WO2016058451A1 - 一种双支撑离心泵的冷却液或加热液循环*** - Google Patents
一种双支撑离心泵的冷却液或加热液循环*** Download PDFInfo
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- WO2016058451A1 WO2016058451A1 PCT/CN2015/088223 CN2015088223W WO2016058451A1 WO 2016058451 A1 WO2016058451 A1 WO 2016058451A1 CN 2015088223 W CN2015088223 W CN 2015088223W WO 2016058451 A1 WO2016058451 A1 WO 2016058451A1
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- sealing gland
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- end seal
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
- F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/043—Shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
- F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
- F04D7/06—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
- F04D29/12—Shaft sealings using sealing-rings
- F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid pumps
- F04D29/128—Shaft sealings using sealing-rings especially adapted for liquid pumps with special means for adducting cooling or sealing fluid
Definitions
- the invention relates to a double supported centrifugal pump.
- it relates to a coolant or heated liquid circulation system for a dual-support centrifugal pump.
- the cooling passages are two sets of mutually independent cooling passages formed on the sealing glands 3, 5 on both sides of the double-supported centrifugal pump, that is, the cooling or heating liquid can only be respectively supported on the double support.
- the sealing glands 3, 5 on both sides of the centrifugal pump are circulated, and the pump shaft 1 that needs to be cooled or heated cannot be cooled or heated.
- a low-temperature circulating fluid such as water, oil, steam or nitrogen
- a low-temperature circulating fluid such as water, oil, steam or nitrogen
- the fluid flows from the stationary high-temperature components and then flows out, and the heat of the pump body is taken away.
- the fluid flowing out becomes a high-temperature fluid, and then flows through a cooler located outside the pump body, and the fluid passes through. After the cooler cools down, it becomes a cryogenic fluid, and then the fluid is reintroduced into the stationary components, and thus circulated to control the temperature of the pump body. This method is called cooling.
- the above cooler can be changed to a heater. Heating in this way is referred to as heating.
- Cooling or heating only on the surface of the rotating parts of the high temperature centrifugal pump for example: shaft or bushing
- the cooling fluid only contacts the partial surface of the rotating part of the centrifugal pump. In other words, the axial length of the fluid contacting the rotating part is short, so the flow area of the cooling liquid is small.
- the portion of the rotating component that is cooled or heated by the fluid is not at the core where the rotating component is most in need of cooling or heating.
- the cooling fluid is not in direct contact with the pump shaft.
- the stationary components are in contact with the atmosphere, so their temperature does not represent the temperature at the core of the device. Therefore, if you control their temperature well, you can't say that the problem is solved.
- the rotating parts of the high-temperature centrifugal pump are the parts that need to be cooled most. If it is always in a high temperature state, it will bring many disadvantages. Do not do too much analysis here.
- the rotating parts of the high-temperature centrifugal pump are also the parts that need to be heated most. If it is not fully heated, the consequences are also very serious, especially when the high-temperature centrifugal pump is started, and it is not done here. Too much analysis.
- the technical problem to be solved by the present invention is to provide a coolant or a heating liquid circulation system of a double-supported centrifugal pump capable of directly cooling or heating a rotating component part which is most in need of cooling or heating.
- a coolant or a heating liquid circulation system of a double-supported centrifugal pump which is formed in a double-supported centrifugal pump, and includes a pump shaft, a left sleeve sleeve sleeved around the outer circumference of the pump shaft, and a right
- the sleeve is respectively passed through the left atmospheric end seal static ring, the left atmospheric end seal moving ring, and the left media end seal static ring is sleeved on the outer left first sleeve of the left left sleeve and the second left seal
- the gland is respectively passed through the right atmospheric end seal static ring, the right atmospheric end seal moving ring and the right media end seal static ring to cover the first right seal gland and the second right seal on the outer circumference of the right sleeve a gland, the first left sealing gland, the second left sealing gland, the left sleeve, the pump shaft, the right sleeve, the first right sealing gland,
- the heat exchange liquid circulation passage includes a first passage formed on the first left seal gland and an upper port connected to the heat exchanger through an external pipe, formed in the a second passage between the first left sealing gland and the left atmospheric end sealing ring and extending through the left pumping ring, formed on the second left sealing gland, the left atmospheric end sealing ring, a third passage between the static end ring and the left sleeve, the left end of the media end forming an eighth passage on the left sleeve and the pump shaft, forming a fourth passage in the pump shaft, formed in The right sleeve and the ninth passage on the pump shaft are formed between the right sleeve, the right medium end seal static ring, the second right seal gland and the right atmosphere end seal ring a fifth passage formed between the first right sealing gland and the right atmospheric end sealing ring and passing through the sixth passage of the right pumping ring, and the first right sealing gland formed on the fifth sealing gland
- the upper and upper ports are connected to the seventh passage of the heat exchanger through an external line.
- the second channel formed between the first left sealing gland and the left atmospheric end sealing ring is provided with a left pumping ring formed on the first right sealing gland and the right atmosphere
- the sixth channel between the end seal moving rings is set to the right Side pumping ring.
