High-power hydraulic suspension pump

Abstract

The present application relates to the technical field of suspension pump, and provide a kind of high-power hydraulic suspension pump, including pump shell and motor, pump shell has liquid inlet and liquid outlet, and pump shell has inner shell body inside;Motor is located in inner shell body, and motor stator component and motor rotor component have cooling gap between them;Motor rotor component is connected with shaft, and one end of shaft is provided with impeller, and auxiliary bearing is provided on shaft or impeller;Impeller and inner shell body have rear gap communicated with second space, and rear gap, cooling gap, communication flow hole and shaft flow hole are sequentially communicated, and form cooling support flow path.Rotor component, shaft and impeller are supported by cooling support flow path and auxiliary bearing, so that rotor component is suspended as a whole, and the design of cooling support flow path and auxiliary bearing greatly improves the carrying capacity of suspension pump in axial direction, can meet the demand of high-power carrying capacity, and through the setting of auxiliary bearing, the reliability and safety are higher when starting and stopping.

Description

Technical Field

[0001] This invention relates to the technical field of suspension pumps, and more particularly to a high-power hydraulic suspension pump. Background Technology

[0002] Pumps are one of the key pieces of equipment in the industrial field, widely used in water supply and drainage, shipbuilding, nuclear power, chemical industry and other fields, undertaking the important function of transporting liquids. A significant problem in the current application of pump equipment is the large size and weight of pumps, as well as their high vibration and noise levels.

[0003] To address this issue, suspended pumps have been proposed in related technologies. However, conventional suspended pumps have limited load-bearing capacity due to their structural design, resulting in low application power, which greatly restricts their development and application. Furthermore, conventional suspended pumps have poor reliability and safety under start-up and shutdown conditions. Summary of the Invention

[0004] This invention provides a high-power hydraulic suspension pump to solve the shortcomings of existing technologies, such as low power, limited load-bearing capacity, and poor reliability and safety during start-up and shutdown.

[0005] This invention provides a high-power hydraulic suspension pump, comprising: a pump casing and a motor; the pump casing has an inlet and an outlet; the pump casing has an inner shell, the inner shell having a first space formed therein, and a second space formed between the inner shell and the inner wall of the pump casing; the motor is disposed within the first space, and the motor includes a stator component and a rotor component; the stator component is fixedly disposed within the first space, and the rotor component is movably disposed within the stator component, with a cooling gap between the stator component and the rotor component; the rotor component is connected to a rotating shaft, the rotating shaft... An impeller is provided at one end of the device, and the impeller is arranged inside the liquid inlet. An auxiliary bearing is provided on the rotating shaft or the impeller. An axial flow hole is provided on the rotating shaft, and the axial flow hole extends to one end of the rotating shaft at the position of the impeller. A radial connecting flow hole is provided at the end of the rotating shaft near the auxiliary bearing. There is a rear gap between the impeller and the inner housing that communicates with the second space. The rear gap, the cooling gap, the connecting flow hole and the axial flow hole are sequentially connected to form a cooling support flow path, so that some liquid circulates through the cooling support flow path.

[0006] According to the high-power hydraulic suspension pump provided by the present invention, axial guide vanes and radial guide vanes are provided on the inner wall of the pump casing near the liquid inlet.

[0007] According to the high-power hydraulic suspension pump provided by the present invention, the auxiliary bearing includes a bearing bush and a bearing seat. The bearing seat is fixedly disposed at the bottom of the first space, and the bearing bush is fixedly disposed at the end of the rotating shaft. There is a bearing clearance between the bearing bush and the bearing seat.

[0008] The high-power hydraulic suspension pump provided by the present invention has a bearing clearance greater than 0.25 mm in the working state.

[0009] According to the high-power hydraulic suspension pump provided by the present invention, the minimum values ​​of the rear clearance and the cooling clearance are both greater than 0.3 mm in the working state.

[0010] According to the high-power hydraulic suspension pump provided by the present invention, the rear clearance includes at least a first clearance section extending axially and a second clearance section extending radially.

[0011] According to the high-power hydraulic suspension pump provided by the present invention, the auxiliary bearing is disposed on the impeller and the inner housing located in the second gap section. The auxiliary bearing includes a bearing bush and a bearing seat. The bearing bush is fixedly disposed on the impeller, and the bearing seat is fixedly disposed on the inner housing. There is a bearing gap between the bearing bush and the bearing seat.

