another optional embodiment, the power end housing may also include a plurality of 103', and the extension direction of the second reinforcing ribs 103' passes through the center O of the bearing seat 101, as shown in Figure 13. The plurality of second reinforcing ribs 103' can be arranged symmetrically up and down along the seat hole of the bearing seat 101, and the number is not limited, but it is necessary to avoid the left and right process windows, the crosshead box 200 and the bottom oil return port position, so as to improve the stiffness of the bearing seat 101 and prevent the roller bearing from being subjected to excessive axial force. Theoretically, the number of second reinforcing ribs 103' is not limited, but considering the support strength, force and weight, the second reinforcing ribs 103' and the first reinforcing ribs 103 are arranged uniformly as a whole. In this example, the second reinforcing ribs 103' are designed to have three upper reinforcing ribs 103' on the upper side of the bearing seat 101 and two lower reinforcing ribs 103' on the lower side, wherein the two lower reinforcing ribs 103' can be respectively arranged on both sides of the bottom oil return port without interfering with the bottom oil return port, in order to avoid the bottom oil return port.

注意，虽然这里为了便于说明使用了第二加强筋103’、上侧加强筋103’和下侧加强筋103’的不同表述以进行区分，但这并不意味着它们有实质性差别，在不需要区分它们时，它们可以被统称为第二加强筋103’。Note that although different expressions of the second reinforcing rib 103’, the upper reinforcing rib 103’ and the lower reinforcing rib 103’ are used here to distinguish them for the sake of convenience, this does not mean that there are substantial differences between them. When there is no need to distinguish them, they can be collectively referred to as the second reinforcing rib 103’.

本实例中加强筋103,103’截面为矩形，对比相同面积的其他实心规则截面(如圆形、正方形等)，矩形的长轴截面惯性矩更大，能保证加强筋103,103’具有足够的弯曲刚度，抑制支撑立板102之间的位移和形变；也可根据需求替代为任意满足支撑需求和铸造工艺的截面形状。In this example, the cross-section of the reinforcing ribs 103, 103' is a rectangle. Compared with other solid regular cross-sections of the same area (such as a circle, a square, etc.), the moment of inertia of the long-axis section of the rectangle is larger, which can ensure that the reinforcing ribs 103, 103' have sufficient bending rigidity to suppress the displacement and deformation between the supporting vertical plates 102; it can also be replaced with any cross-sectional shape that meets the support requirements and the casting process as required.

在另一种可选的实施例中，曲轴箱100和十字头箱200均为一体式铸造件，曲轴箱100和十字头箱200密封连接。这里的曲轴箱100和十字头箱200密封连接是指将曲轴箱100内用于安装曲轴的空间与十字头箱200的十字头瓦腔211密封。In another optional embodiment, the crankcase 100 and the crosshead case 200 are both integrally cast parts, and the crankcase 100 and the crosshead case 200 are sealed and connected. The sealed connection between the crankcase 100 and the crosshead case 200 here means that the space in the crankcase 100 for installing the crankshaft is sealed with the crosshead bearing cavity 211 of the crosshead case 200.

另外，前端面106上的连杆通孔117下方的第一加强筋103会阻挡滑轨末端排出的润滑油流入回油口，因此在该第一加强筋103上铸出矩形排油通孔118，参见图14，其右侧图示出了曲轴箱100的前端面106以及连杆通孔117和排油通孔118，左侧图是排油通孔118的放大图；排油通孔118的形状不限，使十字头滑轨顺利排油、不过度削弱第一加强筋103强度即可；通孔成型工艺不限，可为一体式铸造，也可机加工出通孔，或其他去除材料的方式；通孔位置不限，可在每段加强筋103处间隔布置，也可在支撑立板102处间隔布置；通孔数量不限，每段设置一个或多个均可，但保证每个十字头对应至少一个。In addition, the first reinforcing rib 103 below the connecting rod through hole 117 on the front end face 106 will block the lubricating oil discharged from the end of the slide rail from flowing into the oil return port, so a rectangular oil drain through hole 118 is cast on the first reinforcing rib 103, referring to Figure 14, the right side figure shows the front end face 106 of the crankcase 100, the connecting rod through hole 117 and the oil drain through hole 118, and the left side figure is an enlarged view of the oil drain through hole 118; the shape of the oil drain through hole 118 is not limited, so that the crosshead slide rail can drain oil smoothly and the strength of the first reinforcing rib 103 is not excessively weakened; the through hole forming process is not limited, it can be an integral casting, or a through hole can be machined, or other methods of removing material can be used; the position of the through hole is not limited, it can be arranged at intervals at each section of the reinforcing rib 103, or it can be arranged at intervals at the supporting plate 102; the number of through holes is not limited, one or more can be set in each section, but it is guaranteed that each crosshead corresponds to at least one.

本申请实施例中，曲轴箱100为一体式铸造件，采用一体式铸造工艺制造的曲轴箱100能够避免多种焊接缺陷，例如，焊接变形、焊接应力过大等缺陷，进而使得动力端壳体的强度更高，以延长动力端壳体的使用寿命。另外，曲轴箱100进行一体式铸造工艺，能够降低动力端壳体的制造工艺难度。In the embodiment of the present application, the crankcase 100 is an integral casting. The crankcase 100 manufactured by the integral casting process can avoid various welding defects, such as welding deformation, excessive welding stress, etc., thereby making the strength of the power end housing higher, thereby extending the service life of the power end housing. In addition, the integral casting process of the crankcase 100 can reduce the difficulty of the manufacturing process of the power end housing.

另外，需要指出的是，曲轴箱100可以包括用于支撑曲轴箱100的支脚119，例如所述支脚为多个支脚119，多个支脚119的底部在同一平面上，通过地脚螺栓固定在底橇500上，为整个动力端提供支撑和固定，提高***稳定性，参见图15，其示出了曲轴箱100与十字头箱200一起连接在底橇500上的状态，并且示出了曲轴箱的多个支脚119。In addition, it should be pointed out that the crankcase 100 may include a support leg 119 for supporting the crankcase 100. For example, the support leg may include a plurality of support legs 119, and the bottoms of the plurality of support legs 119 are on the same plane and are fixed to the bottom skid 500 by anchor bolts, thereby providing support and fixation for the entire power end and improving the stability of the system. See FIG. 15 , which shows a state in which the crankcase 100 is connected to the bottom skid 500 together with the crosshead case 200, and shows a plurality of support legs 119 of the crankcase.

每个支撑立板102均在前端面106侧和后端面107侧各布置至少一个支脚119，两支脚119之间也可根据需求设置额外若干的支脚119，参见图16；或在每个支撑立板102的底部设置一个从前端面106延伸至后端面107的横向一体式支脚119’，参见图17，其示出了横向一体式支脚119’和纵向一体式支脚119”。曲轴箱100的前端面 106和后端面107的部分用于将各支撑立板102连接并保证整个箱体封闭，其不属于支撑立板102的一部分。前端面106指曲轴箱100与十字头箱200连接一侧的表面；后端面107指曲轴箱100与十字头箱200连接侧的相对侧的表面。Each support plate 102 is provided with at least one support foot 119 on the front face 106 side and the rear face 107 side, and a plurality of additional support feet 119 may be provided between the two support feet 119 as required, as shown in FIG16; or a transverse integrated support foot 119' extending from the front face 106 to the rear face 107 is provided at the bottom of each support plate 102, as shown in FIG17, which shows the transverse integrated support foot 119' and the longitudinal integrated support foot 119". The front face of the crankcase 100 The front face 106 and the rear face 107 are used to connect the support vertical plates 102 and ensure that the entire box body is closed, and they are not part of the support vertical plates 102. The front face 106 refers to the surface on the side where the crankcase 100 is connected to the crosshead box 200; the rear face 107 refers to the surface on the side opposite to the side where the crankcase 100 is connected to the crosshead box 200.

支脚119的位置和数量不仅限于在支撑立板102上，例如，可设置从一侧支撑立板102延伸至另一侧支撑立板102的纵向一体式支脚119”。The position and number of the support legs 119 are not limited to being on the support uprights 102. For example, a longitudinal integrated support leg 119" extending from one support upright 102 to the other support upright 102 may be provided.

参见图18，其示出了支脚119的局部放大图，其中支脚119的根部设置有坡口120，主要目的是提高脚119的根部抗弯强度，同时设置坡口120有利于满足铸造工艺性；坡口120的形式不限，可根据需求设置斜角或弧形(等曲率或变曲率)；与箱体连接处设置有大尺寸过渡圆角，进一步加大根部抗弯强度。Refer to Figure 18, which shows a partial enlarged view of the support leg 119, wherein a groove 120 is provided at the root of the support leg 119. The main purpose is to improve the bending strength of the root of the leg 119. At the same time, the provision of the groove 120 is conducive to satisfying the casting processability; the form of the groove 120 is not limited, and an oblique angle or an arc (equal curvature or variable curvature) can be set according to needs; a large-size transition fillet is provided at the connection with the box body to further increase the bending strength of the root.

另外，支脚119的截面为矩形，以前端面106到后端面107的方向(横向)为长轴方向，使矩形的截面惯性矩更大，能保证支脚具有足够的弯曲刚度；或任意形状，保证支脚119根部的抗弯刚度，支撑可靠。In addition, the cross-section of the support leg 119 is a rectangle, with the direction from the front end face 106 to the rear end face 107 (laterally) as the long axis direction, so that the cross-sectional moment of inertia of the rectangle is larger, which can ensure that the support leg has sufficient bending stiffness; or any shape to ensure the bending stiffness of the root of the support leg 119 and reliable support.

支脚两侧面有减重凹槽121，其形状不限，深度按支撑刚度需求而定；减重凹槽121的起始边缘和终止边缘具有过渡圆角；减重凹槽121远离底部接触面123，以在支脚119的底部提供地脚螺纹孔124的空间，从而保证螺纹连接强度，地脚螺纹孔124中的地脚螺栓提供与底橇500的紧固连接，螺纹孔去除首端不完整丝扣，以提高螺纹连接刚度。There are weight-reducing grooves 121 on both sides of the support foot, and the shape of the grooves is not limited, and the depth is determined according to the support stiffness requirement; the starting edge and the ending edge of the weight-reducing groove 121 have transition fillets; the weight-reducing groove 121 is away from the bottom contact surface 123 to provide space for the anchor threaded hole 124 at the bottom of the support foot 119, thereby ensuring the strength of the threaded connection, and the anchor bolts in the anchor threaded hole 124 provide a fastening connection with the bottom skid 500, and the threaded hole removes the incomplete thread at the head end to improve the threaded connection stiffness.