- the fourth passage is formed inside the pump shaft in the axial direction of the pump shaft.
- the heat exchange liquid circulation passage includes a first passage formed on the first left seal gland and an upper port connected to the heat exchanger through an external pipe, formed in the a second passage between the first left sealing gland and the left atmospheric end sealing ring and extending through the left pumping ring, forming a left side atmospheric end sealing ring, a left media end sealing ring, a third passage between the second left sealing gland and the left sleeve, forming an eighth passage on the left sleeve, formed on the left sleeve, the inner side surface of the right sleeve, and the outer side of the pump shaft a fourth passage between the surfaces, a ninth passage formed on the right sleeve, formed on the right sleeve, the right medium end seal static ring, the second right seal gland, and the right atmosphere a fifth passage between the end sealing rings formed between the first right sealing gland and the right atmospheric end sealing ring and penetrating through the sixth passage of the right pumping ring (14), and formed in The first right side sealing gland and
- the second channel formed between the first left sealing gland and the left atmospheric end sealing ring is provided with a left pumping ring formed on the first right sealing gland and the right atmosphere
- a right pumping ring is disposed in the sixth passage between the end seal moving rings.
- the fourth passage is formed on the outer side of the pump shaft in the axial direction of the pump shaft.
- the coolant or heating liquid circulation system of a double-supported centrifugal pump of the present invention directly supplies cooling or heating to all rotating parts of the high-temperature centrifugal pump to the portion that is most in need of cooling or heating, so that the temperature of the rotating component is always Can be controlled within the set range.
- the invention has the following advantages:
- b can actively increase or decrease the flow of cooling or heating fluid.
- c can actively accelerate or slow down the flow rate of the cooling or heating fluid.
- FIG. 1 is a schematic view showing the external structure of a prior art double-support centrifugal pump
- FIG. 2 is a schematic view showing the internal structure of a prior art double-support centrifugal pump
- Figure 3 is a schematic view showing the external structure of the first embodiment of the double-support centrifugal pump of the present invention
- Figure 4 is a schematic view showing the internal structure of the first embodiment of the double-support centrifugal pump of the present invention.
- Figure 5 is a schematic view showing the internal structure of a second embodiment of the double-support centrifugal pump of the present invention.
- Figure 6 is a schematic view showing the structure of a pump shaft and a bushing of a second embodiment of the double-support centrifugal pump of the present invention
- Figure 7 is a cross-sectional view taken along line A-A of Figure 6.
- pump shaft 2 left bearing housing
- Impeller 16 left side atmospheric end seal static ring
- first channel 302 second channel
- the coolant circulation system of a double-supported centrifugal pump of the present invention is a system for directly supplying cooling or heating liquid to all rotating components in a high-temperature centrifugal pump that most needs cooling or heating.
- Making a circulating fluid with an initial temperature dependent on the machine The mechanical seal or throttling mechanism flows directly from the outside through the stationary component of the pump body into the rotating component body, and the circulating fluid not only rotates synchronously with the rotating component, but also flows axially along the rotating component to reach the core position where cooling or heating is most needed, sufficient
- the heat is taken away while the fluid continuously flows out of the rotating member, and the liquid flowing from the inside of the centrifugal pump to the external pipe of the centrifugal pump is heat-exchanged outside the centrifugal pump, and the temperature returns to the initial temperature.
- the fluid flows into the rotating part of the centrifugal pump, and the above process is repeated in sequence, and the heat exchange is continued to achieve the temperature control of the rotating parts of the
- a coolant circulation system of a double-supported centrifugal pump of the present invention is formed in a double-supported centrifugal pump, and includes a pump shaft 1 and a left sleeve sleeve sleeved around the outer circumference of the pump shaft 1.
- the gland 31 and the second left gland 32 are respectively sleeved on the outer circumference of the right sleeve 22 through the right atmospheric end seal static ring 18, the right atmospheric end seal moving ring 12 and the right media end seal static ring 13 respectively.
- a heat exchanger 7 is connected between the right sleeve 22, the first right sealing gland 51 and the second right sealing gland 52 via the external line 8 and is capable of causing the heat exchange liquid to be in the rotating part At the same time of simultaneous rotation, the heat exchange liquid circulation passage flows along the axial direction of the rotating member.
- the heat exchange liquid circulation passages are connected in sequence as shown by the arrows in FIGS. 3 and 4: formed on the first left seal gland 31 and the upper port is connected through the external pipe 8
- the first passage 201 of the heat exchanger 7 is formed between the first left sealing gland 31 and the left atmospheric end sealing ring 10 and penetrates the second passage 202 of the left pumping ring 9, formed in The second left sealing gland 32, the left atmospheric end sealing ring 10, the third channel 203 between the left media end sealing ring 11 and the left bushing 21 are formed on the left bushing 21 and an eighth passage 208 on the pump shaft 1, a fourth passage 204 formed in the pump shaft 1, a ninth passage 209 formed on the right sleeve 22 and the pump shaft 1, formed in the a fifth passage 205 between the right sleeve 22, the right media end seal static ring 13, the second right seal gland 52 and the right atmospheric end seal ring 12 formed on the first right side a sixth passage 206 between the sealing gland 51 and the right atmospheric end sealing ring 12 and extending through the
- the second channel 202 formed between the first left sealing gland 31 and the left atmospheric end sealing ring 10 is provided with a left pumping ring 9, which is formed on the first right sealing gland A right pumping ring 14 is disposed in the sixth passage 206 between the 51 and the right atmospheric end seal moving ring 12.