[0012] The high-power hydraulic suspension pump provided by the present invention has a diameter of more than 2 mm for the axial flow hole.

[0013] According to the high-power hydraulic suspension pump provided by the present invention, the diameter of the connecting flow hole is greater than 2 mm.

[0014] According to the high-power hydraulic suspension pump provided by the present invention, the rotor component includes a rotor body, and smooth portions are provided at both ends of the rotor body in the axial direction. The distance between the smooth portions and the inner wall of the stator component is less than the distance between the rotor body and the inner wall of the stator component.

[0015] The present invention provides a high-power hydraulic suspension pump in which the rotor component is movably disposed within the stator component, and the rotor component, the shaft and impeller connected to the rotor component are supported by a cooling support flow path and an auxiliary bearing, thereby making the rotor component suspended as a whole. The design of the cooling support flow path and the auxiliary bearing greatly improves the axial load-bearing capacity of the suspension pump, which can meet the high power load-bearing requirements. Furthermore, the auxiliary bearing makes it more reliable and safer during start-up and shutdown. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0017] Figure 1 This is a cross-sectional structural schematic diagram of the hydraulic suspension pump provided by the present invention.

[0018] Figure 2 This is a schematic diagram of the disconnected cross-sectional structure of the hydraulic suspension pump provided by the present invention.

[0019] Figure label:

[0020] 1. Pump casing; 11. Inlet; 12. Back clearance; 121. First clearance; 122. Second clearance; 13. Outlet; 2. Impeller; 3. Radial guide vane; 4. Axial guide vane; 5. Inner casing; 6. Shaft; 61. Shaft flow hole; 62. Flow hole; 7. Smooth part; 8. Motor; 81. Stator assembly; 82. Rotor assembly; 83. Cooling clearance; 9. Auxiliary bearing; 91. Bearing bush; 92. Bearing housing; 93. Bearing clearance; 10. Cooling support flow path. Detailed Implementation

[0021] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this invention. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without creative effort are within the scope of protection of this invention.

[0022] In the description of the embodiments of the present invention, it should be noted that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the embodiments of the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the embodiments of the present invention. In addition, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0023] In the description of the embodiments of the present invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of the present invention based on the specific circumstances.

[0024] In embodiments of the present invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0025] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0026] A hydraulically suspended pump suspends the drive unit (usually the motor) by designing a water flow cavity or channel, thereby achieving the function of a pump. This type of suspended pump improves reliability and service life by reducing mechanical wear and tear.

[0027] However, the limited load-bearing capacity of hydraulically suspended pumps restricts their application. Related technologies, such as the micro hydraulically suspended mechanical pump disclosed in Chinese patent CN114001036A, propose a hydraulic suspension pump principle for applications with power ratings not exceeding 100W. This principle relies on the combined action of hydraulic and magnetic forces to suspend rotating components. However, in high-power applications, the aforementioned hydraulic suspension load cannot meet the load-bearing requirements of the significantly increased weight of the rotating components, and safety and reliability issues also arise during start-up and shutdown.

[0028] Regarding the problems in related technologies, such as Figure 1 , Figure 2As shown, the present invention provides a high-power hydraulic suspension pump, including a pump casing 1 and a motor 8. The pump casing 1 has an inlet 11 and an outlet 13. An inner casing 5 is located inside the pump casing 1, with a first space formed inside the inner casing 5 and a second space formed between the inner casing 5 and the inner wall of the pump casing 1. The motor 8 is disposed within the first space and includes a stator component 81 and a rotor component 82. The stator component 81 is fixedly disposed within the first space, and the rotor component 82 is movably disposed within the stator component 81, with a cooling gap 83 between the stator component 81 and the rotor component 82. The rotor component 82 is connected to a rotating shaft 6. An impeller 2 is provided at one end of the rotating shaft 6, and the impeller 2 is arranged inside the liquid inlet 11. An auxiliary bearing 9 is provided on the rotating shaft 6 or the impeller 2. An axial flow hole 61 is provided on the rotating shaft 6, and the axial flow hole 61 extends to one end of the rotating shaft 6 at the position of the impeller 2. A radial connecting flow hole 62 is provided at the end of the rotating shaft 6 near the auxiliary bearing 9. There is a rear gap 12 between the impeller 2 and the inner shell 5, which communicates with the second space. The rear gap 12, the cooling gap 83, the connecting flow hole 62 and the axial flow hole 61 are connected in sequence to form a cooling support flow path 10, so that some liquid circulates through the cooling support flow path 10. High-power suspension pumps require higher load-bearing capacity and higher stability to support the stable operation of the high-power suspension pump. In this embodiment, the setting of the cooling support flow path 10 and the auxiliary bearing 9 makes the overall load-bearing capacity and stability higher, which can realize the stable operation of the high-power suspension pump.