参见图19，其是曲轴箱的示出了整个轴承座孔的一侧的截面图，其中曲轴箱100的侧面呈八边形，多边形结构能保证壳体刚度，在相同体积下质量更小，能有效减轻壳体重量，同时为工艺窗板提供更多安装面；或曲轴箱100侧面为其他壳体形状，如等曲率或变曲率球面均可；顶部104和底部105沿柱塞轴线对称布置，能更好地保证变形量均匀；前端面106和后端面107平行，其之间的距离取决于泵组件的尺寸。Refer to Figure 19, which is a cross-sectional view of one side of the crankcase showing the entire bearing seat hole, wherein the side of the crankcase 100 is octagonal, and the polygonal structure can ensure the rigidity of the shell, has a smaller mass under the same volume, can effectively reduce the weight of the shell, and provide more installation surfaces for the process window plate; or the side of the crankcase 100 is other shell shapes, such as a spherical surface with equal curvature or variable curvature; the top 104 and the bottom 105 are arranged symmetrically along the axis of the plunger, which can better ensure uniform deformation; the front end face 106 and the rear end face 107 are parallel, and the distance between them depends on the size of the pump assembly.

在多边形壳体，特别是八边形壳体的情况下，为工艺窗提供了加工和安装平面，为便于连杆盖和连杆体的安装，在前端面106、后端面107以及前端面106斜向上、斜向下对应连杆盖的位置布置了四处工艺窗，这里需要说明的是，前端面106上的工艺窗可以是曲轴的连杆通过其中进入十字头箱中的连杆通孔。因此必须确保安装该四处工艺窗的四个平面，另外，为保证整个曲轴箱100壳体对称、支撑均匀、减轻自重，将整体设置为8个面，同时避开了各加强筋103,103’的布局，防止过度削弱加强筋103,103’的强度。In the case of a polygonal shell, especially an octagonal shell, a processing and installation plane is provided for the process window. To facilitate the installation of the connecting rod cover and the connecting rod body, four process windows are arranged on the front end face 106, the rear end face 107, and the position of the front end face 106 obliquely upward and obliquely downward corresponding to the connecting rod cover. It should be noted here that the process window on the front end face 106 can be the connecting rod through hole through which the connecting rod of the crankshaft enters the crosshead box. Therefore, the four planes for installing the four process windows must be ensured. In addition, in order to ensure the symmetry of the entire crankcase 100 shell, uniform support, and reduce dead weight, the whole is set to 8 planes, while avoiding the layout of each reinforcement rib 103, 103' to prevent excessive weakening of the strength of the reinforcement rib 103, 103'.

参见图7和图20，图7示出了曲轴箱的立体图，其中示出了油气分离器凸台125；并且图20示出了曲轴箱的切割立体图，其中示出了在曲轴箱100的顶部设置的多个油气分离器凸台的部分切割图，其中在顶部104设置有多个油气分离器凸台125，便于加工出安装平面，凸台125与顶部104之间设置有过渡圆角，进一步提高了连接处刚度。凸台125的数量及位置不限(顶部或其他位置)；由于整体式铸造壳体密闭性较强，设置油气分离器能释放内部气体并隔离外部杂质，有助于平衡壳体内外气压。设置油气分离器在平衡曲轴箱100内外气压的同时，避免外部水汽侵入曲轴箱100，水汽会加速内部泵配件的锈蚀，锈蚀颗粒作为磨粒还会加速金属零件磨损，同时游离水在热的金属表面闪蒸会导致点蚀。长时间的水汽浸入造成曲轴箱100内润滑油乳化，导致润滑油的润滑性能急剧下降，进而影响润滑部件的表面摩擦系数，最终导致轴承轴瓦的异常磨损，甚至是烧瓦等现象。7 and 20, FIG. 7 shows a perspective view of the crankcase, which shows the oil separator boss 125; and FIG. 20 shows a cut perspective view of the crankcase, which shows a plurality of oil separators disposed on the top of the crankcase 100. Partial cutaway diagram of the gas separator boss, wherein multiple oil-gas separator bosses 125 are provided on the top 104, which facilitates the processing of the installation plane, and a transition fillet is provided between the boss 125 and the top 104, which further improves the rigidity of the connection. The number and position of the boss 125 are not limited (top or other positions); since the integral casting shell has strong airtightness, the oil-gas separator can release the internal gas and isolate external impurities, which helps to balance the air pressure inside and outside the shell. The oil-gas separator is provided to balance the air pressure inside and outside the crankcase 100 while preventing external water vapor from invading the crankcase 100. Water vapor will accelerate the rust of internal pump accessories, and rust particles as abrasive particles will also accelerate the wear of metal parts. At the same time, free water flashes on the hot metal surface and causes pitting. Long-term water vapor immersion causes the lubricating oil in the crankcase 100 to emulsify, resulting in a sharp drop in the lubricating performance of the lubricating oil, which in turn affects the surface friction coefficient of the lubricated parts, and ultimately leads to abnormal wear of the bearing bushing, or even burning of the bushing.

参见图21和图22，图21示出了从下方看到的曲轴箱100的立体图，图22示出了曲轴箱200和回油口盖板未安装状态的立体图，其中在底部105上以支撑立板102为间隔均匀布置一个或多个回油口126(其数量取决于加强筋103,103’和支撑立板102的数量和位置)，在各支撑立板102间空余的位置设置回油口126(即避开支撑立板102)，回油口126的设置便于润滑油的回收、循环和冷却，回油口126的成型工艺不限，可为一体式铸造，也可机加工，或其他增加或去除材料的方式；形状不限于圆形；外圈设置回油盖板安装凸台127，便于一体式盖板128的密封，或可采用分体式盖板各自密封。例如，一体式盖板128能够可拆卸地安装在回油盖板安装凸台127上以对回油口126进行密封。所有回油口126不需要严格按照图中所示的一条直线布置，此处是为了美观对称及回油管的规整布置设置为一条直线。Referring to Figures 21 and 22, Figure 21 shows a stereoscopic view of the crankcase 100 as seen from below, and Figure 22 shows a stereoscopic view of the crankcase 200 and the oil return port cover plate in an uninstalled state, wherein one or more oil return ports 126 (the number of which depends on the number and position of the reinforcing ribs 103, 103' and the support plates 102) are evenly arranged on the bottom 105 with the support plates 102 as intervals, and the oil return ports 126 are set in the empty positions between the support plates 102 (that is, avoiding the support plates 102). The setting of the oil return ports 126 facilitates the recovery, circulation and cooling of the lubricating oil. The molding process of the oil return port 126 is not limited, and it can be one-piece casting, machining, or other methods of adding or removing materials; the shape is not limited to a circle; the outer ring is provided with an oil return cover plate mounting boss 127 to facilitate the sealing of the one-piece cover plate 128, or a split cover plate can be used to seal each separately. For example, the integrated cover plate 128 can be detachably mounted on the oil return cover plate mounting boss 127 to seal the oil return port 126. All oil return ports 126 do not need to be arranged strictly in a straight line as shown in the figure, but are arranged in a straight line here for aesthetic symmetry and regular arrangement of the oil return pipes.

参见图23和图24，其分别示出了曲轴箱100上的从壳体外表面朝向曲轴的方向贯穿的各个工艺窗129,129’，其中顶部104和底部105两侧各设置有多个圆形工艺窗同时作为工艺窗129，便于拧紧三段式连杆中的连接螺栓，同时减轻壳体重量；其数量不限，形状不限于圆形，不阻挡螺栓拧紧工具拧紧螺栓即可；窗口成型工艺不限，可为一体式铸造，也可机加工，或其他去除材料的方式。通过工艺窗能够观察和/或操作曲轴箱100内部的部件，例如曲轴等。See FIG. 23 and FIG. 24, which respectively show the process windows 129, 129' on the crankcase 100 that penetrate from the outer surface of the shell toward the crankshaft, wherein multiple circular process windows are provided on both sides of the top 104 and the bottom 105 and serve as process windows 129 at the same time, which facilitates tightening the connecting bolts in the three-section connecting rod and reduces the weight of the shell; the number of process windows 129 is not limited, the shape is not limited to circular, and it only needs not to block the bolt tightening tool from tightening the bolts; the window molding process is not limited, and it can be one-piece casting, machining, or other methods of removing materials. Through the process windows, it is possible to observe and/or operate the components inside the crankcase 100, such as the crankshaft, etc.

后端面107上设置有多个长矩形工艺窗同时作为工艺窗129’，便于连杆盖和连杆体的装配，同时减轻壳体重量；其数量取决于压裂泵缸数，形状不限于长矩形，后端面107的工艺窗能使连杆盖在安装时顺利通过，前端面106上设置有与工艺窗129’类似的开口，称为连杆通孔117，使连杆体在安装时顺利通过，并允许十字头滑套的延长端伸入，且不阻碍连杆工作时的正常摆动即可。另外，后端面107五个工艺窗129’外圈有矩形的凹台130，便于安装盖板后仍与后端面107平齐，盖板安装螺栓为沉头螺栓，使整个盖板安装区域无部件凸起，防止剐蹭和磕碰，也一定程度上减轻曲轴箱100重量，参见图25，其示出了后端面107安装了盖板122的状态。工艺窗129及凹台130的成型工艺不限，可为一体式铸造，也可机加工，或其他去除材料的方式。The rear end face 107 is provided with a plurality of long rectangular process windows which also serve as process windows 129', so as to facilitate the assembly of the connecting rod cover and the connecting rod body and reduce the weight of the casing; the number of long rectangular process windows depends on the number of cylinders in the fracturing pump, and the shape is not limited to a long rectangle. The process windows of the rear end face 107 enable the connecting rod cover to pass smoothly during installation, and the front end face 106 is provided with an opening similar to the process window 129', called a connecting rod through hole 117, so as to enable the connecting rod body to pass smoothly during installation and allow the extended end of the crosshead sleeve to extend in without hindering the normal swing of the connecting rod during operation. In addition, the outer circle of the five process windows 129' of the rear end face 107 has a rectangular recess 130, so as to facilitate the installation of the cover plate so that it remains flush with the rear end face 107, and the cover plate mounting bolts are countersunk Bolts are provided to make the entire cover plate installation area free of protruding parts, thereby preventing scratches and bumps, and also reducing the weight of the crankcase 100 to a certain extent. Referring to FIG. 25 , it shows the state where the cover plate 122 is installed on the rear end surface 107. The molding process of the process window 129 and the concave platform 130 is not limited, and can be integrally cast, machined, or other ways of removing materials.