- the heat exchange liquid circulation passage may further include, as indicated by an arrow in FIG. 5, sequentially connected to each other: the first left seal gland formed on the first side 31 and the upper port are connected to the first passage 301 of the heat exchanger 7 through the external line 8, formed between the first left sealing gland 31 and the left atmospheric end sealing ring 10 and through the left
- the second passage 302 of the side pumping ring 9 is formed between the left atmospheric end seal moving ring 10, the left medium end seal static ring 11, the second left seal gland 32 and the left sleeve 21 a three-channel 303, an eighth passage 308 formed on the left sleeve 21, forming an eighth passage between the inner surface of the left sleeve 21, the right sleeve 22 and the outer surface of the pump shaft 1 304, a ninth passage 309 formed on the right sleeve 22, formed on the right sleeve 22, the right medium end seal static ring 13, the second right seal gland 52, and the right atmosphere end Sealing the
- the second channel 202 formed between the first left sealing gland 31 and the left atmospheric end sealing ring 10 is provided with a left pumping ring 9, which is formed on the first right sealing gland A right pumping ring 14 is disposed in the sixth passage 206 between the 51 and the right atmospheric end seal moving ring 12.
- the working process of the first embodiment of the coolant circulation system of the double-supported centrifugal pump of the present invention is that the liquid for heat exchange inside the double-supported centrifugal pump is sequentially connected from the heat exchanger 7 through the external conduit 8
- the first passage 201 in the first left sealing gland 31 is formed between the first left sealing gland 31 and the left atmospheric end sealing ring 10 and penetrates the second of the left pumping ring 9 a passage 202, formed in the second left sealing gland 32, the left side atmospheric end sealing ring 10, the left side media end sealing ring 11 and the left bushing 21, a third passage 203 formed in the
- the left sleeve 21 and the eighth passage 208 on the pump shaft 1 form a fourth passage 204 in the pump shaft 1, forming a ninth passage on the right sleeve 22 and the pump shaft 1.
- the seventh passage 207 in the first right sealing gland 51 exchanges heat with the rotating component inside the double-supported centrifugal pump, in particular, the pump shaft 1, and the liquid after heat exchange is located on the first right side.
- the seventh passage 207 in the sealing gland 51 flows out through the external line 8 into the heat exchanger 7 for heat exchange, at which time the temperature of the fluid returns to the initial temperature and then enters the first left seal again through the external line 8.
- the first passage 201 in the gland 31 continues to exchange heat with the rotating components inside the dual-support centrifugal pump. This cycle achieves heat exchange to the rotating components within the dual-supported centrifugal pump.
- the working process of the second embodiment of the coolant circulation system of a double-supported centrifugal pump of the present invention shown in FIG. 5 is the same as that of the first embodiment described above with reference to FIGS. 3 and 4, but only in the first embodiment.
- the liquid for heat exchange in the example is moved in the axial direction inside the pump shaft 1, and exchanges heat with the pump shaft 1.
- the liquid for heat exchange is axially moved in the gap between the outer surface of the pump shaft 1 and the inner surfaces of the left sleeve 21 and the right sleeve 22, and is heated to the pump shaft 1. exchange.
- the fluid material delivered by the centrifugal pump is limited by the refining or chemical process and the temperature is constant, that is, the material transfers heat to the rotating component
- the heat transfer takes time, using the centrifugal pump of the present invention.
- the rotating component undergoes a new heat exchange with the coolant circulation system flowing through the present invention when the temperature has not yet changed. Therefore, the temperature of the rotating member can always be controlled within a desired range.
- the fluid enters the first passage 201 from the heat exchanger 13 and exchanges heat with the first left sealing gland 31; the second passage 202 and the first left sealing gland 31, the left side The atmospheric end seal static ring 16, the left atmosphere end seal moving ring 10, the left pump effect ring 9 and the second left seal gland 32 exchange heat; enter the third passage 203 and the second left seal gland 32, left The side atmospheric end seal moving ring 10, the left side medium end seal static ring 11, the left side media end seal moving ring 17 and the left sleeve 21 exchange heat; enter the eighth passage 208 and the left sleeve 21, and the left side of the medium end seal The moving ring 17, the left side medium end seal static ring 11 and the pump shaft 1 exchange heat; enter the fourth passage 204 and the pump shaft 1 for heat exchange; enter the 209 channel and the pump shaft 1, the right sleeve 22, and the right medium end Sealing the moving ring 12, sealing the static ring 13 on the right side of the medium, performing heat exchange; entering the 205
- the right atmosphere end sealing ring 12 and the second right sealing gland 52 exchange heat; enter the sixth channel 206 and the second right sealing gland 52, the right atmosphere sealing ring 12, and the right pumping ring 14.