[0029] It is understood that in this embodiment, the rotating component is suspended within the pump casing 1 during operation (i.e., normal water pumping). Specifically, the flow through the cooling support flow path 10 generates an upward axial lifting force, thereby achieving overall suspension and improving the overall load-bearing capacity. Furthermore, the inclusion of auxiliary bearings 9 enhances safety and reliability during start-up and shutdown, resulting in a stronger load-bearing capacity.

[0030] The stator component 81 is fixedly installed, while the rotor component 82 is movably installed within the first space. The rotor component 82 requires axial and radial force balance to remain suspended. This will be explained through a detailed analysis below.

[0031] Regarding axial force balance, the rotating components (for ease of description, rotor component 82, shaft 6, and impeller 2 are collectively referred to as rotating components) are subjected to forces including their own weight F1, the axial force F2 generated by the transported water on impeller 2, the axial support force F3 formed by the fluid pressure of the cooling support flow path 10 under circulating flow, and the axial support force F4 generated by the auxiliary bearing 9. Among them, F3 and F4 are used to balance F1 and F2. That is, when impeller 2 rotates normally, F1+F2 must be vertically downward, and F3+F4 must be vertically upward. The forces of the four parts are balanced, so that the rotating components are ultimately in an equilibrium position, and the rotating components are in a suspended state during operation.

[0032] Specifically, such as Figure 2 As shown, Figure 2 The flow direction indicated by the middle arrow is a circulation diagram of the cooling support flow path 10. The fluid pressure at the outlet end of impeller 2 is relatively high. Most of the fluid flows out of the pump through the second space and the outlet 13, while a small portion returns to the inlet end of impeller 2 through the rear gap 12, cooling gap 83, connecting flow hole 62, and axial flow hole 61, forming a circulation (i.e., cooling support flow path 10). The circulating fluid in the cooling support flow path 10 serves two purposes: firstly, it meets the requirement of maintaining a gap between rotating and stationary components (for ease of description, the stator component 81 and the inner housing 5 are collectively referred to as stationary components) to ensure operational safety; secondly, the circulating fluid also provides coolant for the shielded motor 8 body, meaning that the heat generated by the stator component 81 is carried away by the fluid in the cooling support flow path 10.

[0033] As the fluid flows through the cooling support flow path 10, it adapts to the flow resistance characteristics formed by the gaps, resulting in a certain pressure distribution. The pressure gradually decreases from the high pressure at the inlet section of the cooling support flow path 10 to the low pressure at the outlet section, thereby generating a vertically upward supporting force F3 to support the rotating components. Since the flow resistance characteristics are closely related to the gap value, small gaps are the main source of flow resistance. Therefore, the pressure loss of the cooling fluid mainly occurs at small gaps. In this embodiment, gaps are set throughout the cooling support flow path 10, and the hydraulic suspension of the rotating components under operating conditions is achieved by controlling the gaps.

[0034] Regarding the balancing of radial forces, conventional motors 8 all have radial bearings, which can provide radial support force in the presence of radial imbalance forces, ensuring that rotating parts do not undergo severe deflection. This embodiment uses a balancing method without radial bearings to achieve balance, as detailed below.

[0035] First, the stator component 81 and the electronic component have a cooling gap 83. The cooling gap 83 is a section of the cooling support flow path 10. It is similar to the hydrodynamic lubrication principle of water-lubricated bearings. When the rotating component is slightly eccentric, a radial force will be generated to resist the eccentric action. In the case of eccentricity, the gap value of the cooling gap 83 is not uniform on the entire circumference. The larger the eccentricity, the smaller the minimum value of the cooling gap 83, and the greater the balancing force generated based on the hydrodynamic lubrication principle, so that the rotor component 82 can achieve radial balance.

