Pressurizing assembly for radial plunger pump and radial plunger pump

Abstract

The invention provides a pressurizing assembly for a radial plunger pump and the radial plunger pump, and belongs to the field of plunger pumps. The pressurization assembly for the radial plunger pump comprises a pressurization shell and an impeller, the pressurization shell is provided with an inner cavity, the inner cavity comprises a pressurization area used for containing the impeller and a conveying area communicating with the periphery of the pressurization area, and a suction inlet used for sucking a working medium is formed in the shell wall, corresponding to the pressurization area, of the pressurization shell. The shell wall, corresponding to the conveying area, of the pressurizing shell is provided with a discharging opening used for discharging the working medium. During use, the impeller can rotate along with the rotating shaft in the pressurizing area so that the working medium can be discharged after being pressurized in the pressurizing shell. The radial plunger pump comprises the pressurizing assembly. According to the radial plunger pump, the working medium is pressurized in advance, so that the working medium can enter the plunger assembly more easily, the phenomena of cavitation, air suction and the like are reduced, and the radial plunger pump has better working capacity and longer service life.

Description

Technical Field

[0001] This invention belongs to the field of plunger pumps, and in particular relates to a booster assembly for a radial plunger pump and a radial plunger pump. Background Technology

[0002] Radial piston pumps can pressurize water to ultra-high pressure (e.g., above 100 MPa), directly utilizing its pressure energy for processing (such as waterjet processing, water-guided laser processing, etc.), and have become a revolutionary technology in the field of special processing. In addition to pressurizing water, radial piston pumps can also be used to pressurize working media such as water-ethylene glycol, emulsions, aviation kerosene, gasoline, and diesel.

[0003] The general structure of a radial piston pump can be referred to in Chinese invention patent application CN107939628A, which discloses a multi-head radial piston pump. The multi-head radial piston pump includes a pump body, piston mechanisms, and eccentric wheels. The piston mechanisms are installed at intervals in the pump body along the circumferential direction. The pump body is provided with a drive shaft, and the eccentric wheels are mounted on the drive shaft. The eccentric wheels are rotatably installed between the piston mechanisms. When the eccentric wheels rotate, the piston mechanisms move back and forth in the radial direction successively, thereby successively sucking up and discharging the working medium.

[0004] Radial piston pumps are used in certain special environments, such as when the pump is installed above the oil tank, the suction line is long with many bends, the operating speed is very high, or when conveying high-viscosity media. In these situations, the pump's suction conditions are poor, making it prone to cavitation and suction cavitation. Cavitation occurs when the working medium's flow resistance is high and it cannot enter the piston assembly in time. Due to the low local pressure within the piston assembly, dissolved air in the working medium precipitates out, or the working medium vaporizes, generating bubbles. During the subsequent discharge of the working medium, the pressure within the piston assembly rapidly increases, and these bubbles are drastically compressed and quickly collapse. The collapse generates extremely high impact pressure and temperature, causing fatigue spalling on the surface of metal parts. Suction cavitation occurs when the piston assembly fails to draw in enough working medium. During the discharge of the working medium, there will be a drop or fluctuation in the actual output pressure, preventing the radial piston pump from stably reaching its rated output pressure. Summary of the Invention

[0005] The purpose of this invention is to provide a booster assembly for a radial piston pump, so as to solve the technical problem that radial piston pumps are prone to cavitation and air suction when used in special environments, which affects the normal use of the radial piston pump.

[0006] Another object of the present invention is to provide a radial piston pump to solve the above-mentioned technical problems.

[0007] To achieve the above objectives, the technical solution of the radial piston pump provided by this invention is as follows: A radial piston pump includes a housing, a shaft, and piston assemblies arranged around the shaft. An eccentric structure is provided on the shaft for pushing each piston assembly. A pressurization assembly is disposed within the housing, comprising a pressurization shell and an impeller. The pressurization shell is fixed to the housing or the piston assemblies. The pressurization shell has an inner cavity including a pressurization region for accommodating the impeller and a delivery region connected to the pressurization region. An intake port for drawing in working medium is provided on the shell wall corresponding to the pressurization region, and an outlet for discharging working medium is provided on the shell wall corresponding to the delivery region. The outlet is connected to the inlet of the piston assembly. The impeller is fixed to the shaft and can rotate with the shaft within the pressurization region, thereby pressurizing the working medium within the pressurization shell before discharge.

[0008] As a further improvement, the impeller is fixed to the end of the rotating shaft. The two axial end walls of the booster housing are respectively the open end wall with a central opening and the complete end wall with a complete structure. The central hole of the open end wall constitutes the suction port and also constitutes the through hole for the rotating shaft to pass through. An annular space is left between the central hole wall of the open end wall and the rotating shaft for the working medium to pass through.

[0009] As a further improvement, the eccentric structure includes an eccentric inner ring fixed on a rotating shaft and a bearing outer ring sleeved outside the eccentric inner ring and capable of rotating relative to the eccentric inner ring. An axially penetrating flushing groove is provided on the rotational mating interface of at least one of the bearing outer ring and the eccentric inner ring. During use, the working medium flows through the flushing groove before being sucked in by the pressurization component to lubricate and cool the eccentric inner ring and the bearing outer ring.

[0010] As a further improvement, a flow guide ring extending outward from the center hole wall of the opening end wall is provided, and all parts of the eccentric structure are within the inner diameter range of the flow guide ring.

[0011] As a further improvement, the pump inlet of the radial piston pump is located on the end wall of one axial end of the housing, and the end wall of the housing with the pump inlet is adjacent to the complete end wall of the booster housing with a gap between them for the working medium to flow in all directions.

