WO2023168765A1 - 机封冷却结构及具有其的高压热水泵 - Google Patents

机封冷却结构及具有其的高压热水泵 Download PDF

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WO2023168765A1
WO2023168765A1 PCT/CN2022/083396 CN2022083396W WO2023168765A1 WO 2023168765 A1 WO2023168765 A1 WO 2023168765A1 CN 2022083396 W CN2022083396 W CN 2022083396W WO 2023168765 A1 WO2023168765 A1 WO 2023168765A1
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Prior art keywords
cooling
mechanical seal
cavity
pump body
main shaft
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PCT/CN2022/083396
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English (en)
French (fr)
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余敏
余梦琦
张丹艺
杨丹飞
周维坚
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浙江水泵总厂有限公司
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Publication of WO2023168765A1 publication Critical patent/WO2023168765A1/zh

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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
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/026—Selection of particular materials especially adapted for liquid pumps
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • 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

Definitions

  • the present application relates to the technical field related to high-pressure hot water pumps, and in particular to a mechanical seal cooling structure and a high-pressure hot water pump having the same.
  • centrifugal pumps are used to transport liquids with higher temperatures, such as boiler water, etc.
  • the medium temperature can reach 110°C-260°C.
  • this type of transported medium is usually subjected to high pressure, thereby affecting the centrifugal force.
  • the sealing performance of the pump has high requirements; seals such as O-rings in the mechanical seal of centrifugal pumps are prone to deterioration and failure due to high temperatures, which will lead to a decrease in the sealing performance of the centrifugal pump. Therefore, for high-pressure hot water pumps, the cooling of the mechanical seal is very important. important.
  • the seal standard flushing scheme PLAN23 (API682-2014, fourth edition) is generally self-flushing.
  • a line passing through an external heat exchanger is connected to the mechanical seal cavity.
  • the sealed pipeline enables the transport medium in the machine seal cavity to achieve self-circulation through the sealed pipeline, and the external heat exchanger cools the transport medium in the sealed pipeline.
  • a mechanical seal cooling structure with small footprint and low cost and a high-pressure hot water pump having the same are provided.
  • This application first provides a mechanical seal cooling structure, including a pump body, a cooling section, a main shaft, and a sealing assembly; the cooling section is fixed on the pump body, and the main shaft penetrates the cooling section to the pump body, A mechanical seal cavity is provided in the cooling section around the main shaft, and a cooling cavity is also provided in the cooling section around the mechanical seal cavity; the seal assembly includes a balance drum and a mechanical seal, and the balance drum is located at the The cooling section is close to the side of the pump body to connect the pump body and the mechanical seal cavity.
  • the mechanical seal is located on the side of the cooling section away from the pump body and is located in the mechanical seal cavity.
  • the mechanical seal cooling structure further includes a cooling component, the cooling component includes a cooling tube, the cooling tube is disposed in the cooling cavity, and both ends of the cooling tube are connected to the mechanical seal cavity respectively.
  • the machine seal cooling structure in this application sets cooling pipes with two ends connected to the machine seal cavity in the cooling cavity, so that the liquid in the machine seal cavity can realize self-circulation along the cooling pipes under the action of the pressure difference on both sides of the balance drum. , and conducts heat exchange with the coolant in the cooling cavity through the cooling tube to complete the heat exchange and cooling, greatly reducing the floor space and production cost of the cooling system. Only one set of cooling cavity inlet and outlet water pipes are needed to meet the cooling and cooling needs. Reduces the difficulty of subsequent inspection and maintenance.
  • the cooling tube includes two openings
  • the cooling assembly also includes an auxiliary impeller disposed in the mechanical seal cavity.
  • the auxiliary impeller is fixed on the main shaft and is connected with the cooling
  • the opening on the side of the tube close to the pump body corresponds to input the liquid in the mechanical seal cavity into the cooling tube.
  • the liquid in the mechanical seal cavity can be actively pumped into the cooling pipe, thereby increasing the flow rate of the liquid in the cooling pipe, thereby increasing the cooling effect on the mechanical seal.
  • the liquid inlet of the auxiliary impeller is toward the mechanical seal side, and the liquid outlet is toward the opening of the cooling pipe on the side close to the pump body.
  • the transport liquid returned to the mechanical seal cavity can be directly transported to the liquid inlet of the auxiliary impeller, thereby forming a complete internal circulation and avoiding the introduction of a large amount of high-temperature liquid on the pump body side into the mechanical seal cavity. A large amount of heat can cause mechanical seal failure.
  • the effective flow rate of the auxiliary impeller is 0.4kg/m, and the lift is 4m-5m.
  • the cooling assembly further includes a blocking member disposed in the mechanical seal cavity, and the blocking member is located between two openings of the cooling tube to block liquid from flowing out of the mechanical seal cavity. The side close to the pump body flows to the side of the mechanical seal.
  • the blocking effect of the blocking member can effectively prevent a large amount of high-temperature liquid in the pump body from flowing directly through the mechanical seal cavity to the mechanical seal without being cooled by the cooling pipe, thereby causing the sealing effect of the mechanical seal to fail.