[0036] Secondly, the electromagnetic interaction between the stator component 81 and the rotor component 82 will also generate a certain electromagnetic force under eccentric conditions, causing the rotating component to return to the central equilibrium position. Based on the above design, when there is a certain radial imbalance force in the rotating component, the rotating component will not be eccentric indefinitely due to the action of water pressure and electromagnetic force. After a certain degree of eccentricity, it will regain equilibrium, making the radial imbalance force relatively small under all operating conditions, and the degree of eccentricity also relatively small. The cooling gap 83 between the stator component 81 and the rotor component 82 (for example, the initial design of the cooling gap 83 is 2-3 mm, and the minimum value of the gap at the equilibrium position is not less than 0.3 mm, which meets the safety operation requirements) can still ensure safe operation and prevent physical collisions between the rotating component and the stationary component that could cause damage.

[0037] In a specific implementation, the suspension pump adopts a vertical pump structure, meaning the pump casing 1, stator component 81, and rotor component 82 are arranged vertically. This ensures that the rotating components are vertical, gravity is directed along the axial direction, and no radial force is generated, which is beneficial for the design of radial force balance.

[0038] According to one embodiment of the present invention, an axial guide vane 4 and a radial guide vane 3 are provided on the inner wall of the pump casing 1 near the inlet 11. Liquid is input through the inlet 11 and pumped out under pressure by the work of the pump body. In this embodiment, the radial guide vane 3 and the axial guide vane 4 are arranged to achieve uniform flow at the outlet of the impeller 2. On the one hand, this significantly reduces the fluid excitation generated by the fluid at the outlet of the impeller 2, which helps to reduce vibration and noise; on the other hand, it improves the uniformity of flow in the circumferential direction, reduces the radial unbalanced force on the rotating parts, and provides support for eliminating the radial bearing by reducing the radial force.

[0039] In a specific configuration, the radial guide vane 3 is positioned at the front end of the axial guide vane 4, meaning the liquid is output after passing through the radial guide vane 3 and the axial guide vane 4 sequentially. The radial guide vane 3 comprises multiple helical blades with their rotation direction facing radially, and these multiple radial guide vanes 3 are evenly spaced around the inner wall of the pump casing 1. Similarly, the axial guide vane 4 comprises multiple helical blades with their rotation direction facing axially, and these multiple axial guide vanes 4 are evenly spaced around the inner wall of the pump casing.

[0040] In one embodiment of the present invention, an auxiliary bearing 9 is disposed at the bottom end of the rotating shaft 6. The auxiliary bearing 9 includes a bearing bush 91 and a bearing seat 92. The bearing seat 92 is fixedly disposed at the bottom of the first space, and the bearing bush 91 is fixedly disposed at the end of the rotating shaft 6. A bearing clearance 93 is provided between the bearing bush 91 and the bearing seat 92. During the start-up and shutdown process of the suspension pump, the axial balance of the rotating parts may become unbalanced due to the uncirculated or decreased flow rate of the cooling support flow path 10. In this embodiment, the auxiliary bearing 9 can provide greater support force during the start-up and shutdown phases to avoid collisions between the rotating parts and the stationary parts, thereby improving the safety and reliability of the pump.

[0041] Under normal operating conditions, the rotating parts can be lifted and suspended due to the high flow rate of fluid in the cooling support flow path 10, at which point the auxiliary bearing 9 provides very little support. However, during start-up and shutdown, the fluid in the cooling support flow path 10 is not yet sufficient to fully support the rotating parts, so the auxiliary bearing 9 provides auxiliary support, thereby improving the pump's reliability.

[0042] Specifically, by placing the auxiliary bearing 9 at the bottom end of the rotating shaft 6, support can be provided by the auxiliary bearing 9 at the bottom end during start-up and shutdown, thereby achieving a balance of forces in various parts along the axial direction. This method facilitates installation and maintenance.

[0043] In one embodiment of the present invention, the bearing clearance 93 is greater than 0.25 mm in the operating state. By limiting the bearing clearance 93 in the operating state, the pump body has a better noise reduction effect.