参见图26-33，其中图26示出了曲轴箱100与十字头箱200将要通过螺栓进行连接之前的立体图；图27示出了曲轴箱100与十字头箱200将要通过螺栓进行连接之前的从另一个角度看到的立体图；图28是曲轴箱100的在截面中示出了两道螺纹孔的侧面图以及两道螺纹孔的局部放大图；图29示出了曲轴箱100与十字头箱200通过两道螺栓连接在一起的截面图；图30示出了两道螺栓连接的局部放大图；图31示出了两道螺栓一对一布置的截面图；图32示出了两道螺栓一对二布置的截面图，图33示出了两道螺栓布置位置之间的关系的截面图。可以看出，十字头箱200与曲轴箱100采用两重螺栓连接，第一道螺栓连接为使用长的多个第一螺栓131进行整体固定及预紧，第二道螺栓连接为使用在第一螺栓131外圈的第二螺栓132进行密封和紧固，在曲轴箱100的前端面106上的密封面设置有密封槽133和密封件，或者直接采用密封胶密封，避免油气渗漏，防止水汽导致润滑油污染、内部金属部件腐蚀磨损等不良后果。相较于一道螺栓连接密封，两道螺栓的双重固定及连接能有效保证密封面的贴合和紧固，防止由于柱塞力和连杆侧向力导致的密封面脱开和滑移，阻挡油气油压的泄露。在另外的实施例中，螺栓布置不限于两道，可根据连接、密封需求和空间布局，设置多道螺栓连接。Refer to Figures 26-33, wherein Figure 26 shows a stereoscopic view of the crankcase 100 and the crosshead case 200 before they are connected by bolts; Figure 27 shows a stereoscopic view of the crankcase 100 and the crosshead case 200 before they are connected by bolts from another angle; Figure 28 is a side view of the crankcase 100 showing two threaded holes in cross section and a partial enlarged view of the two threaded holes; Figure 29 shows a cross-sectional view of the crankcase 100 and the crosshead case 200 connected together by two bolts; Figure 30 shows a partial enlarged view of the connection of two bolts; Figure 31 shows a cross-sectional view of a one-to-one arrangement of two bolts; Figure 32 shows a cross-sectional view of a one-to-two arrangement of two bolts, and Figure 33 shows a cross-sectional view of the relationship between the arrangement positions of the two bolts. It can be seen that the crosshead case 200 and the crankcase 100 are connected by two bolts. The first bolt connection is to use a plurality of long first bolts 131 for overall fixing and pre-tightening, and the second bolt connection is to use the second bolt 132 on the outer ring of the first bolt 131 for sealing and tightening. The sealing surface on the front end face 106 of the crankcase 100 is provided with a sealing groove 133 and a seal, or directly sealed with a sealant to avoid oil and gas leakage, prevent water vapor from causing lubricating oil pollution, corrosion and wear of internal metal parts and other adverse consequences. Compared with the single bolt connection seal, the double fixation and connection of the two bolts can effectively ensure the fit and tightening of the sealing surface, prevent the sealing surface from being disengaged and slipped due to the plunger force and the lateral force of the connecting rod, and block the leakage of oil, gas and oil pressure. In other embodiments, the bolt arrangement is not limited to two, and multiple bolt connections can be provided according to the connection, sealing requirements and space layout.

在密封面上与支撑立板102对应的位置布置有上下两排用于长的第一螺栓131的第一螺纹孔141，其多为均匀布置，具***置与支撑立板102布置方式有关，即用于长的第一螺栓131的第一螺纹孔141是从曲轴箱100的前端面106钻入支撑立板102的，用于第一道螺栓连接；为保证螺纹连接处有足够刚度，螺纹孔口设置直径稍大于螺纹孔直径的沉台，沉入深度大于等于1个螺距，避免拧紧时前几圈螺纹因刚度不足而被拉断，或密封表面受拉变形，影响密封连接效果。Two upper and lower rows of first threaded holes 141 for the long first bolts 131 are arranged at positions on the sealing surface corresponding to the support vertical plate 102. Most of them are evenly arranged, and the specific positions are related to the arrangement of the support vertical plate 102, that is, the first threaded holes 141 for the long first bolts 131 are drilled into the support vertical plate 102 from the front end surface 106 of the crankcase 100, and are used for the first bolt connection; in order to ensure that the threaded connection has sufficient rigidity, a sinking platform with a diameter slightly larger than the diameter of the threaded hole is provided at the threaded hole mouth, and the sinking depth is greater than or equal to 1 pitch, so as to avoid the first few turns of thread being broken due to insufficient rigidity when tightening, or the sealing surface being tensilely deformed, which affects the sealing connection effect.

在此实施例中，两端第一螺纹孔141的直径小于中段第一螺纹孔141的直径，这是由于中段位置的长的第一螺栓131需要同时承受左右两侧连杆和十字头轴向拉力的叠加，需要加大直径来保证螺栓的抗拉强度，而两端长的第一螺栓131受到单侧轴向力相对较小，可适当减小螺栓直径。也可根据使用需求设置为相同直径，螺纹孔数量、深度不限。需要指出的是，两端第一螺纹孔141是位于曲轴箱100的长度方向X两端的第一螺纹孔141，中段第一螺纹孔141位于两端第一螺纹孔141之间。In this embodiment, the diameter of the first threaded holes 141 at both ends is smaller than the diameter of the first threaded hole 141 in the middle section. This is because the long first bolt 131 in the middle section needs to bear the superposition of the axial tension of the connecting rods and the crosshead on both sides at the same time, and the diameter needs to be increased to ensure the tensile strength of the bolt, while the long first bolt 131 at both ends is relatively small in the unilateral axial force, and the bolt diameter can be appropriately reduced. It can also be set to the same diameter according to the use requirements, and the number and depth of the threaded holes are not limited. It should be pointed out that the first threaded holes 141 at both ends are the first threaded holes 141 located at both ends of the crankcase 100 in the length direction X, and the first threaded hole 141 in the middle section is located between the first threaded holes 141 at both ends.

另外，在密封面上布置有上下两排用于连接十字头箱200的第二螺纹孔142，或者该第二螺纹孔142沿十字头箱200外缘一圈布置，用于第二螺栓连接；第二螺纹孔142之间的距离相同或不相同(均匀布置或不均匀布置)均可。如上所述，第一螺纹孔141在各支撑立板102上下两端布置两排，而第二螺纹孔142在前端面106上沿第一螺纹孔141外圈布置并具有一定间隔，第一螺纹孔141与第二螺纹孔142可一一对应或一对多加密布置。例如，第二螺纹孔142可在第一螺纹孔141周围加密布置，组合形成更大面积但不相互影响的螺纹夹紧区域，保证两螺栓间的接触面夹紧不松脱。In addition, the sealing surface is provided with two rows of second threaded holes 142 for connecting the crosshead box 200, or Or the second threaded holes 142 are arranged along the outer edge of the crosshead box 200 for second bolt connection; the distances between the second threaded holes 142 can be the same or different (evenly arranged or unevenly arranged). As described above, the first threaded holes 141 are arranged in two rows at the upper and lower ends of each supporting vertical plate 102, and the second threaded holes 142 are arranged along the outer circle of the first threaded holes 141 on the front end surface 106 with a certain interval. The first threaded holes 141 and the second threaded holes 142 can correspond one to one or be arranged one to many in a dense manner. For example, the second threaded holes 142 can be densely arranged around the first threaded holes 141, combining to form a larger area of threaded clamping area that does not affect each other, to ensure that the contact surface between the two bolts is clamped and not loose.

关于两道螺纹孔形成的三角区域形状及面积与密封强度效果之间关系的具体描述，参见下文。For a detailed description of the relationship between the shape and area of the triangular area formed by the two threaded holes and the sealing strength effect, see below.

当螺栓旋入螺纹孔并拧紧后，被连接件受压变形并产生回弹趋势，曲轴箱100与十字头箱200的接触面会形成以螺纹孔轴线为中心的圆形夹紧区域(直径约为1.5～2倍螺纹孔公称直径)。一对二的三角形螺纹孔的合理布置，即一个第一螺纹孔141对应于两个第二螺纹孔142的布置，会组合形成更大的夹紧区域，进一步提高两接触面的夹紧效果。例如，三角形可以为等边三角形。当三个顶点距离过远时，每个螺栓的夹紧区域过度分离会影响紧固效果，在柱塞长时间往复运动的冲击下可能发生松脱和泄露；反之，若三个顶点距离过近，每个圆形夹紧区域会互相叠加，不仅不利于密封夹紧区域的扩大，还会造成部分区域压紧力的叠加，导致被连接件表面的破坏。When the bolt is screwed into the threaded hole and tightened, the connected part is deformed under pressure and has a tendency to rebound. The contact surface between the crankcase 100 and the crosshead case 200 will form a circular clamping area centered on the axis of the threaded hole (with a diameter of about 1.5 to 2 times the nominal diameter of the threaded hole). The reasonable arrangement of the one-to-two triangular threaded holes, that is, the arrangement of one first threaded hole 141 corresponding to two second threaded holes 142, will combine to form a larger clamping area, further improving the clamping effect of the two contact surfaces. For example, the triangle can be an equilateral triangle. When the three vertices are too far apart, the excessive separation of the clamping area of each bolt will affect the tightening effect, and loosening and leakage may occur under the impact of the long-term reciprocating motion of the plunger; on the contrary, if the three vertices are too close, each circular clamping area will overlap with each other, which is not only not conducive to the expansion of the sealing clamping area, but also causes the superposition of the clamping force in some areas, resulting in damage to the surface of the connected part.

每个螺纹孔去除首端不完整丝扣，提高螺纹连接刚度；曲轴箱100与十字头箱200的连接方式不限于螺纹连接，可采用保证两者紧密连接不发生相对位移的任意连接方式，例如，采用外部夹持结构将两接触面夹紧定位，或采用电磁吸连接、液压连接、自动连接钩等方式，但考虑到以上方案均需外接夹紧机构，结构复杂，制造维护成本较高，在极大的柱塞力往复作用下密封面可能松脱。综合制造成本和连接可靠性，本实例选用螺纹连接。Each threaded hole removes the incomplete thread at the head end to improve the rigidity of the threaded connection; the connection method of the crankcase 100 and the crosshead case 200 is not limited to threaded connection, and any connection method that ensures that the two are tightly connected without relative displacement can be used, for example, an external clamping structure is used to clamp and position the two contact surfaces, or electromagnetic suction connection, hydraulic connection, automatic connection hook, etc. are used. However, considering that the above solutions all require an external clamping mechanism, the structure is complex, the manufacturing and maintenance costs are high, and the sealing surface may loosen under the reciprocating action of the huge plunger force. Considering the manufacturing cost and connection reliability, threaded connection is selected in this example.