  • the blocking member is a blocking block, which is located between the side wall of the mechanical sealing chamber and the outer peripheral surface of the auxiliary impeller, and is fixed to the side wall of the mechanical sealing chamber. connect.
  • the cooling tube is centered on the main shaft and is spirally arranged along the axial direction of the main shaft.
  • spiral arrangement can effectively increase the contact area between the cooling tube and the coolant, thereby increasing the heat transfer effect.
  • the water outlet of the cooling tube is fixed to the top wall of the mechanical seal cavity, and the water inlet is fixed to the bottom wall of the mechanical seal cavity.
  • the cooling tube is a metal tube.
  • a second aspect of this application provides a high-pressure hot water pump, including the above-mentioned mechanical seal cooling structure.
  • Figure 1 is a schematic cross-sectional structural diagram of a high-pressure hot water pump in some embodiments of the present application.
  • Figure 2 is an enlarged structural schematic diagram of position A in Figure 1.
  • Figure 3 is an enlarged structural schematic diagram of position B in Figure 2.
  • Cooling section 11. Mechanical seal cavity; 12. Cooling cavity; 20. Pump body; 30. Spindle; 40. Seal component; 41. Balance drum; 42. Mechanical seal; 50. Cooling component; 51 , cooling pipe; 511, water inlet; 512, water outlet; 52, auxiliary impeller; 521, liquid inlet; 522, liquid outlet; 53, blocking block; 100, machine seal cooling structure.
  • first and second are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of indicated technical features. Therefore, features defined as “first” and “second” may explicitly or implicitly include at least one of these features.
  • “plurality” means at least two, such as two, three, etc., unless otherwise expressly and specifically limited.
  • the first feature being "on” or “below” the second feature may mean that the first feature is in direct contact with the second feature, or the first feature and the second feature are in indirect contact. Contact through intermediaries.
  • the terms “above”, “above” and “above” the first feature of the second feature may mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is higher in level than the second feature.
  • "Below”, “below” and “beneath” the first feature of the second feature may mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature has a smaller horizontal height than the second feature.
  • a balance drum is usually installed between the pump body and the cooling section of a centrifugal pump.
  • the balance drum has a certain gap so that the liquid on both sides of the balance drum (liquid in the pump body and liquid in the mechanical seal cavity) is in a dynamic state. equilibrium state, thus being able to balance the axial force.
  • the centrifugal pump is connected to two sets of inlet and outlet pipes.
  • One set of water inlet and outlet pipes is connected to the cooling cavity.
  • Another set of inlet and outlet pipes are connected to the machine seal cavity and form a self-circulation. Due to the pressure difference on both sides of the balance drum (the liquid on one side of the pump body is the pressurized outlet liquid, its pressure is greater than the liquid in the machine seal cavity). , the liquid in the machine seal cavity will continue to flow along the self-circulating pipeline.
  • the self-circulating pipeline is located on the outer part of the centrifugal pump and will pass through an external heat exchanger.
  • Coolant will continue to flow through the heat exchanger, thereby making the self-circulating pipeline
  • the circulation pipeline in the heat exchanger can complete the cooling of the transport medium in the self-circulation pipeline through the heat exchange effect of the coolant, thereby reducing the temperature of the liquid in the mechanical seal cavity and achieving the cooling effect of the mechanical seal.
  • the traditional cooling solution occupies a large area due to the independent heat exchanger; and the pipeline connections are very complicated, including at least the cooling cavity pipeline, the mechanical seal cavity self-circulation pipeline and the heat exchanger coolant pipeline.
  • the three sets of pipelines are very cumbersome to repair and maintain in the later period, resulting in higher production and use costs of traditional cooling systems.
  • the present application provides a mechanical seal cooling structure 100, which includes a pump body 20, a cooling section 10, a main shaft 30, and a sealing assembly 40; the cooling section 10 is fixed on the pump body 20, and the main shaft 30 Penetrating the cooling section 10 into the pump body 20, the cooling section 10 is provided with an organic sealing cavity 11 surrounding the main shaft 30, and the cooling section 10 is also provided with a cooling cavity 12 surrounding the mechanical sealing cavity 11; the sealing assembly 40 includes a balance drum 41 and a mechanical sealing chamber 11. The seal 42 and the balance drum 41 are located on the side of the cooling section 10 close to the pump body 20 to communicate with the pump body 20 and the mechanical seal cavity 11.
  • the mechanical seal 42 is located on the side of the cooling section 10 away from the pump body 20 and is located in the mechanical seal cavity 11. ;
  • the mechanical seal cooling structure 100 also includes a cooling component 50.
  • the cooling component 50 includes a cooling tube 51.
  • the cooling tube 51 is disposed in the cooling cavity 12, and its two ends are connected to the mechanical seal cavity 11 respectively.