- the right atmospheric seal static ring 18 and the first right seal gland 51 exchange heat, and enter the seventh passage 207 to exchange heat with the first right seal gland 51.
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Abstract
一种双支撑离心泵的冷却液或加热液循环***,有套在泵轴(1)外周的左轴套(21)、右轴套(22)、通过左侧大气端密封静环(16)、左侧大气端密封动环(10)、左侧介质端密封静环(11)套在左轴套(21)外周的第一左侧密封压盖(31)和第二左侧密封压盖(32),通过右侧大气端密封静环(18)、右侧大气端密封动环(12)和右侧介质端密封静环(13)套在右轴套(22)外周的第一右侧密封压盖(51)和第二右侧密封压盖(52),在第一左侧密封压盖(31)、第二左侧密封压盖(32)、左轴套(21)、泵轴(1)、右轴套(22)、第一右侧密封压盖(51)和第二右侧密封压盖(52)之间形成有一条连接热交换器(7)使热交换液体在随旋转部件同步旋转时,又沿旋转部件的轴向流动的热交换液体循环通道。直接向最需要冷却或者加热的部位提供冷却或加热,使旋转部件的温度总是能够控制在设定的范围之内。
Description
本发明涉及一种双支撑离心泵。特别是涉及一种双支撑离心泵的冷却液或加热液循环***。
在炼油、化工产业里,高温离心泵在转动机械设备中扮演着重要角色,它的冷却或加热始终是一个重要的课题。
到目前为止所有方法大多都是针对离心泵静止部件进行冷却,例如:轴承箱外壳、机械密封压盖等,这一点从“API610附录B(标准性)冷却水和润滑***示意图”和“API682附录D(标准性附录)标准冲洗方案和辅助金属构件中标准密封冲洗方案02”就可以看出;对旋转部件的冷却也仅仅限于局部的表面,这一点从“API682附录D(标准性附录)标准冲洗方案和辅助金属构件中标准密封冲洗方案51、61、65A、65B、66A、66B和52、53A、53B、53C、54、55”就可以看出;冷却液接触到该部分旋转部件以后既不能完全与其同步旋转,又不能沿着其轴向流动,并且过流面积小。如图1、图2所示,冷却通道是分别形成在双支撑离心泵两侧的密封压盖3、5上的两组互不相通的冷却通道,即冷却或加热液体只能分别在双支撑离心泵两侧的密封压盖3、5内进行循环,而不能对需要进行冷却或加热的泵轴1进行冷却或加热。
除此之外,对于冷却泵体的静止部件:往泵壳,轴承箱和机械密封压盖的空心腔体内引入低温循环流体,例如:水、油、蒸汽或氮气等。该流体从这些静止的高温部件体内转一圈再流出去,把泵体的热量带走,流出以后的流体就变成了高温流体,然后流经位于泵体外部静止的冷却器,该流体经过冷却器冷却降温以后又变成低温流体,然后再把该流体重新引入到这些静止的部件体内,如此循环起来达到控制泵体温度的目的。这种方法被称做冷却。
同理,当泵需要加热的时候,把上述的冷却器改成加热器即可。用这种方法进行加热被称做加热。
目前还没有把这种流体直接引入到高温离心泵连续旋转运动的空心旋转零部件腔体内实现对其进行冷却或者加热的技术。
因此,目前在现有技术中对高温离心泵冷却或加热所存在的不足有:
(一)仅在高温离心泵旋转部件(例如:轴或轴套)表面进行冷却或加热:
1、冷却流体只接触离心泵旋转部件的局部表面,换句话说流体接触旋转部件的轴向长度很短,所以,冷却液体过流面积小。
2、流体所冷却或者加热的旋转部件的部位并不是位于旋转部件最需要冷却或者加热的核心部位。
3、流体在接触离心泵的旋转部件表面时无法进行轴向位移,所以,对流的效果差。
4、在整个旋转部件上无法做到想冷却哪就能冷却到哪。
5、冷却流体没有与泵轴直接接触。
(二)只能对泵壳、轴承箱和机械密封压盖这些泵体上的静止部件进行冷却或加热:
1、所述静止部件都与大气接触,所以,它们的温度不能代表设备核心部位的温度。因此,把它们的温度控制得再好也不能说问题就解决了。
2、无法准确测量与监督设备核心部位的精确温度与瞬时温度变化。
3、现有技术所冷却或加热的部位与设备真正需要冷却或加热的核心部位之间总是隔着新鲜的被输送的流体物料,换句话说就是物料会把热量传给转子,而热量传递又需要时间,高温离心泵核心部位的旋转部件所接触的物质绝大部分是新鲜的被输送的流体物料。这些流体物料根本来不及得到冷却或加热就流走了,换成了新的物料,这些新鲜流体物料受到炼油或化工工艺的限制而温度恒定。也就是说旋转部件的核心部位总是得不到来自现有冷却或加热的技术的关照,如同隔靴搔痒。