在曲轴箱100与十字头箱200的连接端面上设置有密封槽133，参见图34。该密封槽133围绕长的第一螺纹孔141和连杆通孔117外圈布置，同时绕开十字头箱200的排气腔和滑轨腔体外圆。在这种情况下，曲轴的连杆从其中通过并进入十字头箱200的连杆通孔117位于密封槽133的内侧，从而方便对连杆通孔进行有效密封。密封槽133的作用是放置密封圈，靠螺栓的夹紧使曲轴箱和十字头箱两个被密封件接触面与密封圈之间产生接触压缩应力，在压力作用下，密封圈发生弹性变形填充和密封两接触面的间隙，进而达到壳体内部油气密封的目的。如图所示，两道螺栓131和132布置在密封槽133外部。密封槽133围绕第一螺纹孔141和第二螺纹孔142及十字头滑轨、十字头排气腔的外形绕曲布置。将两道螺纹孔141和142布置在密封槽133的外部以及绕曲设计能将长螺栓圆周面和接触密封面隔开，使整个长螺纹孔气压相通，另外，也一定程度上增大密封长度，提高密封可靠性。另外，密封槽成型方式不限，可采用除机加工外其他去除材料的方式；槽内放置密封件，包括但不限于密封圈、密封环等；或者取消密封槽，直接采用密封胶密封。A sealing groove 133 is provided on the connecting end surface of the crankcase 100 and the crosshead case 200, see FIG34. The sealing groove 133 is arranged around the long first threaded hole 141 and the outer circle of the connecting rod through hole 117, while bypassing the exhaust chamber and the outer circle of the slide rail chamber of the crosshead case 200. In this case, the connecting rod of the crankshaft passes through and enters the connecting rod through hole 117 of the crosshead case 200, which is located on the inner side of the sealing groove 133, so as to facilitate the effective sealing of the connecting rod through hole. The function of the sealing groove 133 is to place the sealing ring. The clamping of the bolts generates contact compression stress between the contact surfaces of the two sealed parts of the crankcase and the crosshead case and the sealing ring. Under the action of pressure, the sealing ring undergoes elastic deformation to fill and seal the gap between the two contact surfaces, thereby achieving the purpose of oil and gas sealing inside the shell. As shown in the figure, two bolts 131 and 132 are arranged outside the sealing groove 133. The sealing groove 133 is arranged around the outer shape of the first threaded hole 141 and the second threaded hole 142 and the crosshead slide rail and the crosshead exhaust chamber. The two threaded holes 141 and 142 are arranged outside the sealing groove 133. The design of the winding part can separate the circumference of the long bolt from the contact sealing surface, so that the entire long threaded hole can communicate with the air pressure. In addition, it also increases the sealing length to a certain extent and improves the sealing reliability. In addition, the sealing groove can be formed in any way, and other methods of removing materials can be used except machining; sealing parts can be placed in the groove, including but not limited to sealing rings, sealing rings, etc.; or the sealing groove can be eliminated and directly sealed with sealant.

曲轴箱100的前端面106有通往轴承座101的润滑油孔，成型方式不限；十字头箱200的内置润滑油路间隔设置了额外的支路以与曲轴箱100前端面106的油孔相连，油路通向各轴承支撑面用于润滑轴承的油孔，油孔位置要求与轴承外圈油孔的凹槽对齐；若忽略油路加工难度，支路数量、角度和位置均可不限，达到润滑轴承的目的即可。注意避开螺纹孔承力影响区，避免削弱螺纹连接的强度，或因螺栓拧入导致的油孔变形堵塞。The front end face 106 of the crankcase 100 has a lubricating oil hole leading to the bearing seat 101, and the molding method is not limited; the built-in lubricating oil circuit of the crosshead box 200 is provided with additional branches at intervals to connect with the oil holes of the front end face 106 of the crankcase 100, and the oil circuit leads to the oil holes of each bearing support surface for lubricating the bearings, and the position of the oil hole is required to be aligned with the groove of the oil hole of the outer ring of the bearing; if the difficulty of oil circuit processing is ignored, the number, angle and position of the branches can be unlimited, and the purpose of lubricating the bearing can be achieved. Pay attention to avoid the load-bearing influence area of the threaded hole to avoid weakening the strength of the threaded connection or deformation and blockage of the oil hole caused by screwing in the bolt.

为防止润滑油渗漏，十字头箱200和曲轴箱100相连接的油孔端面需要单独的密封槽和密封件(包括但不限于密封圈、密封环)，或单独涂覆密封胶等，密封方式不限。To prevent lubricating oil leakage, the oil hole end faces connecting the crosshead case 200 and the crankcase 100 need separate sealing grooves and seals (including but not limited to sealing rings, sealing rings), or be coated with sealant separately, etc. The sealing method is not limited.

上述双重螺栓连接方式不限于分体式铸造曲轴箱100和十字头箱200的连接，同样地，分体式拼焊曲轴箱100和十字头箱200的连接同样适用，或任意组合连接，如拼焊曲轴箱100和铸造十字头箱200的连接，铸造曲轴箱100和拼焊十字头箱200的连接等。The above-mentioned double bolt connection method is not limited to the connection between the split cast crankcase 100 and the crosshead box 200. Similarly, the connection between the split welded crankcase 100 and the crosshead box 200 is also applicable, or any combination of connections, such as the connection between the welded crankcase 100 and the cast crosshead box 200, the connection between the cast crankcase 100 and the welded crosshead box 200, etc.

此外，本申请还提供了一种包含上述动力端壳体的柱塞泵，柱塞泵还可以包括液力端壳体，其中液力端壳体、十字头箱200和曲轴箱100能够依次连接在一起，第一螺纹孔141能够从液力端壳体贯穿到曲轴箱100，并且第一螺栓131能够通过第一螺纹孔141将液力端壳体、十字头箱200和曲轴箱100连接在一起。In addition, the present application also provides a plunger pump including the above-mentioned power end housing, and the plunger pump may also include a hydraulic end housing, wherein the hydraulic end housing, the crosshead box 200 and the crankcase 100 can be connected together in sequence, the first threaded hole 141 can pass through the hydraulic end housing to the crankcase 100, and the first bolt 131 can connect the hydraulic end housing, the crosshead box 200 and the crankcase 100 together through the first threaded hole 141.

具体地，本技术可以具有以下构成。Specifically, the present technology can have the following configurations.

(A1)一种用于柱塞泵的动力端壳体，其特征在于，包括：(A1) A power end housing for a plunger pump, characterized by comprising:

一体式曲轴箱100，所述曲轴箱100包括多个轴承座101和多个支撑立板102，所述支撑立板102用于支撑所述轴承座101，且所述支撑立板102沿所述轴承座101的轴线方向间隔排布，所述曲轴箱100在各个所述支撑立板102之间包括第一加强筋103，其中所述轴承座101所受最大合力的方向与所述柱塞泵的柱塞的轴向方向之间的夹角为βmax，并且所述第一加强筋103与所述柱塞的轴向方向之间的夹角为第一夹角，所述第一夹角大于或等于0.8βmax，且小于或等于1.2βmax。An integrated crankcase 100 includes a plurality of bearing seats 101 and a plurality of support plates 102, wherein the support plates 102 are used to support the bearing seats 101, and the support plates 102 are arranged at intervals along the axial direction of the bearing seats 101, and the crankcase 100 includes a first reinforcing rib 103 between each of the support plates 102, wherein the angle between the direction of the maximum resultant force on the bearing seat 101 and the axial direction of the plunger of the plunger pump is βmax, and the angle between the first reinforcing rib 103 and the axial direction of the plunger is a first angle, and the first angle is greater than or equal to 0.8βmax and less than or equal to 1.2βmax.

(A2)根据(A1)所述的动力端壳体，其特征在于，所述第一加强筋103至少设置于所述曲轴箱100的前端面106和/或后端面107上，所述前端面106是所述曲轴箱100的与十字头箱200连接侧的表面，并且所述后端面107是所述前端面106的相对侧的表面。(A2) The power end housing according to (A1) is characterized in that the first reinforcing rib 103 is at least provided on the front end face 106 and/or the rear end face 107 of the crankcase 100, and the front end face 106 is the crankshaft The rear end face 107 is a surface of the box 100 on the side connected to the crosshead box 200 , and the rear end face 107 is a surface on the opposite side of the front end face 106 .

(A3)根据上述(A2)所述的动力端壳体，其特征在于，在所述前端面106和所述后端面107上分别设置有一组所述第一加强筋103，并且每组内的所述第一加强筋103相对于所述柱塞泵的柱塞的轴向方向彼此对称。(A3) The power end housing according to (A2) above is characterized in that a group of the first reinforcing ribs 103 are respectively provided on the front end face 106 and the rear end face 107, and the first reinforcing ribs 103 in each group are symmetrical to each other relative to the axial direction of the plunger of the plunger pump.

(A4)根据上述(A3)所述的动力端壳体，其特征在于，设置于所述前端面106上的所述一组第一加强筋103与设置于所述后端面107上的所述一组第一加强筋103相对于所述轴承座101的垂直中心线彼此对称。(A4) The power end housing according to (A3) above is characterized in that the set of first reinforcing ribs 103 arranged on the front end face 106 and the set of first reinforcing ribs 103 arranged on the rear end face 107 are symmetrical to each other relative to the vertical center line of the bearing seat 101.

(A5)根据上述(A3)所述的动力端壳体，其特征在于，每组所述第一加强筋103包括两个所述第一加强筋103，所述两个第一加强筋103的延伸方向之间的夹角大于或等于1.8βmax，且小于或等于2.2βmax。(A5) The power end housing according to (A3) above is characterized in that each group of the first reinforcing ribs 103 includes two first reinforcing ribs 103, and the angle between the extension directions of the two first reinforcing ribs 103 is greater than or equal to 1.8βmax and less than or equal to 2.2βmax.