  • cooling pipes 51 By arranging cooling pipes 51 with both ends connected to the mechanical sealing cavity 11 in the cooling cavity 12, the liquid in the mechanical sealing cavity 11 can realize self-circulation along the cooling pipe 51 under the action of the pressure difference on both sides of the balance drum 41, and Through the cooling pipe 51, heat is exchanged with the cooling liquid in the cooling cavity 12 to complete the heat exchange and cooling. It is equivalent to building the self-circulation pipeline in the traditional technology into the cooling section 10, and replacing the heat exchanger in the traditional technology with the cooling cavity 12 and the continuously flowing coolant, which greatly reduces the floor space and production cost of the cooling system. , and at the same time, compared with the three sets of pipelines in the traditional technology, this application only requires one set of cooling cavity 12 inlet and outlet pipes to meet the cooling and cooling requirements, which greatly reduces the difficulty of subsequent inspection and maintenance.
  • the cooling assembly 50 also includes an auxiliary impeller 52 disposed in the mechanical seal cavity 11 .
  • the auxiliary impeller 52 is fixed on the main shaft 30 and corresponds to the opening of the cooling pipe 51 near the pump body 20 , to input the liquid in the mechanical seal cavity 11 into the cooling tube 51 .
  • the auxiliary impeller 52 By providing the auxiliary impeller 52, when the auxiliary impeller 52 rotates, the liquid in the mechanical seal cavity 11 can be actively pumped into the cooling pipe 51, thereby increasing the flow rate of the liquid in the cooling pipe 51, thereby increasing the cooling effect on the mechanical seal 42. This avoids the situation where the flow rate of the self-circulating liquid along the cooling pipe 51 is small and the cooling effect is insufficient due to only relying on the pressure difference on both sides of the balance drum 41 for driving.
  • auxiliary impeller 52 is fixedly mounted on the main shaft 30 so that the auxiliary impeller 52 can be directly driven by the main shaft 30 without the need for additional driving components.
  • a mechanical seal cooling structure 100 has a simple structure and is not easily damaged. It can effectively increase the service life in the high temperature and high pressure environment in the mechanical seal cavity 11 and reduce subsequent maintenance costs.
  • the fluid route in the mechanical seal cavity 11 is as follows: after the main shaft 30 starts to rotate, the cooling liquid begins to continuously flow into the cooling cavity 12, and the main shaft 30 will drive the auxiliary impeller 52 to rotate together, so that the liquid in the mechanical seal cavity 11
  • the liquid enters the auxiliary impeller 52 along the liquid inlet 521 of the auxiliary impeller 52, and after being pressurized, flows into the cooling pipe 51 along the liquid outlet 522 of the auxiliary impeller 52; at this time, the high-temperature liquid in the cooling pipe 51 will interact with the cooling chamber.
  • the cooling liquid in 12 undergoes heat exchange to achieve cooling of the transported liquid.
  • the cooled liquid will be returned to the mechanical seal cavity 11 from the opening of the cooling pipe 51 near the mechanical seal 42 to cool the mechanical seal 42 .
  • the cooled liquid can be returned to the mechanical seal cavity 11 through the opening of the cooling pipe 51 close to the mechanical seal 42, so as to further Increase the cooling effect on the mechanical seal 42.
  • the liquid inlet of the auxiliary impeller 52 is toward the side of the mechanical seal 42
  • the liquid outlet is toward the opening of the cooling pipe 51 on the side of the pump body 20 ; so that the cooling pipe 51 is close to the mechanical seal 42
  • the conveying liquid returned to the mechanical seal cavity 11 through the opening at can be directly conveyed to the liquid inlet 521 of the auxiliary impeller 52, thereby forming a complete internal circulation, and the mechanical seal 42 is realized by the conveying liquid in the internal circulation. Continued cooling.
  • the effective flow rate of the auxiliary impeller 52 is 0.4kg/m, and the lift is 4m-5m; under these impeller parameters, the liquid sent by the auxiliary impeller 52 passes through the cooling pipe 51 and is close to the machine.
  • the liquid outlet 522 at the seal 42 flows out, the liquid temperature just drops to close to or equal to the temperature of the cooling liquid in the cooling cavity 12 so that the heat exchange effect of the cooling tube 51 can be fully utilized.
  • the flow rate of the transported liquid will be reduced, so that the transported liquid is still in the cooling tube 51 in the cooling chamber 12, but its temperature has been reduced to the same as that in the cooling chamber 12.
  • the coolant temperatures are the same or close to each other, so that the heat exchange effect of the cooling pipe 51 from this position to the rear cannot be fully utilized, and the overall heat exchange efficiency is relatively low.
  • the flow rate of the transported liquid will increase, so that when the transported liquid flows out from the cooling pipe 51 close to the liquid outlet 522 of the mechanical seal 42 , the liquid temperature is still higher than that of the cooling chamber 12
  • the temperature of the internal coolant that is, the flow rate of the conveyed liquid is too fast, and since the driving power of the auxiliary impeller 52 comes from the rotation of the main shaft 30, excessively increasing the corresponding parameters of the auxiliary impeller 52 will lead to a waste of energy of the main shaft 30, resulting in The overall efficiency of the centrifugal pump decreases.