4、高温离心泵的旋转部件是最需要得到冷却的部件,如果它总是处在高温状态会带来很多不利因素,在这里不做过多分析。
5、同理,高温离心泵的旋转部件也是最需要加热的部件,它要是得不到充分的加热同样后果也很严重,尤其是在高温离心泵启动的时刻更是如此,在这里也不做过多分析。
发明内容
本发明所要解决的技术问题是,提供一种能够直接对最需要冷却或者加热的旋转着的零部件部位进行冷却或加热的双支撑离心泵的冷却液或加热液循环***。
本发明所采用的技术方案是:一种双支撑离心泵的冷却液或加热液循环***,形成在双支撑离心泵内,包括有泵轴、套在所述泵轴外周的左轴套、右轴套、分别通过左侧大气端密封静环、左侧大气端密封动环、左侧介质端密封静环套在所述左轴套外周的第一左侧密封压盖和第二左侧密封压盖,分别通过右侧大气端密封静环、右侧大气端密封动环和右侧介质端密封静环套在所述右轴套外周的第一右侧密封压盖和第二右侧密封压盖,在所述的第一左侧密封压盖、第二左侧密封压盖、左轴套、泵轴、右轴套、第一右侧密封压盖和第二右侧密封压盖之间形成有一条通过外部管路连接位于外部的热交换器且能够使热交换液体在随旋转部件同步旋转的同时,又沿旋转部件的轴向流动的热交换液体循环通道。
所述的热交换液体循环通道包括有依次相连通的:形成在所述的第一左侧密封压盖上且上端口通过外部管路连接所述热交换器的第一通道,形成在所述的第一左侧密封压盖和左侧大气端密封动环之间并且贯穿左侧泵效环的第二通道,形成在所述的第二左侧密封压盖、左侧大气端密封动环、左侧介质端密封静环和左轴套之间的第三通道,形成在所述的左轴套和泵轴上的第八通道,形成在所述的泵轴内的第四通道,形成在所述的右轴套和泵轴上的第九通道,形成在所述的右轴套、右侧介质端密封静环、第二右侧密封压盖和右侧大气端密封动环之间的第五通道,形成在所述的第一右侧密封压盖和右侧大气端密封动环之间并且贯穿右侧泵效环的第六通道,以及形成在所述的第一右侧密封压盖上且上端口通过外部管路连接所述热交换器的第七通道。
所述的形成在第一左侧密封压盖和左侧大气端密封动环之间的第二通道内设置有左侧泵效环,所述的形成在第一右侧密封压盖和右侧大气端密封动环之间的第六通道内设置有右
侧泵效环。
所述的第四通道是在所述泵轴的内部沿泵轴的轴向形成。
所述的热交换液体循环通道包括有依次相连通的:形成在所述的第一左侧密封压盖上且上端口通过外部管路连接所述热交换器的第一通道,形成在所述的第一左侧密封压盖和左侧大气端密封动环之间并且贯穿左侧泵效环的第二通道,形成在所述的左侧大气端密封动环、左侧介质端密封静环、第二左侧密封压盖和左轴套之间的第三通道,形成在所述的左轴套上的第八通道,形成在所述的左轴套、右轴套内侧表面和泵轴外侧表面之间的第四通道,形成在所述的右轴套上的第九通道,形成在所述的右轴套、右侧介质端密封静环、第二右侧密封压盖和右侧大气端密封动环之间的第五通道,形成在所述的第一右侧密封压盖和右侧大气端密封动环之间并且贯穿右侧泵效环(14)的第六通道,以及形成在所述的第一右侧密封压盖上且上端口通过外部管路连接所述热交换器的第七通道。
所述的形成在第一左侧密封压盖和左侧大气端密封动环之间的第二通道内设置有左侧泵效环,所述的形成在第一右侧密封压盖和右侧大气端密封动环之间的第六通道内设置有右侧泵效环。
所述的第四通道是沿泵轴的轴向形成在所述泵轴的外侧。
本发明的一种双支撑离心泵的冷却液或加热液循环***,是直接向最需要冷却或者加热的部位,即高温离心泵所有旋转着的部件提供冷却或加热,使旋转部件的温度总是能够控制在设定的范围之内。本发明具有如下优点:
1、克服了现有技术的不足。
2、在控制离心泵旋转部件的温度方面真正做到变被动为主动:
a,在离心泵旋转部件的整个轴向长度上需要冷却或加热到哪里,就可以通过设计把流道开到哪里,冷却或加热流体就流到哪里。
b,可以主动地加大或减少冷却或加热流体的流量。
c,可以主动地加快或减慢冷却或加热流体的流速。
3、通过测量刚从离心泵旋转部件的旋转腔体流出来的流体温度,就可以监督设备核心部位的精确温度与瞬时温度。这样能够及时和准确地发现问题,更早采取措施,确保设备安全运行。
4、不用加大太多的物质投入,与API610和API682标准不冲突也不排斥,利用方案52,方案53a、方案53b、方案53c、方案54、方案55以及所有具有双端面机械密封或两组节流机构的现有设备与方案中,都能够跟本发明并联以后同时使用。
5、使真正需要控制温度的旋转部件实现了温度的有效控制。
6、给生产制造高温离心泵行业,甚至炼油和化工行业提供了发展空间。因为炼油和化工行业必然逐步向更深加工的方向发展,化工残留物越来越少,工况温度越来越高,如果我们没有手段和技术来控制离心泵的温度,发展就会放慢。