(A6)根据上述(A1)所述的动力端壳体，其特征在于，所述曲轴箱100还在各个所述支撑立板102之间包括多个第二加强筋103’，并且所述第二加强筋103’的延伸方向通过所述轴承座101的圆心。(A6) The power end housing according to (A1) above is characterized in that the crankcase 100 also includes a plurality of second reinforcing ribs 103' between each of the supporting vertical plates 102, and the extension direction of the second reinforcing ribs 103' passes through the center of the bearing seat 101.

(A7)根据上述(A6)所述的动力端壳体，其特征在于，所述多个第二加强筋103’沿着所述轴承座101的座孔对称布置。(A7) The power end housing according to (A6) above is characterized in that the multiple second reinforcing ribs 103' are symmetrically arranged along the seat hole of the bearing seat 101.

(A8)根据上述(A6)所述的动力端壳体，其特征在于，所述多个第二加强筋103’在所述轴承座101的上下两侧布置，其中在上侧布置有三个上侧加强筋103’并且在下侧布置有两个下侧加强筋103’，所述两个下侧加强筋103’的位置分别位于底部回油口的两侧而不与所述底部回油口产生干扰。(A8) The power end housing according to (A6) above is characterized in that the multiple second reinforcing ribs 103' are arranged on the upper and lower sides of the bearing seat 101, wherein three upper reinforcing ribs 103' are arranged on the upper side and two lower reinforcing ribs 103' are arranged on the lower side, and the positions of the two lower reinforcing ribs 103' are respectively located on both sides of the bottom oil return port without interfering with the bottom oil return port.

(A9)根据上述(A1)-(A8)中任一项所述的动力端壳体，其特征在于，所述第一加强筋103和/或所述第二加强筋103’与所述支撑立板102之间设置有过渡坡口115，并且所述坡口115与所述支撑立板102之间具有过渡圆角116。(A9) The power end housing according to any one of (A1) to (A8) above is characterized in that a transition groove 115 is provided between the first reinforcing rib 103 and/or the second reinforcing rib 103' and the supporting vertical plate 102, and a transition fillet 116 is provided between the groove 115 and the supporting vertical plate 102.

(A10)根据上述(A1)-(A8)中任一项所述的动力端壳体，其特征在于，所述第一加强筋103和/或所述第二加强筋103’的截面为矩形的。(A10) The power end casing according to any one of (A1) to (A8) above, characterized in that the cross-section of the first reinforcing rib 103 and/or the second reinforcing rib 103' is rectangular.

(A11)根据上述(A2)所述的动力端壳体，其特征在于，在所述曲轴箱100的所述前端面106上的连杆通孔117下方的所述第一加强筋103上设置有通孔118。(A11) The power end housing according to (A2) above is characterized in that a through hole 118 is provided on the first reinforcing rib 103 below the connecting rod through hole 117 on the front end surface 106 of the crankcase 100.

(A12)根据上述(A1)所述的动力端壳体，其特征在于，所述轴承座101的宽度由施加在所述轴承座101上的轴承的宽度限定，所述轴承座101包括位于所述曲轴箱100的两端的两个端部轴承座101以及若干个中段轴承座101，所述中段轴承座101位于所述两个端部轴承座101之间，其中各个所述中段轴承座101的宽度大于所述两个端部轴承座101中的每一个的宽度。(A12) The power end housing according to (A1) above is characterized in that the width of the bearing seat 101 is defined by the width of the bearing applied to the bearing seat 101, and the bearing seat 101 includes two end bearing seats 101 located at both ends of the crankcase 100 and a plurality of middle bearing seats 101, wherein the middle bearing seat 101 is located between the two end bearing seats 101, and the width of each middle bearing seat 101 is greater than that of the two end bearing seats 101. The width of each of the end bearing seats 101.

(A13)根据上述(A12)所述的动力端壳体，其特征在于，所述两个端部轴承座101中的位于所述曲轴箱100的减速箱连接侧的一个端部轴承座101的宽度比所述两个端部轴承座101中的另一个端部轴承座101的宽度宽。(A13) The power end housing according to (A12) above is characterized in that the width of one of the two end bearing seats 101 located on the reduction gearbox connection side of the crankcase 100 is wider than the width of the other end bearing seat 101 of the two end bearing seats 101.

(A14)根据上述(A1)所述的动力端壳体，其特征在于，所述支撑立板102之间的间距不同，并且相对于所述曲轴箱100的长度方向X的中心，所述支撑立板102之间的间距设置成对称，所述长度方向X与所述轴承座101的轴线方向平行。(A14) The power end housing according to (A1) above is characterized in that the spacing between the support vertical plates 102 is different, and the spacing between the support vertical plates 102 is set to be symmetrical relative to the center of the length direction X of the crankcase 100, and the length direction X is parallel to the axial direction of the bearing seat 101.

(A15)根据上述(A1)所述的动力端壳体，其特征在于，在所述支撑立板102上设置有减重凹槽109。(A15) The power end housing according to (A1) above is characterized in that a weight-reducing groove 109 is provided on the supporting vertical plate 102 .

(A16)根据上述(A15)所述的动力端壳体，其特征在于，所述减重凹槽109的起始边缘和终止边缘具有过渡圆角。(A16) The power end housing according to (A15) above is characterized in that the starting edge and the ending edge of the weight-reducing groove 109 have transition radius.

(A17)根据上述(A1)所述的动力端壳体，其特征在于，在所述支撑立板102的顶部设置有吊点凸台110，并且所述吊点凸台110与所述曲轴箱100的箱体连接处设置有过渡圆角。(A17) The power end housing according to (A1) above is characterized in that a hanging point boss 110 is provided on the top of the supporting vertical plate 102, and a transition fillet is provided at the connection between the hanging point boss 110 and the crankcase 100.

(A18)根据上述(A1)所述的动力端壳体，其特征在于，所述曲轴箱100的底部包括支脚119，所述支脚119用于支撑所述曲轴箱100。(A18) The power end housing according to (A1) above is characterized in that the bottom of the crankcase 100 includes a support foot 119, and the support foot 119 is used to support the crankcase 100.

(A19)根据上述(A18)所述的动力端壳体，其特征在于，各个所述支撑立板102在所述曲轴箱100的前端侧和后端侧均包含至少一个所述支脚119，所述前端侧为所述曲轴箱100的与十字头箱200连接的一侧，所述后端侧为所述前端侧的相对侧。(A19) The power end housing according to (A18) above is characterized in that each of the supporting vertical plates 102 includes at least one support foot 119 on the front end side and the rear end side of the crankcase 100, the front end side being the side of the crankcase 100 connected to the crosshead case 200, and the rear end side being the opposite side of the front end side.

(A20)根据上述(A18)所述的动力端壳体，其特征在于，所述支脚119为在各个所述支撑立板102的底部设置的从所述曲轴箱100的前端侧延伸至后端侧的横向一体式支脚119’，所述前端侧为所述曲轴箱100的与十字头箱200连接的一侧，所述后端侧为所述前端侧的相对侧。(A20) The power end housing according to (A18) above is characterized in that the support foot 119 is a transverse integrated support foot 119' arranged at the bottom of each of the supporting vertical plates 102 and extending from the front end side to the rear end side of the crankcase 100, the front end side being the side of the crankcase 100 connected to the crosshead case 200, and the rear end side being the opposite side of the front end side.

(A21)根据上述(A18)所述的动力端壳体，其特征在于，所述支脚119为沿所述曲轴箱100的长度方向X从一端的所述支撑立板102延伸至另一端的所述支撑立板102的纵向一体式支脚119”，所述长度方向X与所述轴承座101的轴线方向平行。(A21) The power end housing according to (A18) above is characterized in that the support foot 119 is a longitudinal integrated support foot 119" extending from the support vertical plate 102 at one end to the support vertical plate 102 at the other end along the length direction X of the crankcase 100, and the length direction X is parallel to the axial direction of the bearing seat 101.

(A22)根据上述(A18)-(A21)中任一项所述的动力端壳体，其特征在于，所述支脚119,119’,119”的根部设置有坡口120，并且所述坡口120与所述曲轴箱100的箱体连接处设置有过渡圆角。(A22) The power end housing according to any one of (A18) to (A21) above is characterized in that a groove 120 is provided at the root of the support legs 119, 119', 119", and a transition fillet is provided at the connection between the groove 120 and the crankcase 100.

(A23)根据上述(A18)-(A21)中任一项所述的动力端壳体，其特征在于，所述支脚119,119’,119”上设置有减重凹槽121，所述减重凹槽121远离所述支脚119, 119’,119”的底部接触面123，并且所述减重凹槽121的起始边缘和终止边缘具有过渡圆角。(A23) The power end housing according to any one of (A18) to (A21) above is characterized in that a weight-reducing groove 121 is provided on the support feet 119, 119', 119", and the weight-reducing groove 121 is away from the support feet 119, The bottom contact surface 123 of 119 ′, 119 ″, and the starting edge and the ending edge of the weight-reducing groove 121 have transition radius.

(A24)根据上述(A1)所述的动力端壳体，其特征在于，在所述曲轴箱100的顶部104设置有至少一个油气分离器凸台125。(A24) The power end housing according to (A1) above is characterized in that at least one oil-gas separator boss 125 is provided on the top 104 of the crankcase 100 .

(A25)根据上述(A1)所述的动力端壳体，其特征在于，在所述曲轴箱100的底部105设置有至少一个回油口126。(A25) The power end housing according to (A1) above is characterized in that at least one oil return port 126 is provided at the bottom 105 of the crankcase 100 .

(A26)根据上述(A25)所述的动力端壳体，其特征在于，所述动力端壳体还包括一体式盖板128，在所述回油口126的外圈设置有回油盖板安装凸台127，并且所述一体式盖板128能够可拆卸地安装在所述回油盖板安装凸台127上以对所述回油口126进行密封。(A26) According to the power end housing described in (A25) above, it is characterized in that the power end housing also includes an integrated cover plate 128, and an oil return cover plate mounting boss 127 is provided on the outer ring of the oil return port 126, and the integrated cover plate 128 can be detachably mounted on the oil return cover plate mounting boss 127 to seal the oil return port 126.

(A27)根据上述(A1)所述的动力端壳体，其特征在于，所述曲轴箱100上设置有从壳体外表面朝向曲轴的方向贯穿的工艺窗129,129’，通过所述工艺窗129,129’能够观察和/或操作所述曲轴箱100内部的部件。(A27) The power end housing according to (A1) above is characterized in that the crankcase 100 is provided with a process window 129, 129' penetrating from the outer surface of the housing toward the crankshaft, and the components inside the crankcase 100 can be observed and/or operated through the process window 129, 129'.