  • the cooling assembly 50 also includes a blocking member disposed in the mechanical seal cavity 11 .
  • the blocking member is located between the two openings of the cooling tube 51 to prevent the high-temperature liquid from flowing out after the auxiliary impeller 52 starts to work. It flows directly from the side of the mechanical seal chamber 11 close to the pump body 20 to the side of the mechanical seal 42 .
  • the blocking member prevents the rotating and non-rotating parts from seizing; on the other hand, it allows the coolant to flow from the side of the pump body 20 to the mechanical seal 42 to ensure that the machine is sealed in the initial state.
  • the chamber 11 can be filled with coolant.
  • the blocking member By providing the blocking member, it can effectively prevent a large amount of high-temperature liquid in the pump body 20 from flowing directly through the mechanical seal cavity 11 to the mechanical seal 42 without being cooled by the cooling pipe 51 , thereby causing the sealing effect of the mechanical seal 42 to fail. occur.
  • the blocking member is a blocking block 53.
  • the blocking block 53 is located between the side wall of the mechanical sealing chamber 11 and the outer peripheral surface of the auxiliary impeller 52, and is fixedly connected to the side wall of the mechanical sealing chamber 11; Through the narrow gap at the balance drum 41 and the gap between the blocking block 53 and the outer peripheral surface of the auxiliary impeller 52, an effect equivalent to a labyrinth seal can be formed, further optimizing the blocking effect and preventing high-temperature liquid from directly flowing into the mechanical seal 42.
  • the cooling pipe 51 is centered on the main shaft 30 and is spirally arranged along the axial direction of the main shaft 30 to increase the contact area between the cooling pipe 51 and the cooling liquid in the cooling cavity 12 as much as possible, that is, to increase the cooling pipe.
  • the heat exchange area is 51, thereby increasing the heat exchange effect of the cooling pipe 51.
  • the water outlet 512 of the cooling pipe 51 is fixed to the top wall of the mechanical seal cavity 11
  • the water inlet 511 is fixed to the bottom wall of the mechanical seal cavity 11 ; due to the different liquid temperatures, the density will exist. The difference is that usually high-temperature liquids have lower density and are located on the upper side, while low-temperature liquids have higher density and are located on the lower side;