7、也同样适应化工反应釜的搅拌转子和其它带有定子和转子的机械设备,例如:透平机、压缩机、风机、电动机、发电机、发动机、内燃机、涡轮机、螺杆泵、齿轮泵等等。
图1是现有技术的双支撑离心泵的外部结构示意图;
图2是现有技术的双支撑离心泵的内部结构示意图;
图3是本发明的双支撑离心泵第一实施例的外部结构示意图;
图4是本发明的双支撑离心泵第一实施例的内部结构示意图;
图5是本发明的双支撑离心泵第二实施例的内部结构示意图;
图6是本发明的双支撑离心泵第二实施例泵轴与轴套的结构示意图;
图7是图6中A-A的剖示图。
图中
1:泵轴 2:左侧轴承座
3:左侧密封压盖 4:泵壳
5:右侧密封压盖 6:右侧轴承座
7:热交换器 8:外部管路
9:左侧泵效环 10:左侧大气端密封动环
11:左侧介质端密封静环 12:右侧大气端密封动环
13:右侧介质端密封静环 14:右侧泵效环
15:叶轮 16:左侧大气端密封静环
17:左侧介质端密封动环 18:右侧大气端密封静环
19:右侧介质端密封动环 21:左轴套
22:右轴套 31:第一左侧密封压盖
32:第二左侧密封压盖 51:第一右侧密封压盖
52:第二右侧密封压盖 201:第一通道
202:第二通道 203:第三通道
204:第四通道 205:第五通道
206:第六通道 207:第七通道
208:第八通道 209:第九通道
301:第一通道 302:第二通道
303:第三通道 304:第四通道
305:第五通道 306:第六通道
307:第七通道 308:第八通道
309:第九通道
下面结合实施例和附图对本发明的一种双支撑离心泵的冷却液或加热液循环***做出详细说明。
本发明的一种双支撑离心泵的冷却液循环***,是一种直接向最需要冷却或者加热的高温离心泵中所有旋转部件提供冷却或加热液体的***。使一具有初始温度的循环流体依靠机
械密封或节流机构由外部经泵体的静止部件直接流进旋转部件体内,循环流体不但跟着旋转部件同步旋转,而且还沿着旋转部件轴向流动达到最需要冷却或加热的核心位置,充足地进行热交换以后,在流体不断地流出旋转部件的同时带走热量,从离心泵内部流到离心泵外部管路中的液体在离心泵外部进行热交换后,温度又回到了初始温度,在循环过程中该流体又流进了离心泵旋转部件的体内,依次循环重复上述过程,周而复始,持续进行热交换,从而达到了控制离心泵旋转零部件的温度。
如图3、图4所示,本发明的一种双支撑离心泵的冷却液循环***,形成在双支撑离心泵内,包括有泵轴1、套在所述泵轴1外周的左轴套21、右轴套22、分别通过左侧大气端密封静环16、左侧大气端密封动环10、左侧介质端密封静环11套在所述左轴套21外周的第一左侧密封压盖31和第二左侧密封压盖32,分别通过右侧大气端密封静环18、右侧大气端密封动环12和右侧介质端密封静环13套在所述右轴套22外周的第一右侧密封压盖51和第二右侧密封压盖52,在所述的第一左侧密封压盖31、第二左侧密封压盖32、左轴套21、泵轴1、右轴套22、第一右侧密封压盖51和第二右侧密封压盖52之间形成有一条通过外部管路8连接位于外部的热交换器7且能够使热交换液体在随旋转部件同步旋转的同时,又沿旋转部件的轴向流动的热交换液体循环通道。
所述的热交换液体循环通道如图3、图4中的箭头所示包括有依次相连通的:形成在所述的第一左侧密封压盖31上且上端口通过外部管路8连接所述热交换器7的第一通道201,形成在所述的第一左侧密封压盖31和左侧大气端密封动环10之间并且贯穿左侧泵效环9的第二通道202,形成在所述的第二左侧密封压盖32、左侧大气端密封动环10、左侧介质端密封静环11和左轴套21之间的第三通道203,形成在所述的左轴套21和泵轴1上的第八通道208,形成在所述的泵轴1内的第四通道204,形成在所述的右轴套22和泵轴1上的第九通道209,形成在所述的右轴套22、右侧介质端密封静环13、第二右侧密封压盖52和右侧大气端密封动环12之间的第五通道205,形成在所述的第一右侧密封压盖51和右侧大气端密封动环12之间并且贯穿右侧泵效环14的第六通道206,以及形成在所述的第一右侧密封压盖51上且上端口通过外部管路8连接所述热交换器7的第七通道207。其中,所述的第四通道204是在所述泵轴1的内部沿泵轴1的轴向形成。
所述的形成在第一左侧密封压盖31和左侧大气端密封动环10之间的第二通道202内设置有左侧泵效环9,所述的形成在第一右侧密封压盖51和右侧大气端密封动环12之间的第六通道206内设置有右侧泵效环14。