[0044] Understandably, the auxiliary bearing 9 is similar to a water-lubricated bearing, and its load-bearing capacity increases as the bearing clearance 93 decreases. Typically, the bearing reaches its preset load-bearing design value at 0.05-0.1 mm. Because the bearing clearance 93 is small at this point, the stiffness generated by the fluid within the bearing clearance 93 is relatively large, resulting in greater vibration energy transmitted from the bearing to the rotating components, leading to higher pump noise. However, in this embodiment, since the rotating components are supported by the fluid in the cooling support flow, the bearing clearance 93 can reach a larger value. In this case, the auxiliary bearing 9 essentially does not act as a load-bearing component, thereby reducing the noise generated by the pump.

[0045] In specific settings, the minimum values ​​of the rear clearance 12 and cooling clearance 83 are both greater than 0.3 mm in the working state.

[0046] Understandably, by limiting the minimum value of the gaps in the rear clearance 12 and the cooling clearance 83, the overall clearance design ensures that the clearance in the working state is greater than 0.3 mm, thereby reducing the overall operating noise of the pump body. Specifically, the connection between the rear clearance 12 and the cooling clearance 83 is the narrowest part of the entire cooling support flow path 10, while the rest is larger than the rear clearance 12 and the cooling clearance 83. This limitation of the two smaller gaps ensures that the minimum value of all gaps between rotating and stationary parts in the working state is greater than 0.3 mm.

[0047] In a specific configuration, the rear gap 12 includes at least a first gap 121 segment extending axially and a second gap 122 segment extending radially. In the working state, the first gap 121 segment and the second gap 122 segment are the narrowest sections of the entire cooling support flow path 10. Through axial and radial limitation, the fluid can generate greater resistance when flowing through the two sections, thereby generating an axially upward lifting force and ultimately achieving a balance of various forces.

[0048] According to one embodiment of the present invention, an auxiliary bearing 9 is disposed on the impeller 2 located within the second gap 122. The auxiliary bearing 9 includes a bearing bush 91 and a bearing housing 92. The bearing bush 91 is fixedly disposed on the impeller 2, and the bearing housing 92 is fixedly disposed on the inner housing 5. A bearing gap 93 is provided between the bearing bush 91 and the bearing housing 92. The auxiliary bearing 9 is disposed at the lower end of the rotating shaft 6, and can also be disposed within the second gap 122. By integrating with the second gap 122, the structure of the entire pump body becomes more compact and the volume is smaller.

[0049] In specific implementation, a bearing bush 91 (with a wear-resistant, low-resistance coefficient surface treatment) is installed at the position of the impeller 2 in the second gap 122 segment. Similarly, a bearing seat 92 (with a wear-resistant, low-resistance coefficient surface treatment) is installed at the position of the inner housing 5 in the second gap 122 segment to assist the installation of the bearing 9. By installing it at this position, it can be supported by the auxiliary bearing 9 during the start-up and shutdown phases. That is, during the start-up and shutdown phases, the gap at the second gap 122 segment is very small, thereby achieving effective support. After the cooling support flow path 10 starts flowing, the gap at the second gap 122 segment increases, and at this time, the cooling support flow path 10 provides support.

[0050] According to one embodiment of the present invention, the diameter of the axial flow hole 61 is greater than 2 mm. The axial flow hole 61 is used to output the fluid input from each gap in the first space to the end of the impeller 2, so that the impeller 2 can perform work again to achieve overall circulation.

[0051] In a specific configuration, the axial flow hole 61 is a straight through hole, and the axial flow hole 61 is larger than each gap, so that the fluid in the cooling support flow path 10 can flow quickly, thereby achieving the lifting and support of the rotating parts.

[0052] In a further example, the diameter of the connecting flow orifice 62 is greater than 2 mm. The connecting flow orifice 62 is used to connect the axial flow orifice 61 to the cooling gap 83, and the orifice diameter setting of the connecting flow orifice 62 can further enable rapid fluid flow.

[0053] According to one embodiment of the present invention, the rotor component 82 includes a rotor body, and smooth portions 7 are provided at both ends of the rotor body along the axial direction. The distance between the smooth portions 7 and the inner wall of the stator component 81 is less than the distance between the rotor body and the inner wall of the stator component 81. The provision of the smooth portions 7 can enhance the radial load-bearing capacity, thereby improving the overall load-bearing capacity and stability.