  • the high-temperature liquid located on the upper side of the mechanical sealing cavity 11 can directly enter the cooling pipe 51 from the water outlet 512 , and the low-temperature liquid after cooling by the cooling pipe 51 The liquid can flow back to the bottom of the mechanical seal cavity 11 through the water inlet 511 of the cooling pipe 51, which is beneficial to the circulation of the cooling liquid.
  • the cooling tube 51 is a metal tube; metal material has relatively excellent heat transfer efficiency, and using a metal tube as the cooling tube 51 can effectively increase the heat exchange effect of the cooling tube 51 ; in some embodiments , the cooling tube 51 is a copper tube.
  • a second aspect of this application provides a high-pressure hot water pump, which includes the above-mentioned mechanical seal cooling structure.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

一种机封冷却结构(100)及具有其的高压热水泵。机封冷却结构(100)包括泵体(20)、冷却段(10)、主轴(30)、以及密封组件(40)；冷却段(10)固设于泵体(20)，主轴(30)贯穿冷却段(10)至泵体(20)内，冷却段(10)内环绕主轴(30)开设有机封腔(11)，冷却段(10)内还开设有环绕机封腔(11)开设的冷却腔(12)；密封组件(40)包括平衡鼓(41)以及机械密封(42)；机封冷却结构(100)还包括冷却组件(50)，冷却组件(50)包括设置于冷却腔(12)内的冷却管(51)，冷却管(51)的两端分别与机封腔(11)连通。

Description

机封冷却结构及具有其的高压热水泵
相关申请
本申请要求2022年3月9日申请的，申请号为202210230768.2，发明名称为“机封冷却结构及具有其的高压热水泵”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及高压热水泵相关技术领域，特别是涉及一种机封冷却结构及具有其的高压热水泵。
背景技术
部分离心泵用于输送温度较高的液体，如锅炉水等，其介质温度能达到110℃-260℃，为保证输送介质保持液体状态，此类输送介质通常会被施以高压，从而对离心泵的密封性具有较高要求；而离心泵机械密封中的O形圈等密封件容易因高温导致变质失效，会导致离心泵的密封性下降，因此对于高压热水泵，机械密封的冷却降温十分重要。
目前，对于机械密封的降温有多种不同的标准冲洗方案，其中，密封标准冲洗方案PLAN23(API682-2014，第四版)一般为自冲洗，在机封腔上连接一条经过外置换热器的密封管路，使得机封腔内的输送介质能够经过该密封管路实现自循环，且外置换热器对密封管路内的输送介质实现降温。
但是，此类换热系统虽然对机械密封的降温效果明显，但占地面积较大，且管路连接十分复杂，换热系统整体成本较高。
发明内容
根据本申请的各种实施例，提供一种占地小、成本低的机封冷却结构及具有其的高压热水泵。
本申请首先提供一种机封冷却结构，包括泵体、冷却段、主轴、以及密封组件；所述冷却段固设于所述泵体，所述主轴贯穿所述冷却段至所述泵体内，所述冷却段内环绕所述主轴开设有机封腔，所述冷却段内还开设有环绕所述机封腔开设的冷却腔；所述密封组件包括平衡鼓以及机械密封，所述平衡鼓位于所述冷却段靠近所述泵体的一侧，以连通所述泵体与所述机封腔，所述机械密封位于所述冷却段远离所述泵体的一侧且位于所述机封腔内；所述机封冷却结构还包括冷却组件，所述冷却组件包括冷却管，所述冷却管设置于所述冷却腔内，且所述冷却管的两端分别与所述机封腔连通。
本申请中机封冷却结构，通过在冷却腔内设置两端分别与机封腔连通的冷却管，使得机封腔内的液体能够在平衡鼓两侧压差作用下，沿冷却管实现自循环，并通过冷却管，与冷却腔内的冷却液进行热交换，完成换热降温，大大减少冷却系统的占地面积以及生产成本，仅需要一组冷却腔进出水管即可满足冷却降温需求，大大减少了后续检修维护的难度。
在其中一个实施例中，所述冷却管包括两个开口，所述冷却组件还包括设置于所述机封腔内的辅助叶轮，所述辅助叶轮固设于所述主轴，且与所述冷却管靠近所述泵体一侧的开口对应，以将所述机封腔内的液体输入至所述冷却管内。
可以理解的是，辅助叶轮转动时能够将机封腔内的液体主动泵送至冷却管内，从而增加冷却管内液体的流速，进而增加对机械密封的冷却效果。