如图5、图6、图7所示,所述的热交换液体循环通道还可以是如图5中的箭头所示包括有依次相连通的:形成在所述的第一左侧密封压盖31上且上端口通过外部管路8连接所述热交换器7的第一通道301,形成在所述的第一左侧密封压盖31和左侧大气端密封动环10之间并且贯穿左侧泵效环9的第二通道302,形成在所述的左侧大气端密封动环10、左侧介质端密封静环11、第二左侧密封压盖32和左轴套21之间的第三通道303,形成在所述的左轴套21上的第八通道308,形成在所述的左轴套21、右轴套22的内表面和泵轴1的外表面之间的第八通道304,形成在所述的右轴套22上的第九通道309,形成在所述的右轴套22、右侧介质端密封静环13、第二右侧密封压盖52和右侧大气端密封动环12之间的第五通道305,
形成在所述的第一右侧密封压盖51和右侧大气端密封动环12之间并且贯穿右侧泵效环14的第六通道306,以及形成在所述的第一右侧密封压盖51上且上端口通过外部管路8连接所述热交换器7的第七通道307。
所述的形成在第一左侧密封压盖31和左侧大气端密封动环10之间的第二通道202内设置有左侧泵效环9,所述的形成在第一右侧密封压盖51和右侧大气端密封动环12之间的第六通道206内设置有右侧泵效环14。
本发明的一种双支撑离心泵的冷却液循环***第一实施例的工作过程是:用于对双支撑离心泵内部进行换热的液体从热交换器7通过外部管路8依次进入相连通的第一左侧密封压盖31中的第一通道201,形成在所述的第一左侧密封压盖31和左侧大气端密封动环10之间并且贯穿左侧泵效环9的第二通道202,形成在所述的第二左侧密封压盖32、左侧大气端密封动环10、左侧介质端密封静环11和左轴套21之间的第三通道203,形成在所述的左轴套21和泵轴1上的第八通道208,形成在所述的泵轴1内的第四通道204,形成在所述的右轴套22和泵轴1上的第九通道209,形成在所述的右轴套22、右侧介质端密封静环13、第二右侧密封压盖52和右侧大气端密封动环12之间的第五通道205,形成在所述的第一右侧密封压盖51和右侧大气端密封动环12之间并且贯穿右侧泵效环14的第六通道206,形成在第一右侧密封压盖51内的第七通道207,与双支撑离心泵内部的旋转部件进行热交换,特别是与泵轴1进行热交换,热交换后的液体从位于第一右侧密封压盖51内的第七通道207流出通过外部管路8进入热交换器7进行热交换后,此时流体的温度又回到了初始温度然后又通过外部管路8再次进入第一左侧密封压盖31中的第一通道201继续与双支撑离心泵内部的旋转部件进行换热。如此循环,实现了对双支撑离心泵内的旋转部件的热交换。
图5所示的本发明的一种双支撑离心泵的冷却液循环***第二实施例的工作过程与上述图3、图4所述的第一实施例的工作过程相同,只是在第一实施例中用于热交换的液体是在泵轴1的内部沿轴向进行移动,与泵轴1进行热交换。而在第二实施例中用于热交换的液体是在泵轴1的外表面与左轴套21、右轴套22的内表面之间的间隙内沿轴向移动,与泵轴1进行热交换。
在整个循环过程中,虽然离心泵输送的流体物料受到炼油或化工工艺的限制而温度恒定,也就是说物料会把热量传给旋转部件,但是,热量传递需要时间,采用本发明的离心泵的旋转部件在温度还没有来得及发生变化时又与流经本发明的冷却液循环***进行了新的热交换。因此,所述的旋转部件的温度总是能够控制在所希望的范围之内。
从图4中可以看出流体从热交换器13出来以后进入第一通道201与第一左侧密封压盖31进行热交换;进入第二通道202与第一左侧密封压盖31、左侧大气端密封静环16、左侧大气端密封动环10、左侧泵效环9和第二左侧密封压盖32进行热量交换;进入第三通道203与第二左侧密封压盖32、左侧大气端密封动环10、左侧介质端密封静环11、左侧介质端密封动环17和左轴套21进行热量交换;进入第八通道208与左轴套21、左侧介质端密封动环17、左侧介质端密封静环11和泵轴1进行热量交换;进入第四通道204与泵轴1进行热量交换;进入209通道与泵轴1、右轴套22、右侧介质端密封动环12、右侧介质端密封静环13、进行热量交换;进入205通道与右轴套22、右侧介质端密封动环19、右侧介质端密封静环
13、右侧大气端密封动环12和第二右侧密封压盖52进行热量交换;进入第六通道206与第二右侧密封压盖52、右侧大气密封动环12、右侧泵效环14、右侧大气密封静环18和第一右侧密封压盖51进行热交换;进入第七通道207与第一右侧密封压盖51进行热交换。
Claims (7)