(A28)根据上述(A1)所述的动力端壳体，其特征在于，在所述曲轴箱100的靠近十字头箱200侧的表面上设置有多个第一螺纹孔141，所述第一螺纹孔141用于通过第一螺栓131将所述曲轴箱100与所述十字头箱200连接。(A28) The power end housing according to (A1) above is characterized in that a plurality of first threaded holes 141 are provided on the surface of the crankcase 100 close to the crosshead case 200, and the first threaded holes 141 are used to connect the crankcase 100 to the crosshead case 200 through first bolts 131.

(A29)根据上述(A1)所述的动力端壳体，其特征在于，在所述曲轴箱100的靠近十字头箱200侧的表面上设置有密封面，所述密封面上具有密封槽133，所述曲轴箱100的连杆通孔位于所述密封槽133的内侧。(A29) The power end housing according to (A1) above is characterized in that a sealing surface is provided on the surface of the crankcase 100 close to the crosshead case 200, and a sealing groove 133 is provided on the sealing surface, and the connecting rod through hole of the crankcase 100 is located on the inner side of the sealing groove 133.

(A30)根据上述(A1)所述的动力端壳体，其特征在于，在所述曲轴箱100的靠近十字头箱200侧的表面上设置有通往所述轴承座101的润滑油孔，所述润滑油孔的位置与轴承外圈油孔的凹槽对齐。(A30) The power end housing according to (A1) above is characterized in that a lubricating oil hole leading to the bearing seat 101 is provided on the surface of the crankcase 100 close to the crosshead case 200, and the position of the lubricating oil hole is aligned with the groove of the oil hole of the outer ring of the bearing.

(A31)根据上述(A1)所述的动力端壳体，其特征在于，所述曲轴箱100是一体铸造成型的。(A31) The power end housing according to (A1) above is characterized in that the crankcase 100 is integrally cast.

(A32).一种柱塞泵，所述柱塞泵包括根据上述(A1)-(A31)中任一项所述的动力端壳体。(A32). A plunger pump, comprising a power end housing according to any one of (A1) to (A31) above.

(A33)根据上述(A32)所述的柱塞泵，其特征在于，还包括液力端壳体，并且所述动力端壳体还包括十字头箱200，所述液力端壳体、所述十字头箱200和曲轴箱100依次连接，其中第一螺纹孔141能够从所述液力端壳体贯穿到所述曲轴箱100，并且第一螺栓131能够通过所述第一螺纹孔141将所述液力端壳体、所述十字头箱200和曲轴箱100连接在一起。 (A33) The plunger pump according to (A32) above is characterized in that it also includes a hydraulic end housing, and the power end housing also includes a crosshead box 200, the hydraulic end housing, the crosshead box 200 and the crankcase 100 are connected in sequence, wherein the first threaded hole 141 can pass through the hydraulic end housing to the crankcase 100, and the first bolt 131 can connect the hydraulic end housing, the crosshead box 200 and the crankcase 100 together through the first threaded hole 141.

(A34)根据上述(A33)所述的柱塞泵，其特征在于，在所述曲轴箱100的靠近所述十字头箱200侧的表面上还设置有第二螺纹孔142，所述第二螺纹孔142至少从所述十字头箱200贯穿到所述曲轴箱100，并且第二螺栓132能够通过所述第二螺纹孔142至少将所述十字头箱200与所述曲轴箱100进行密封连接。(A34) The plunger pump according to the above (A33) is characterized in that a second threaded hole 142 is also provided on the surface of the crankcase 100 close to the crosshead case 200, and the second threaded hole 142 at least penetrates from the crosshead case 200 to the crankcase 100, and the second bolt 132 can seal and connect at least the crosshead case 200 and the crankcase 100 through the second threaded hole 142.

(A35)根据上述(A34)所述的柱塞泵，其特征在于，所述第二螺纹孔142沿所述第一螺纹孔141的外圈布置并与所述第一螺纹孔141之间具有一定间隔。(A35) The plunger pump according to the above (A34) is characterized in that the second threaded hole 142 is arranged along the outer circle of the first threaded hole 141 and has a certain distance between it and the first threaded hole 141.

(A36)根据上述(A35)所述的动力端壳体，其特征在于，所述第一螺纹孔141与所述第二螺纹孔142一对二地布置，并且彼此对应的一个所述第一螺纹孔141与两个所述第二螺纹孔142之间的位置连线构成三角形。(A36) The power end housing according to (A35) above is characterized in that the first threaded hole 141 and the second threaded hole 142 are arranged in a pair, and the position lines between the corresponding first threaded hole 141 and two corresponding second threaded holes 142 form a triangle.

(B1)一种用于柱塞泵的动力端壳体，其特征在于，包括：(B1) A power end housing for a plunger pump, characterized in that it comprises:

一体式曲轴箱100，所述曲轴箱100包括多个轴承座101和多个支撑立板102，所述支撑立板102用于支撑所述轴承座101，且所述支撑立板102沿所述轴承座101的轴线方向间隔排布，其中所述轴承座101的宽度由施加在所述轴承座101上的轴承的宽度限定。An integrated crankcase 100 includes a plurality of bearing seats 101 and a plurality of support plates 102, wherein the support plates 102 are used to support the bearing seats 101, and the support plates 102 are arranged at intervals along the axial direction of the bearing seats 101, wherein the width of the bearing seats 101 is limited by the width of the bearings applied to the bearing seats 101.

(B2)根据上述(B1)所述的动力端壳体，其特征在于，所述轴承座101包括位于所述曲轴箱100的两端的两个端部轴承座101以及若干个中段轴承座101，所述中段轴承座101位于所述两个端部轴承座101之间，其中各个所述中段轴承座101的宽度大于所述两个端部轴承座101中的每一个的宽度。(B2) The power end housing according to (B1) above is characterized in that the bearing seat 101 includes two end bearing seats 101 located at both ends of the crankcase 100 and a plurality of middle bearing seats 101, wherein the middle bearing seat 101 is located between the two end bearing seats 101, wherein the width of each middle bearing seat 101 is greater than the width of each of the two end bearing seats 101.

(B3)根据上述(B2)所述的动力端壳体，其特征在于，所述两个端部轴承座101中的位于所述曲轴箱100的减速箱连接侧的一个端部轴承座101的宽度比所述两个端部轴承座101中的另一个端部轴承座101的宽度宽。(B3) The power end housing according to (B2) above is characterized in that the width of one of the two end bearing seats 101 located on the reduction gearbox connection side of the crankcase 100 is wider than the width of the other end bearing seat 101 of the two end bearing seats 101.

(B4)根据上述(B1)所述的动力端壳体，其特征在于，所述支撑立板102之间的间距不同，并且相对于所述曲轴箱100的长度方向X的中心，所述支撑立板102之间的间距设置成对称，所述长度方向X与所述轴承座101的轴线方向平行。(B4) The power end housing according to (B1) above is characterized in that the spacing between the support vertical plates 102 is different, and the spacing between the support vertical plates 102 is set to be symmetrical relative to the center of the length direction X of the crankcase 100, and the length direction X is parallel to the axial direction of the bearing seat 101.

(B5)根据上述(B1)所述的动力端壳体，其特征在于，在所述支撑立板102上设置有减重凹槽109。(B5) The power end housing according to (B1) above is characterized in that a weight-reducing groove 109 is provided on the supporting vertical plate 102 .

(B6)根据上述(B5)所述的动力端壳体，其特征在于，所述减重凹槽109的起始边缘和终止边缘具有过渡圆角。(B6) The power end housing according to (B5) above is characterized in that the starting edge and the ending edge of the weight-reducing groove 109 have transition radius.

(B7)根据上述(B1)所述的动力端壳体，其特征在于，在所述支撑立板102的顶部设置有吊点凸台110，并且所述吊点凸台110与所述曲轴箱100的箱体连接处设置有过渡圆角。 (B7) The power end housing according to (B1) above is characterized in that a hanging point boss 110 is provided on the top of the supporting vertical plate 102, and a transition fillet is provided at the connection between the hanging point boss 110 and the crankcase 100.

(B8)根据上述(B1)所述的动力端壳体，其特征在于，所述曲轴箱100的底部包括支脚119，所述支脚119用于支撑所述曲轴箱100。(B8) The power end housing according to (B1) above is characterized in that the bottom of the crankcase 100 includes a support leg 119 , and the support leg 119 is used to support the crankcase 100 .

(B9)根据上述(B8)所述的动力端壳体，其特征在于，各个所述支撑立板102在所述曲轴箱100的前端侧和后端侧均包含至少一个所述支脚119，所述前端侧为所述曲轴箱100的与十字头箱200连接的一侧，所述后端侧为所述前端侧的相对侧。(B9) The power end housing according to (B8) above is characterized in that each of the supporting vertical plates 102 includes at least one support foot 119 on the front end side and the rear end side of the crankcase 100, the front end side being the side of the crankcase 100 connected to the crosshead case 200, and the rear end side being the opposite side of the front end side.

(B10)根据上述(B8)所述的动力端壳体，其特征在于，所述支脚119为在各个所述支撑立板102的底部设置的从所述曲轴箱100的前端侧延伸至后端侧的横向一体式支脚119’，所述前端侧为所述曲轴箱100的与十字头箱200连接的一侧，所述后端侧为所述前端侧的相对侧。(B10) The power end housing according to (B8) above is characterized in that the support foot 119 is a transverse integrated support foot 119' arranged at the bottom of each of the supporting vertical plates 102 and extending from the front end side to the rear end side of the crankcase 100, the front end side being the side of the crankcase 100 connected to the crosshead case 200, and the rear end side being the opposite side of the front end side.

(B11)根据上述(B8)所述的动力端壳体，其特征在于，所述支脚119为沿所述曲轴箱100的长度方向X从一端的所述支撑立板102延伸至另一端的所述支撑立板102的纵向一体式支脚119”，所述长度方向X与所述轴承座101的轴线方向平行。(B11) The power end housing according to (B8) above is characterized in that the support foot 119 is a longitudinal integrated support foot 119" extending from the support vertical plate 102 at one end to the support vertical plate 102 at the other end along the length direction X of the crankcase 100, and the length direction X is parallel to the axial direction of the bearing seat 101.