在其中一个实施例中，所述辅助叶轮的进液口朝向所述机械密封一侧，出液口朝向所述冷却管靠近所述泵体一侧的开口。
可以理解的是，回输至机封腔内的输送液体，能够在直接输送至辅助叶轮的进液口，从而形成一完整的内循环，避免因泵体侧的高温液体大量进入机封腔引入大量热量，导致机械密封失效的情况发生。
在其中一个实施例中，所述辅助叶轮的有效流量为0.4kg/m，扬程为4m-5m。
可以理解的是，该参数下，辅助叶轮送输送的液体在经过冷却管并从靠近机械密封处的出液口流出时，液体温度恰好降低至与冷却腔内冷却液的温度接近或相等，以使得冷却管的换热效果能够得到充分利用。
在其中一个实施例中，所述冷却组件还包括设置于所述机封腔内的阻挡件，所述阻挡件位于所述冷却管的两个开口之间，以阻挡液体从所述机封腔靠近所述泵体的一侧流至所述机械密封一侧。
可以理解的是，阻挡件的阻挡作用能够有效避免泵体内的高温液体未经过冷却管的降温，大量的直接通过机封腔流至机械密封处，从而导致机械密封的密封效果失效的情况发生。
在其中一个实施例中，所述阻挡件为阻挡块，所述阻挡块位于所述机封腔的侧壁与所述辅助叶轮的外周面之间，且与所述机封腔的侧壁固定连接。
在其中一个实施例中，所述冷却管以所述主轴为中心，沿所述主轴的轴线方向螺旋设置。
可以理解的是，螺旋设置能够有效增加冷却管与冷却液的接触面积，从而增加换热效果。
在其中一个实施例中，所述冷却管的出水口与所述机封腔的顶壁固设， 入水口与所述机封腔的底壁固设。
可以理解的是，根据液体受热后的性质，本申请中冷却管的出水口与入水口的设计有利于冷却液的循环。
在其中一个实施例中，所述冷却管为金属管。
本申请第二方面提供一种高压热水泵，包括上述的机封冷却结构。
本申请的一个或多个实施例的细节在下面的附图和描述中提出。本申请的其它特征、目的和优点将从说明书、附图以及权利要求书变得明显。
附图说明
为了更清楚地说明本申请实施例或传统技术中的技术方案，下面将对实施例或传统技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅是本申请的一些实施例，对于本领域普通技术人员而言，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1为本申请的一些实施例中高压热水泵的剖视结构示意图。
图2为图1中A处的放大结构示意图。
图3为图2中B处的放大结构示意图。
附图标记：10、冷却段；11、机封腔；12、冷却腔；20、泵体；30、主轴；40、密封组件；41、平衡鼓；42、机械密封；50、冷却组件；51、冷却管；511、入水口；512、出水口；52、辅助叶轮；521、进液口；522、出液口；53、阻挡块；100、机封冷却结构。
具体实施方式
为使本申请的上述目的、特征和优点能够更加明显易懂，下面结合附图 对本申请的具体实施方式做详细的说明。在下面的描述中阐述了很多具体细节以便于充分理解本申请。但是本申请能够以很多不同于在此描述的其它方式来实施，本领域技术人员可以在不违背本申请内涵的情况下做类似改进，因此本申请不受下面公开的具体实施例的限制。
需要说明的是，当组件被称为“固定于”或“设置于”另一个组件，它可以直接在另一个组件上或者也可以存在居中的组件。当一个组件被认为是“连接”另一个组件，它可以是直接连接到另一个组件或者可能同时存在居中组件。本申请的说明书所使用的术语“垂直的”、“水平的”、“上”、“下”、“左”、“右”以及类似的表述只是为了说明的目的，并不表示是唯一的实施方式。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。在本申请的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本申请中，除非另有明确的规定和限定，第一特征在第二特征“上”、“下”可以是第一特征直接和第二特征接触，或第一特征和第二特征间接地通过中间媒介接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅表示第一特征水平高度小于第二特征。
除非另有定义，本申请的说明书所使用的所有的技术和科学术语与属于本申请的技术领域的技术人员通常理解的含义相同。在本申请的说明书中所 使用的术语只是为了描述具体的实施方式的目的，不是旨在于限制本申请。本申请的说明书所使用的术语“及/或”包括一个或多个相关的所列项目的任意的和所有的组合。
传统技术中，离心泵的泵体与冷却段之间通常设置有平衡鼓，平衡鼓具有一定缝隙，使得位于平衡鼓两侧的液体(泵体内的液体以及机封腔内的液体)处于一动态平衡状态，从而能够起到平衡轴向力的作用。
但是，对于高压热水泵而言，通过平衡鼓进入机封腔的高温液体，会导致机械密封中的O形圈等零件变质失效，从而导致机械密封的寿命及密封效果受到影响。
在目前的PLAN23密封标准冲洗方案中，离心泵连接两组进出水管。其中一组进出水管连接冷却腔，通过持续通入冷却液，带走冷却段内的热量，从而完成间接完成对机械密封的降温。另一组进出水管连接机封腔，且形成一自循环，由于平衡鼓两侧的压差作用(泵体一侧的液体为经过增压的出口液体，其压力大于机封腔内的液体)，机封腔内的液体会沿自循环管路持续流动，该自循环管路位于离心泵外侧部分的管道，会经过一外置换热器，换热器内持续通有冷却液，从而使得自循环管路在换热器内能够通过冷却液的换热作用，完成对自循环管路内的输送介质的降温，进而降低机封腔内的液体温度，达到对机械密封降温的效果。
但是，传统冷却方案中，由于具有独立的换热器，占地面积较大；且管路连接十分复杂，至少包括冷却腔管路、机封腔自循环管路以及换热器冷却液管路三组管路，在后期检修维护时十分繁琐，导致传统冷却系统的生产及使用成本均较高。