- 一种双支撑离心泵的冷却液或加热液循环***,形成在双支撑离心泵内,包括有泵轴(1)、套在所述泵轴(1)外周的左轴套(21)、右轴套(22)、分别通过左侧大气端密封静环(16)、左侧大气端密封动环(10)、左侧介质端密封静环(11)套在所述左轴套(21)外周的第一左侧密封压盖(31)和第二左侧密封压盖(32),分别通过右侧大气端密封静环(18)、右侧大气端密封动环(12)和右侧介质端密封静环(13)套在所述右轴套(22)外周的第一右侧密封压盖(51)和第二右侧密封压盖(52),其特征在于,在所述的第一左侧密封压盖(31)、第二左侧密封压盖(32)、左轴套(21)、泵轴(1)、右轴套(22)、第一右侧密封压盖(51)和第二右侧密封压盖(52)之间形成有一条通过外部管路(8)连接位于外部的热交换器(7)且能够使热交换液体在随旋转部件同步旋转的同时,又沿旋转部件的轴向流动的热交换液体循环通道。
- 根据权利要求1所述的一种双支撑离心泵的冷却液或加热液循环***,其特征在于,所述的热交换液体循环通道包括有依次相连通的:形成在所述的第一左侧密封压盖(31)上且上端口通过外部管路(8)连接所述热交换器(7)的第一通道(201),形成在所述的第一左侧密封压盖(31)和左侧大气端密封动环(10)之间并且贯穿左侧泵效环(9)的第二通道(202),形成在所述的第二左侧密封压盖(32)、左侧大气端密封动环(10)、左侧介质端密封静环(11)和左轴套(21)之间的第三通道(203),形成在所述的左轴套(21)和泵轴(1)上的第八通道(208),形成在所述的泵轴(1)内的第四通道(204),形成在所述的右轴套(22)和泵轴(1)上的第九通道(209),形成在所述的右轴套(22)、右侧介质端密封静环(13)、第二右侧密封压盖(52)和右侧大气端密封动环(12)之间的第五通道(205),形成在所述的第一右侧密封压盖(51)和右侧大气端密封动环(12)之间并且贯穿右侧泵效环(14)的第六通道(206),以及形成在所述的第一右侧密封压盖(51)上且上端口通过外部管路(8)连接所述热交换器(7)的第七通道(207)。
- 根据权利要求2所述的一种双支撑离心泵的冷却液或加热液循环***,其特征在于,所述的形成在第一左侧密封压盖(31)和左侧大气端密封动环(10)之间的第二通道(202)内设置有左侧泵效环(9),所述的形成在第一右侧密封压盖(51)和右侧大气端密封动环(12)之间的第六通道(206)内设置有右侧泵效环(14)。
- 根据权利要求2所述的一种双支撑离心泵的冷却液或加热液循环***,其特征在于,所述的第四通道(204)是在所述泵轴(1)的内部沿泵轴(1)的轴向形成。
- 根据权利要求1所述的一种双支撑离心泵的冷却液或加热液循环***,其特征在于,所述的热交换液体循环通道包括有依次相连通的:形成在所述的第一左侧密封压盖(31)上且上端口通过外部管路(8)连接所述热交换器(7)的第一通道(301),形成在所述的第一左侧密封压盖(31)和左侧大气端密封动环(10)之间并且贯穿左侧泵效环(9)的第二通道(302),形成在所述的左侧大气端密封动环(10)、左侧介质端密封静环(11)、第二左侧密封压盖(32)和左轴套(21)之间的第三通道(303),形成在所述的左轴套(21)上的第八 通道(308),形成在所述的左轴套(21)、右轴套(22)内侧表面和泵轴(1)外侧表面之间的第四通道(304),形成在所述的右轴套(22)上的第九通道(309),形成在所述的右轴套(22)、右侧介质端密封静环(13)、第二右侧密封压盖(52)和右侧大气端密封动环(12)之间的第五通道(305),形成在所述的第一右侧密封压盖(51)和右侧大气端密封动环(12)之间并且贯穿右侧泵效环(14)的第六通道(306),以及形成在所述的第一右侧密封压盖(51)上且上端口通过外部管路(8)连接所述热交换器(7)的第七通道(307)。
- 根据权利要求5所述的一种双支撑离心泵的冷却液或加热液循环***,其特征在于,所述的形成在第一左侧密封压盖(31)和左侧大气端密封动环(10)之间的第二通道(302)内设置有左侧泵效环(9),所述的形成在第一右侧密封压盖(51)和右侧大气端密封动环(12)之间的第六通道(306)内设置有右侧泵效环(14)。
- 根据权利要求5所述的一种双支撑离心泵的冷却液或加热液循环***,其特征在于,所述的第四通道(304)是沿泵轴(1)的轴向形成在所述泵轴(1)的外侧。
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US10060446B2 (en) | 2018-08-28 |
CN104806574B (zh) | 2018-01-09 |
WO2016058454A1 (zh) | 2016-04-21 |
CN104235073A (zh) | 2014-12-24 |
US20170241437A1 (en) | 2017-08-24 |
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