(B12)根据上述(B8)-(B11)中任一项所述的动力端壳体，其特征在于，所述支脚119,119’,119”的根部设置有坡口120，并且所述坡口120与所述曲轴箱100的箱体连接处设置有过渡圆角。(B12) The power end housing according to any one of (B8) to (B11) above is characterized in that a groove 120 is provided at the root of the support legs 119, 119', 119", and a transition fillet is provided at the connection between the groove 120 and the crankcase 100.

(B13)根据上述(B8)-(B11)中任一项所述的动力端壳体，其特征在于，所述支脚119,119’,119”上设置有减重凹槽121，所述减重凹槽121远离所述支脚119,119’,119”的底部接触面123，并且所述减重凹槽121的起始边缘和终止边缘具有过渡圆角。(B13) The power end housing according to any one of (B8) to (B11) above is characterized in that a weight-reducing groove 121 is provided on the support feet 119, 119', 119", the weight-reducing groove 121 is away from the bottom contact surface 123 of the support feet 119, 119', 119", and the starting edge and the ending edge of the weight-reducing groove 121 have transition radius.

(B14)根据上述(B1)所述的动力端壳体，其特征在于，在所述曲轴箱100的顶部104设置有至少一个油气分离器凸台125。(B14) The power end housing according to (B1) above is characterized in that at least one oil-gas separator boss 125 is provided on the top 104 of the crankcase 100 .

(B15)根据上述(B1)所述的动力端壳体，其特征在于，在所述曲轴箱100的底部105设置有至少一个回油口126。(B15) The power end housing according to (B1) above is characterized in that at least one oil return port 126 is provided at the bottom 105 of the crankcase 100 .

(B16)根据上述(B15)所述的动力端壳体，其特征在于，所述动力端壳体还包括一体式盖板128，在所述回油口126的外圈设置有回油盖板安装凸台127，并且所述一体式盖板128能够可拆卸地安装在所述回油盖板安装凸台127上以对所述回油口126进行密封。(B16) According to the power end housing described in (B15) above, it is characterized in that the power end housing also includes an integrated cover plate 128, and an oil return cover plate mounting boss 127 is provided on the outer ring of the oil return port 126, and the integrated cover plate 128 can be detachably mounted on the oil return cover plate mounting boss 127 to seal the oil return port 126.

(B17)根据上述(B1)所述的动力端壳体，其特征在于，所述曲轴箱100上设置有从壳体外表面朝向曲轴的方向贯穿的工艺窗129,129’，通过所述工艺窗129,129’能够观察和/或操作所述曲轴箱100内部的部件。(B17) The power end casing according to (B1) above is characterized in that the crankcase 100 is provided with a process window 129, 129' penetrating from the outer surface of the casing toward the crankshaft, and the components inside the crankcase 100 can be observed and/or operated through the process window 129, 129'.

(B18)根据上述(B1)所述的动力端壳体，其特征在于，在所述曲轴箱100的靠近十字头箱200侧的表面上设置有多个第一螺纹孔141，所述第一螺纹孔141用于通过第一螺栓131将所述曲轴箱100与所述十字头箱200连接。(B18) The power end housing according to (B1) above is characterized in that A plurality of first threaded holes 141 are provided on the surface close to the crosshead case 200 . The first threaded holes 141 are used to connect the crankcase 100 to the crosshead case 200 through first bolts 131 .

(B19)根据上述(B1)所述的动力端壳体，其特征在于，在所述曲轴箱100的靠近十字头箱200侧的表面上设置有密封面，所述密封面上具有密封槽133，所述曲轴箱100的连杆通孔位于所述密封槽133的内侧。(B19) The power end housing according to (B1) above is characterized in that a sealing surface is provided on the surface of the crankcase 100 close to the crosshead case 200, and a sealing groove 133 is provided on the sealing surface, and the connecting rod through hole of the crankcase 100 is located on the inner side of the sealing groove 133.

(B20)根据上述(B1)所述的动力端壳体，其特征在于，在所述曲轴箱100的靠近十字头箱200侧的表面上设置有通往所述轴承座101的润滑油孔，所述润滑油孔的位置与轴承外圈油孔的凹槽对齐。(B20) The power end housing according to (B1) above is characterized in that a lubricating oil hole leading to the bearing seat 101 is provided on the surface of the crankcase 100 close to the crosshead case 200, and the position of the lubricating oil hole is aligned with the groove of the oil hole of the outer ring of the bearing.

(B21)根据上述(B1)所述的动力端壳体，其特征在于，所述曲轴箱100是一体铸造成型的。(B21) The power end housing according to (B1) above is characterized in that the crankcase 100 is integrally cast.

(B22)根据上述(B1)所述的动力端壳体，其特征在于，所述曲轴箱100在各个所述支撑立板102之间包括多个第二加强筋103’，并且所述第二加强筋103’的延伸方向通过所述轴承座101的圆心。(B22) The power end housing according to (B1) above is characterized in that the crankcase 100 includes a plurality of second reinforcing ribs 103' between each of the supporting vertical plates 102, and the extension direction of the second reinforcing ribs 103' passes through the center of the bearing seat 101.

(B23)根据上述(B22)所述的动力端壳体，其特征在于，所述多个第二加强筋103’沿着所述轴承座101的座孔对称布置。(B23) According to the power end housing described in (B22) above, it is characterized in that the multiple second reinforcing ribs 103' are symmetrically arranged along the seat hole of the bearing seat 101.

(B24)根据上述(B22)所述的动力端壳体，其特征在于，所述多个第二加强筋103’在所述轴承座101的上下两侧布置，其中在上侧布置有三个上侧加强筋103’并且在下侧布置有两个下侧加强筋103’，所述两个下侧加强筋103’的位置分别位于底部回油口的两侧而不与所述底部回油口产生干扰。(B24) The power end housing according to (B22) above is characterized in that the plurality of second reinforcing ribs 103' are arranged on the upper and lower sides of the bearing seat 101, wherein three upper reinforcing ribs 103' are arranged on the upper side and two lower reinforcing ribs 103' are arranged on the lower side, and the positions of the two lower reinforcing ribs 103' are respectively located on both sides of the bottom oil return port without interfering with the bottom oil return port.

(B25)根据上述(B22)所述的动力端壳体，其特征在于，所述第二加强筋103’与所述支撑立板102之间设置有过渡坡口115，并且所述坡口115与所述支撑立板102之间具有过渡圆角116。(B25) According to the power end housing described in (B22) above, it is characterized in that a transition groove 115 is arranged between the second reinforcing rib 103' and the supporting vertical plate 102, and a transition fillet 116 is provided between the groove 115 and the supporting vertical plate 102.

(B26)根据上述(B22)所述的动力端壳体，其特征在于，所述第二加强筋103’的截面为矩形的。(B26) The power end housing according to (B22) above is characterized in that the cross-section of the second reinforcing rib 103' is rectangular.

(B27)一种柱塞泵，所述柱塞泵包括根据上述(B1)-(B26)中任一项所述的动力端壳体。(B27) A plunger pump, comprising a power end housing according to any one of (B1) to (B26) above.

(B28)根据上述(B27)所述的柱塞泵，其特征在于，还包括液力端壳体，并且所述动力端壳体还包括十字头箱200，所述液力端壳体、所述十字头箱200和曲轴箱100依次连接，其中第一螺纹孔141能够从所述液力端壳体贯穿到所述曲轴箱100，并且第一螺栓131能够通过所述第一螺纹孔141将所述液力端壳体、所述十字头箱200和曲轴箱100连接在一起。 (B28) The plunger pump according to the above (B27) is characterized in that it also includes a hydraulic end housing, and the power end housing also includes a crosshead box 200, the hydraulic end housing, the crosshead box 200 and the crankcase 100 are connected in sequence, wherein the first threaded hole 141 can pass through the hydraulic end housing to the crankcase 100, and the first bolt 131 can connect the hydraulic end housing, the crosshead box 200 and the crankcase 100 together through the first threaded hole 141.

(B29)根据上述(B28)所述的柱塞泵，其特征在于，在所述曲轴箱100的靠近所述十字头箱200侧的表面上还设置有第二螺纹孔142，所述第二螺纹孔142至少从所述十字头箱200贯穿到所述曲轴箱100，并且第二螺栓132能够通过所述第二螺纹孔142至少将所述十字头箱200与所述曲轴箱100进行密封连接。(B29) The plunger pump according to the above (B28) is characterized in that a second threaded hole 142 is also provided on the surface of the crankcase 100 close to the crosshead case 200, and the second threaded hole 142 at least penetrates from the crosshead case 200 to the crankcase 100, and the second bolt 132 can seal and connect at least the crosshead case 200 and the crankcase 100 through the second threaded hole 142.

(B30)根据上述(B29)所述的柱塞泵，其特征在于，所述第二螺纹孔142沿所述第一螺纹孔141的外圈布置并与所述第一螺纹孔141之间具有一定间隔。(B30) The plunger pump according to (B29) above is characterized in that the second threaded hole 142 is arranged along the outer circle of the first threaded hole 141 and has a certain distance from the first threaded hole 141.

(B31)根据上述(B30)所述的动力端壳体，其特征在于，所述第一螺纹孔141与所述第二螺纹孔142一对二地布置，并且彼此对应的一个所述第一螺纹孔141与两个所述第二螺纹孔142之间的位置连线构成三角形。(B31) The power end housing according to the above (B30) is characterized in that the first threaded hole 141 and the second threaded hole 142 are arranged in a pair, and the position lines between the corresponding first threaded hole 141 and two corresponding second threaded holes 142 form a triangle.

以上所述仅为本发明的实施例而已，并不用于限制本发明。对于本领域技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原理之内所作的任何修改、等同替换、改进等，均应包含在本发明的权利要求范围之内。 The above description is only an embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent substitution, improvement, etc. made within the spirit and principle of the present invention should be included in the scope of the claims of the present invention.