请参阅图1和图2所示，本申请提供一种机封冷却结构100，包括泵体 20、冷却段10、主轴30、以及密封组件40；冷却段10固设于泵体20，主轴30贯穿冷却段10至泵体20内，冷却段10内环绕主轴30开设有机封腔11，冷却段10内还开设有环绕机封腔11开设的冷却腔12；密封组件40包括平衡鼓41以及机械密封42，平衡鼓41位于冷却段10靠近泵体20的一侧，以连通泵体20与机封腔11，机械密封42位于冷却段10远离泵体20的一侧且位于机封腔11内；机封冷却结构100还包括冷却组件50，冷却组件50包括冷却管51，冷却管51设置于冷却腔12内，且两端分别与机封腔11连通。
通过在冷却腔12内设置两端分别与机封腔11连通的冷却管51，使得机封腔11内的液体能够在平衡鼓41两侧压差作用下，沿冷却管51实现自循环，并通过冷却管51，与冷却腔12内的冷却液进行热交换，完成换热降温。相当于将传统技术中的自循环管路内置于冷却段10内，并用冷却腔12以及持续通入的冷却液代替了传统技术中的换热器，大大减少冷却系统的占地面积以及生产成本，同时相较于传统技术中的三组管路，本申请中仅需要一组冷却腔12进出水管即可满足冷却降温需求，大大减少了后续检修维护的难度。
在图2所示的实施例中，冷却组件50还包括设置于机封腔11内的辅助叶轮52，辅助叶轮52固设于主轴30，且与冷却管51靠近泵体20一侧的开口对应，以将机封腔11内的液体输入至冷却管51内。
通过设置辅助叶轮52，使得辅助叶轮52转动时能够将机封腔11内的液体主动泵送至冷却管51内，从而增加冷却管51内液体的流速，进而增加对机械密封42的冷却效果，避免因仅依靠平衡鼓41两侧压差驱动，导致沿冷却管51自循环流动的液体流速较小，冷却效果不足的情况发生。
此外，将辅助叶轮52固设于主轴30，使得辅助叶轮52能够由主轴30直接带动，无需设置额外的驱动件进行驱动。这样的机封冷却结构100结构简 单，不易损坏，能够有效增加在机封腔11内的高温高压环境下的使用寿命，降低后续维护成本。
本申请中，机封腔11内的流体路线如下：主轴30开始转动后，冷却腔12内开始持续通入冷却液，主轴30会带动辅助叶轮52一同转动，从而使得机封腔11内的液体沿辅助叶轮52的进液口521进入辅助叶轮52，并获得增压后，沿辅助叶轮52的出液口522流至冷却管51内；此时，冷却管51内的高温液体会与冷却腔12内的冷却液发生热交换，从而实现输送液体的降温，降温后的液体会从冷却管51靠近机械密封42处的开口回输至机封腔11内，以实现对机械密封42的降温。
通过将辅助叶轮52设置为与冷却管51靠近泵体20一侧的开口对应，以使得经冷却后的液体能够通过冷却管51靠近机械密封42的开口回输至机封腔11中，以进一步增加对机械密封42的冷却效果。
在图3所示的实施例中，辅助叶轮52的进液口朝向机械密封42一侧，出液口朝向冷却管51靠近泵体20一侧的开口；以使得经冷却管51靠近机械密封42处的开口回输至机封腔11内的输送液体，能够在直接输送至辅助叶轮52的进液口521，从而形成一完整的内循环，通过内循环内的输送液体实现对机械密封42的持续降温。
与辅助叶轮52的进液口朝向泵体20一侧相比，能够减少因泵体20侧的高温液体大量进入机封腔11所引入的热量，进而增加对机械密封42的冷却效果。
在图2所示的实施例中，辅助叶轮52的有效流量为0.4kg/m，扬程为4m-5m；在该叶轮参数下，辅助叶轮52送输送的液体在经过冷却管51并从靠近机械密封42处的出液口522流出时，液体温度恰好降低至与冷却腔12内 冷却液的温度接近或相等，以使得冷却管51的换热效果能够得到充分利用。
若在此基础上降低辅助叶轮52的相应参数，会使得所输送液体的流速降低，从而使得输送液体仍处于冷却腔12内的冷却管51内，但其温度已经降低至与冷却腔12内的冷却液温度相同或接近，从而导致从该位置往后部分的冷却管51的换热效果无法得到充分利用，整体换热效率相对较低。
若在此基础上增加辅助叶轮52的相应参数，会使得所输送液体的流速增加，从而使得输送液体从冷却管51靠近机械密封42的出液口522流出时，液体温度仍高于冷却腔12内冷却液的温度，即输送液体的流速过快，而由于辅助叶轮52的驱动动力来源于主轴30的转动，因此，过度增加辅助叶轮52的相应参数，会导致主轴30能量的浪费，从而导致离心泵整体效率下降。
在图2所示的实施例中，冷却组件50还包括设置于机封腔11内的阻挡件，阻挡件位于冷却管51的两个开口之间，以防止辅助叶轮52开始工作后，高温液体从机封腔11靠近泵体20的一侧直接流至机械密封42一侧。
阻挡件与辅助叶轮52之间存在一定间隙，一方面防止转动部件与非转动部件咬死；另一方面允许冷却液从泵体20一侧流至机械密封42处，以保证初始状态下机封腔11能够被冷却液充满。
通过设置阻挡件，能够有效避免泵体20内的高温液体，未经过冷却管51的降温，大量的直接通过机封腔11流至机械密封42处，从而导致机械密封42的密封效果失效的情况发生。
在本申请中，经过平衡鼓41进入机封腔11的高温液体，在阻挡件的阻挡作用下，大部分进入冷却管51，小部分液体仍然可能经过阻挡件直接流至机械密封42处，但是，由于冷却管51靠近机械密封42侧的开口会持续输出经降温后的液体，降温后的液体会与上述的小部分高温液体混合，避免液体 温度过高对机械密封42造成影响。
在图3所示的实施例中，阻挡件为阻挡块53，阻挡块53位于机封腔11的侧壁与辅助叶轮52的外周面之间，且与机封腔11的侧壁固定连接；通过平衡鼓41处的狭小缝隙，以及阻挡块53与辅助叶轮52外周面之间的缝隙，能够形成等同于迷宫密封的效果，进一步优化阻挡效果，避免高温液体直接流入机械密封42处。