[0054] Understandably, to further enhance safety and reliability, a smooth part 7 with high wear resistance and low resistance coefficient local surface treatment is provided at the inlet and outlet positions of the cooling gap 83 around the rotor component 82 (similar to installing a water-lubricated bearing). The gap value at the smooth part 7 is set (for example, 2mm) to be smaller than the value of the cooling gap 83 (2.5mm) of most of the length between the stator component 81 and the main body of the rotor component 82. Under normal working conditions, this minimum gap value is still above 0.3mm. Under special working conditions, when large eccentricity occurs, the minimum value of this local gap value may be as low as 0.05-0.1mm. At this time, this local surface is a set of water-lubricated bearings, the radial bearing capacity is greatly increased, and it can still ensure that the rotating part will not physically collide with the stationary part.

[0055] The above examples will be illustrated with specific examples below.

[0056] In a preferred embodiment, the first gap 121 is designed to have a gap value of 1 mm; the second gap 122 is designed to have a gap value of 0.5 mm; the diameter of the connecting flow hole 62 and the axial flow hole 61 is greater than 2 mm; and the remaining gap values ​​in the cooling support flow path 10 are all greater than 2 mm.

[0057] In actual operation, the above-mentioned gap design results in the cooling fluid resistance being mainly concentrated at the first gap 121 and the second gap 122, and the resistance of the second gap 122 is greater than that of the first gap 121. At this time, the fluid pressure between the inlet of the cooling support flow path 10 and the second gap 122 is relatively large, forming a vertically upward axial force F31 on the rotating component. After passing through the second gap 122, the fluid pressure is relatively small, forming a vertically upward axial force F32 on the rotating component. When pump casing 1 is stationary and pump speed and operating conditions remain unchanged, if the rotating parts experience a downward axial force due to imbalance of the total axial force, they will move downwards. At this time, the clearance value of the first gap 121 remains unchanged, while the clearance value of the second gap 122 decreases. Therefore, the resistance of the second gap 122 increases. Since the resistance of other parts of the cooling fluid flow path remains essentially unchanged, the proportion of the second gap 122 in the total fluid resistance increases. Because the total fluid pressure drop in the cooling fluid flow path remains unchanged (equal to the impeller 2 head), the fluid pressure upstream of the second gap 122 ultimately increases, resulting in an increase in F31. Conversely, the fluid pressure downstream of the second gap 122 decreases, causing F32 to decrease. The increase in the amplitude is much greater than the decrease in the amplitude of F32, thus increasing the vertically upward axial force exerted by the fluid in the cooling support flow path 10 on the rotating component. Other axial forces on the rotating component (gravity, the axial force generated by the transported water on the impeller 2 component, and the axial support force generated by the auxiliary bearing 9) do not change significantly. Therefore, the vertically downward axial force on the rotating component will continuously decrease, and eventually the total axial force on the rotating component will rebalance. At this point, the value of the second gap 122 is less than the design value of 0.5mm. Conversely, if the rotating component experiences an upward axial force due to the imbalance of the total axial force, the rotating component will move upward, and the value of the second gap 122 will be greater than the design value of 0.5mm. Overall, the hydraulic scheme design for the hydraulic suspension pump in this example shows that the actual range of the second gap 122 value under various operating conditions is between 0.3-0.8mm, achieving hydraulic suspension of the axial force on the rotating component.

[0058] Furthermore, for safety and reliability, an auxiliary bearing 9 is installed at the lower end of the rotating shaft 6. The design clearance of the auxiliary bearing 9 is 0.45mm, slightly smaller than the design clearance of the second clearance 122 (0.5mm). Under normal circumstances, when the second clearance 122 is greater than 0.3mm, the clearance of the auxiliary bearing 9 is greater than 0.25mm. At this time, the axial force F4 generated by the auxiliary bearing 9 is very small and has little impact on the above balance. When the axial force F3 exerted by the fluid in the cooling support flow path 10 on the rotating component is insufficient to balance the weight F1 and the axial force F2 generated by the transported water on the impeller 2 component, the rotating component will move further downward until the clearance of the auxiliary bearing 9 reaches 0.05-0.1mm (e.g., during start-up and shutdown). When the second clearance 122 is 0.1-0.15mm, the axial force F4 generated by the auxiliary bearing 9 will increase significantly, playing the role of a thrust bearing in a traditional pump. This effectively ensures that the rotating component does not collide with the stationary component, ensuring the safety and reliability of the equipment.