Claims

一种用于柱塞泵的动力端壳体，其特征在于，包括：A power end housing for a plunger pump, characterized by comprising:

一体式曲轴箱(100)，所述曲轴箱(100)包括多个轴承座(101)和多个支撑立板(102)，所述支撑立板(102)用于支撑所述轴承座(101)，且所述支撑立板(102)沿所述轴承座(101)的轴线方向间隔排布，所述曲轴箱(100)在各个所述支撑立板(102)之间包括第一加强筋(103)，其中所述轴承座(101)所受最大合力的方向与所述柱塞泵的柱塞的轴向方向之间的夹角为βmax，并且所述第一加强筋(103)与所述柱塞的轴向方向之间的夹角为第一夹角，所述第一夹角大于或等于0.8βmax，且小于或等于1.2βmax。An integrated crankcase (100), the crankcase (100) comprising a plurality of bearing seats (101) and a plurality of support plates (102), the support plates (102) being used to support the bearing seats (101), and the support plates (102) being arranged at intervals along the axial direction of the bearing seats (101), the crankcase (100) comprising a first reinforcing rib (103) between each of the support plates (102), wherein the angle between the direction of the maximum resultant force on the bearing seat (101) and the axial direction of the plunger of the plunger pump is βmax, and the angle between the first reinforcing rib (103) and the axial direction of the plunger is a first angle, and the first angle is greater than or equal to 0.8βmax and less than or equal to 1.2βmax.
根据权利要求1所述的动力端壳体，其特征在于，所述第一加强筋(103)至少设置于所述曲轴箱(100)的前端面(106)和/或后端面(107)上，所述前端面(106)是所述曲轴箱(100)的与十字头箱(200)连接侧的表面，并且所述后端面(107)是所述前端面(106)的相对侧的表面。The power end housing according to claim 1 is characterized in that the first reinforcing rib (103) is at least arranged on the front end face (106) and/or the rear end face (107) of the crankcase (100), the front end face (106) being the surface of the crankcase (100) on the side connected to the crosshead case (200), and the rear end face (107) being the surface on the opposite side of the front end face (106).
根据权利要求2所述的动力端壳体，其特征在于，在所述前端面(106)和所述后端面(107)上分别设置有一组所述第一加强筋(103)，并且每组内的所述第一加强筋(103)相对于所述柱塞泵的柱塞的轴向方向彼此对称。The power end housing according to claim 2 is characterized in that a group of the first reinforcing ribs (103) are respectively provided on the front end face (106) and the rear end face (107), and the first reinforcing ribs (103) in each group are symmetrical to each other relative to the axial direction of the plunger of the plunger pump.
根据权利要求3所述的动力端壳体，其特征在于，设置于所述前端面(106)上的所述一组第一加强筋(103)与设置于所述后端面(107)上的所述一组第一加强筋(103)相对于所述轴承座(101)的垂直中心线彼此对称。The power end housing according to claim 3 is characterized in that the group of first reinforcing ribs (103) arranged on the front end surface (106) and the group of first reinforcing ribs (103) arranged on the rear end surface (107) are symmetrical to each other relative to the vertical center line of the bearing seat (101).
根据权利要求3所述的动力端壳体，其特征在于，每组所述第一加强筋(103)包括两个所述第一加强筋(103)，所述两个第一加强筋(103)的延伸方向之间的夹角大于或等于1.8βmax，且小于或等于2.2βmax。The power end housing according to claim 3 is characterized in that each group of the first reinforcing ribs (103) includes two first reinforcing ribs (103), and the angle between the extension directions of the two first reinforcing ribs (103) is greater than or equal to 1.8βmax and less than or equal to 2.2βmax.
根据权利要求1所述的动力端壳体，其特征在于，所述曲轴箱(100)还在各个所述支撑立板(102)之间包括多个第二加强筋(103’)，并且所述第二加强筋(103’)的延伸方向通过所述轴承座(101)的圆心。 The power end housing according to claim 1 is characterized in that the crankcase (100) further includes a plurality of second reinforcing ribs (103') between each of the supporting vertical plates (102), and the extension direction of the second reinforcing ribs (103') passes through the center of the bearing seat (101).
根据权利要求6所述的动力端壳体，其特征在于，所述多个第二加强筋(103’)沿着所述轴承座(101)的座孔对称布置。The power end housing according to claim 6 is characterized in that the plurality of second reinforcing ribs (103') are symmetrically arranged along the seat hole of the bearing seat (101).
根据权利要求6所述的动力端壳体，其特征在于，所述多个第二加强筋(103’)在所述轴承座(101)的上下两侧布置，其中在上侧布置有三个上侧加强筋(103’)并且在下侧布置有两个下侧加强筋(103’)，所述两个下侧加强筋(103’)的位置分别位于底部回油口的两侧而不与所述底部回油口产生干扰。The power end housing according to claim 6 is characterized in that the plurality of second reinforcing ribs (103') are arranged on the upper and lower sides of the bearing seat (101), wherein three upper reinforcing ribs (103') are arranged on the upper side and two lower reinforcing ribs (103') are arranged on the lower side, and the positions of the two lower reinforcing ribs (103') are respectively located on both sides of the bottom oil return port without interfering with the bottom oil return port.
根据权利要求1-8中任一项所述的动力端壳体，其特征在于，所述第一加强筋(103)和/或所述第二加强筋(103’)与所述支撑立板(102)之间设置有过渡坡口(115)，并且所述坡口(115)与所述支撑立板(102)之间具有过渡圆角(116)。The power end housing according to any one of claims 1 to 8 is characterized in that a transition groove (115) is provided between the first reinforcing rib (103) and/or the second reinforcing rib (103') and the supporting vertical plate (102), and a transition fillet (116) is provided between the groove (115) and the supporting vertical plate (102).
一种用于柱塞泵的动力端壳体，其特征在于，包括：A power end housing for a plunger pump, characterized by comprising:

一体式曲轴箱(100)，所述曲轴箱(100)包括多个轴承座(101)和多个支撑立板(102)，所述支撑立板(102)用于支撑所述轴承座(101)，且所述支撑立板(102)沿所述轴承座(101)的轴线方向间隔排布，其中所述轴承座(101)的宽度由施加在所述轴承座(101)上的轴承的宽度限定。An integrated crankcase (100), the crankcase (100) comprising a plurality of bearing seats (101) and a plurality of support plates (102), the support plates (102) being used to support the bearing seats (101), and the support plates (102) being arranged at intervals along the axial direction of the bearing seats (101), wherein the width of the bearing seats (101) is defined by the width of the bearings applied to the bearing seats (101).
根据权利要求10所述的动力端壳体，其特征在于，所述轴承座(101)包括位于所述曲轴箱(100)的两端的两个端部轴承座(101)以及若干个中段轴承座(101)，所述中段轴承座(101)位于所述两个端部轴承座(101)之间，其中各个所述中段轴承座(101)的宽度大于所述两个端部轴承座(101)中的每一个的宽度。The power end housing according to claim 10 is characterized in that the bearing seat (101) includes two end bearing seats (101) located at both ends of the crankcase (100) and a plurality of middle bearing seats (101), and the middle bearing seat (101) is located between the two end bearing seats (101), wherein the width of each of the middle bearing seats (101) is greater than the width of each of the two end bearing seats (101).
根据权利要求11所述的动力端壳体，其特征在于，所述两个端部轴承座(101)中的位于所述曲轴箱(100)的减速箱连接侧的一个端部轴承座(101)的宽度比所述两个端部轴承座(101)中的另一个端部轴承座(101)的宽度宽。The power end housing according to claim 11 is characterized in that the width of one of the two end bearing seats (101) located on the reduction gearbox connection side of the crankcase (100) is wider than the width of the other end bearing seat (101) of the two end bearing seats (101).
根据权利要求11所述的动力端壳体，其特征在于，所述支撑立板(102)之间的间距不同，并且相对于所述曲轴箱(100)的长度方向(X)的中心，所述支撑立板(102)之间的间距设置成对称，所述长度方向(X)与所述轴承座(101)的轴线方向平行。The power end housing according to claim 11 is characterized in that the spacing between the support vertical plates (102) is different, and the spacing between the support vertical plates (102) is set symmetrically relative to the center of the length direction (X) of the crankcase (100), and the length direction (X) is parallel to the axis of the bearing seat (101). Direction parallel.
根据权利要求1或10所述的动力端壳体，其特征在于，在所述支撑立板(102)上设置有减重凹槽(109)。The power end housing according to claim 1 or 10, characterized in that a weight-reducing groove (109) is provided on the supporting vertical plate (102).
根据权利要求1或10所述的动力端壳体，其特征在于，在所述支撑立板(102)的顶部设置有吊点凸台(110)，并且所述吊点凸台(110)与所述曲轴箱(100)的箱体连接处设置有过渡圆角。The power end housing according to claim 1 or 10 is characterized in that a hanging point boss (110) is provided on the top of the supporting vertical plate (102), and a transition fillet is provided at the connection between the hanging point boss (110) and the crankcase (100).
根据权利要求1或10所述的动力端壳体，其特征在于，所述曲轴箱(100)的底部包括支脚(119)，所述支脚(119)用于支撑所述曲轴箱(100)。The power end housing according to claim 1 or 10, characterized in that the bottom of the crankcase (100) includes a support foot (119), and the support foot (119) is used to support the crankcase (100).
根据权利要求1或10所述的动力端壳体，其特征在于，在所述曲轴箱(100)的靠近十字头箱(200)侧的表面上设置有多个第一螺纹孔(141)，所述第一螺纹孔(141)用于通过第一螺栓(131)将所述曲轴箱(100)与所述十字头箱(200)连接。The power end housing according to claim 1 or 10 is characterized in that a plurality of first threaded holes (141) are provided on the surface of the crankcase (100) close to the crosshead case (200), and the first threaded holes (141) are used to connect the crankcase (100) to the crosshead case (200) through first bolts (131).
根据权利要求1或10所述的动力端壳体，其特征在于，所述曲轴箱(100)是一体铸造成型的。The power end housing according to claim 1 or 10 is characterized in that the crankcase (100) is integrally cast.
一种柱塞泵，所述柱塞泵包括根据权利要求1-18中任一项所述的动力端壳体。A plunger pump, comprising a power end housing according to any one of claims 1-18.
根据权利要求19所述的柱塞泵，其特征在于，还包括液力端壳体，并且所述动力端壳体还包括十字头箱(200)，所述液力端壳体、所述十字头箱(200)和曲轴箱(100)依次连接，其中第一螺纹孔(141)能够从所述液力端壳体贯穿到所述曲轴箱(100)，并且第一螺栓(131)能够通过所述第一螺纹孔(141)将所述液力端壳体、所述十字头箱(200)和曲轴箱(100)连接在一起。 The plunger pump according to claim 19 is characterized in that it also includes a hydraulic end housing, and the power end housing also includes a crosshead box (200), the hydraulic end housing, the crosshead box (200) and the crankcase (100) are connected in sequence, wherein a first threaded hole (141) can pass through the hydraulic end housing to the crankcase (100), and a first bolt (131) can connect the hydraulic end housing, the crosshead box (200) and the crankcase (100) together through the first threaded hole (141).