在图2所示的实施例中，冷却管51以主轴30为中心，沿主轴30的轴线方向螺旋设置；以尽可能增加冷却管51与冷却腔12内冷却液的接触面积，即增加冷却管51的换热面积，从而能够起到增加冷却管51换热效果的作用。
在图2所示的实施例中，冷却管51的出水口512与机封腔11的顶壁固设，入水口511与机封腔11的底壁固设；由于液体温度不同时密度会存在差别，通常高温液体密度较低，位于上侧，而低温液体密度较高，位于下侧；
通过将冷却管51的出水口512与机封腔11的顶部固设，使得位于机封腔11上侧的高温液体能够从出水口512直接进入冷却管51中，而冷却管51冷却后的低温液体，能够通过冷却管51的入水口511回流至机封腔11的底部，有利于冷却液的循环。
在图2所示的实施例中，冷却管51为金属管；金属材质具有较为优秀的热传递效率，将金属管作为冷却管51，能够有效增加冷却管51的换热效果；在一些实施例中，冷却管51为紫铜管。
本申请第二方面提供一种高压热水泵，该高压热水泵包括上述的机封冷却结构。
以上所述实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这 些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。
以上所述实施例仅表达了本申请的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对申请专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本申请构思的前提下，还可以做出若干变形和改进，这些都属于本申请的保护范围。因此，本申请的专利保护范围应以所附权利要求为准。

Claims (15)

  1. 一种机封冷却结构，包括泵体、冷却段、主轴、以及密封组件；
    所述冷却段固设于所述泵体，所述主轴贯穿所述冷却段至所述泵体内，所述冷却段内环绕所述主轴开设有机封腔，所述冷却段内还开设有环绕所述机封腔开设的冷却腔；
    所述密封组件包括平衡鼓以及机械密封，所述平衡鼓位于所述冷却段靠近所述泵体的一侧，以连通所述泵体与所述机封腔，所述机械密封位于所述冷却段远离所述泵体的一侧且位于所述机封腔内；以及
    所述机封冷却结构还包括冷却组件，所述冷却组件包括冷却管，所述冷却管设置于所述冷却腔内，且所述冷却管的两端分别与所述机封腔连通。
  2. 根据权利要求1所述的机封冷却结构，其中，所述冷却管包括两个开口，所述冷却组件还包括设置于所述机封腔内的辅助叶轮，所述辅助叶轮固设于所述主轴，且与所述冷却管靠近所述泵体一侧的开口对应，以将所述机封腔内的液体输入至所述冷却管内。
  3. 根据权利要求2所述的机封冷却结构，其中，所述辅助叶轮的进液口朝向所述机械密封一侧，所述辅助叶轮的出液口朝向所述冷却管靠近所述泵体一侧的开口。
  4. 根据权利要求2所述的机封冷却结构，其中，所述辅助叶轮的有效流量为0.4kg/m，扬程为4m-5m。
  5. 根据权利要求2所述的机封冷却结构，其中，所述冷却组件还包括设置于所述机封腔内的阻挡件，所述阻挡件位于所述冷却管的两个开口之间，以阻挡液体从所述机封腔靠近所述泵体的一侧流至所述机械密封一侧。
  6. 根据权利要求5所述的机封冷却结构，其中，所述阻挡件为阻挡块， 所述阻挡块位于所述机封腔的侧壁与所述辅助叶轮的外周面之间，且与所述机封腔的侧壁固定连接。
  7. 根据权利要求1所述的机封冷却结构，其中，所述冷却管以所述主轴为中心，沿所述主轴的轴线方向螺旋设置。
  8. 根据权利要求1所述的机封冷却结构，其中，所述冷却管的出水口与所述机封腔的顶壁固设，入水口与所述机封腔的底壁固设。
  9. 根据权利要求1所述的机封冷却结构，其中，所述冷却管为金属管。
  10. 一种高压热水泵，包括机封冷却结构，所述机封冷却机构包括泵体、冷却段、主轴、以及密封组件；
    所述冷却段固设于所述泵体，所述主轴贯穿所述冷却段至所述泵体内，所述冷却段内环绕所述主轴开设有机封腔，所述冷却段内还开设有环绕所述机封腔开设的冷却腔；
    所述密封组件包括平衡鼓以及机械密封，所述平衡鼓位于所述冷却段靠近所述泵体的一侧，以连通所述泵体与所述机封腔，所述机械密封位于所述冷却段远离所述泵体的一侧且位于所述机封腔内；以及
    所述机封冷却结构还包括冷却组件，所述冷却组件包括冷却管，所述冷却管设置于所述冷却腔内，且所述冷却管的两端分别与所述机封腔连通。
  11. 根据权利要求10所述的高压热水泵，其中，所述冷却管包括两个开口，所述冷却组件还包括设置于所述机封腔内的辅助叶轮，所述辅助叶轮固设于所述主轴，且与所述冷却管靠近所述泵体一侧的开口对应，以将所述机封腔内的液体输入至所述冷却管内。
  12. 根据权利要求11所述的高压热水泵，其中，所述辅助叶轮的进液口朝向所述机械密封一侧，所述辅助叶轮的出液口朝向所述冷却管靠近所述泵 体一侧的开口。
  13. 根据权利要求11所述的高压热水泵，其中，所述辅助叶轮的有效流量为0.4kg/m，扬程为4m-5m。
  14. 根据权利要求11所述的高压热水泵，其中，所述冷却组件还包括设置于所述机封腔内的阻挡件，所述阻挡件位于所述冷却管的两个开口之间，以阻挡液体从所述机封腔靠近所述泵体的一侧流至所述机械密封一侧。
  15. 根据权利要求14所述的高压热水泵，其中，所述阻挡件为阻挡块，所述阻挡块位于所述机封腔的侧壁与所述辅助叶轮的外周面之间，且与所述机封腔的侧壁固定连接。
PCT/CN2022/083396 2022-03-09 2022-03-28 机封冷却结构及具有其的高压热水泵 WO2023168765A1 (zh)

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