[0059] Meanwhile, during startup or shutdown, when the impeller 2 generates a very small head, the pressure in the cooling support flow path 10 is also small, so F3 will be small and insufficient to balance F1+F2. At this time, the rotating parts are balanced by the F4 generated by the auxiliary bearing 9, ensuring the safety and reliability of the equipment.

[0060] Through the above description of the embodiments, those skilled in the art can clearly understand that each embodiment can achieve a significant improvement in pump compactness and a significant reduction in volume and weight through integrated design such as setting radial guide vanes 3, axial guide vanes 4, special gap flow channel structure, and auxiliary bearings 9. On the other hand, it can achieve that the rotating parts of the pump are hydraulically suspended in the pump body under normal operating conditions, without rigid connection to the stationary parts of the pump body, and that all kinds of gap values ​​are greater than 0.3mm, which greatly reduces the vibration energy transmitted to the outside through the bearings in traditional pumps and reduces the vibration noise of the pump.

[0061] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A high-power hydraulic suspension pump, characterized in that, include: A pump casing has an inlet and an outlet. Inside the pump casing is an inner shell. A first space is formed inside the inner shell, and a second space is formed between the inner shell and the inner wall of the pump casing. An electric motor is disposed within the first space. The electric motor includes a stator component and a rotor component. The stator component is fixedly disposed within the first space, and the rotor component is movably disposed within the stator component. A cooling gap exists between the stator component and the rotor component. The rotor component is connected to a rotating shaft, one end of which is provided with an impeller, which is arranged inside the liquid inlet. An auxiliary bearing is provided on the rotating shaft or the impeller. An axial flow hole is provided on the rotating shaft, which extends to one end of the rotating shaft at the position of the impeller. A radial connecting flow hole is provided on the end of the rotating shaft near the auxiliary bearing. The impeller and the inner housing have a rear clearance that communicates with the second space. The rear clearance, the cooling clearance, the connecting flow hole, and the axial flow hole are sequentially connected to form a cooling support flow path. In the working state, the liquid circulating through the cooling support flow path generates an axial support force on the rotating component composed of the rotor, shaft and impeller, suspending the rotating component and maintaining a preset bearing clearance between the bearing bush and the bearing housing of the auxiliary bearing; in the pump's start-stop state, the auxiliary bearing is used to support the rotating component.

2. The high-power hydraulic suspension pump according to claim 1, characterized in that, The pump casing inner wall near the liquid inlet is provided with axial guide vanes and radial guide vanes.

3. The high-power hydraulic suspension pump according to claim 1 or 2, characterized in that, The auxiliary bearing is located at the bottom end of the rotating shaft. The auxiliary bearing includes a bearing bush and a bearing seat. The bearing seat is fixedly located at the bottom of the first space. The bearing bush is fixedly located at the end of the rotating shaft. There is a bearing clearance between the bearing bush and the bearing seat.

4. The high-power hydraulic suspension pump according to claim 3, characterized in that, The bearing clearance is greater than 0.25 mm when in operation.

5. The high-power hydraulic suspension pump according to claim 1, characterized in that, In the working state, the minimum values ​​of both the rear clearance and the cooling clearance are greater than 0.3 mm.

6. The high-power hydraulic suspension pump according to claim 1, characterized in that, The rear clearance includes at least a first clearance segment extending axially and a second clearance segment extending radially.

7. The high-power hydraulic suspension pump according to claim 6, characterized in that, The auxiliary bearing is disposed on the impeller and the inner housing located within the second gap section. The auxiliary bearing includes a bearing bush and a bearing housing. The bearing bush is fixedly disposed on the impeller, and the bearing housing is fixedly disposed on the inner housing. There is a bearing gap between the bearing bush and the bearing housing.

8. The high-power hydraulic suspension pump according to claim 1, characterized in that, The diameter of the shaft flow hole is greater than 2 mm.

9. The high-power hydraulic suspension pump according to claim 1, characterized in that, The diameter of the connecting flow hole is greater than 2 mm.

10. The high-power hydraulic suspension pump according to claim 1, characterized in that, The rotor component includes a rotor body, and smooth portions are provided at both ends of the rotor body along the axial direction. The distance between the smooth portions and the inner wall of the stator component is less than the distance between the rotor body and the inner wall of the stator component.

Images