[0012] As a further improvement, the impeller includes an annular mounting portion, a wheel plate fixed to the outer periphery of the mounting portion and parallel to the axial direction in thickness, and blades fixed to one side of the wheel plate in the axial direction, with the side of the wheel plate having blades facing the suction port on the booster housing.

[0013] The beneficial effects are as follows: The radial piston pump provided by this invention is an improvement upon existing technology. This radial piston pump adds a pressurizing component to existing technology. This component pre-pressurizes the working medium before it enters the piston assembly, creating a larger pressure difference between the working medium inside and outside the inlet of the pressurizing component. During the process of the piston assembly drawing in the working medium, the working medium can enter the piston assembly more easily and quickly, avoiding cavitation and air suction. This ensures that the radial piston pump has good working capacity and a long service life even in special environments. Furthermore, this pressurizing component utilizes the existing power of the radial piston pump, requiring no additional power input, making the overall structure of the radial piston pump relatively simple and compact.

[0014] To achieve the above objectives, the technical solution of the booster assembly for a radial piston pump provided by the present invention is as follows: A booster assembly for a radial piston pump includes a booster housing and an impeller. In use, the booster housing is fixed to the outer casing of the radial piston pump or a piston assembly. The booster housing has an inner cavity, which includes a booster area for accommodating the impeller and a delivery area connected around the booster area. The shell wall of the booster housing corresponding to the booster area is provided with a suction port for drawing in the working medium, and the shell wall of the booster housing corresponding to the delivery area is provided with a discharge port for discharging the working medium. In use, the discharge port is connected to the inlet of the piston assembly. During use, the impeller can rotate with the shaft in the booster area, thereby pressurizing the working medium in the booster housing before discharge.

[0015] As a further improvement, the two axial end walls of the pressurization shell are respectively an open end wall with a central opening and a complete end wall with a complete structure. The central hole of the open end wall constitutes the intake port and also constitutes a through hole for the rotating shaft to pass through. During use, an annular space is left between the central hole wall of the open end wall and the rotating shaft for the working medium to pass through.

[0016] As a further improvement, a guide ring extending outward from the center hole of the perforated end wall is provided. The size of the guide ring is such that all parts of the eccentric structure in the radial plunger pump are within the inner diameter range of the guide ring during use.

[0017] As a further improvement, the impeller includes an annular mounting portion, a wheel plate fixed to the outer periphery of the mounting portion and parallel to the axial direction in thickness, and blades fixed to one side of the wheel plate in the axial direction, with the side of the wheel plate having blades facing the suction port on the booster housing.

[0018] The beneficial effects are as follows: The booster assembly for radial piston pumps provided by this invention is a pioneering invention. This booster assembly can pre-pressurize the working medium before it enters the piston assembly, creating a larger pressure difference between the working medium inside and outside the booster assembly inlet. During the process of the piston assembly drawing in the working medium, the working medium can enter the piston assembly more easily and quickly, avoiding cavitation and air suction. This ensures that the radial piston pump has good working capacity and a long service life even in special environments. Furthermore, this booster assembly utilizes the existing power of the radial piston pump, requiring no additional power input, making the overall structure of the radial piston pump relatively simple and compact. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the overall structure of Embodiment 1 of the radial plunger pump in this invention; Figure 2 for Figure 1 Sectional view at point AA; Figure 3 This is a schematic diagram of the end cap structure in Embodiment 1 of the radial plunger pump of the present invention; Figure 4 This is a schematic diagram of the shaft structure in Embodiment 1 of the radial piston pump of the present invention; Figure 5 This is a schematic diagram of the eccentric structure in Embodiment 1 of the radial piston pump of the present invention; Figure 6 This is a cross-sectional view of the eccentric structure in Embodiment 1 of the radial piston pump of the present invention; Figure 7 This is a cross-sectional view of the plunger assembly in Embodiment 1 of the radial plunger pump of the present invention; Figure 8 This is a cross-sectional view of the plunger assembly in Embodiment 1 of the radial plunger pump of the present invention from another perspective; Figure 9 This is a schematic diagram of the external structure of the pump body in Embodiment 1 of the radial plunger pump of the present invention; Figure 10 This is a cross-sectional view of the pump body in Embodiment 1 of the radial piston pump of the present invention; Figure 11 This is a schematic diagram of the external structure of the guide sleeve in Embodiment 1 of the radial plunger pump of the present invention; Figure 12 This is a cross-sectional view of the guide sleeve in Embodiment 1 of the radial piston pump of the present invention; Figure 13 This is a schematic diagram illustrating the working principle of the booster assembly in Embodiment 1 of the radial piston pump of the present invention. Figure 14This is a schematic diagram of the structure of the booster housing after removing the complete end wall in Embodiment 1 of the radial plunger pump of the present invention; Figure 15 This is a schematic diagram of the external structure of the booster housing in Embodiment 1 of the radial plunger pump of the present invention; Figure 16 This is a schematic diagram of the impeller structure in Embodiment 1 of the radial piston pump of the present invention; Figure 17 This is a cross-sectional view of the impeller in Embodiment 1 of the radial piston pump of the present invention.

[0020] Explanation of reference numerals in the attached figures: 1. Outer shell; 11. Housing; 12. End cap; 121. Circumferential channel; 122. Connecting channel; 123. Pump outlet channel; 13. Pump inlet; 14. Pump outlet; 15. Shaft seal structure; 2. Rotating shaft; 21. Rotating mating section; 22. Mounting transmission section; 23. Threaded hole; 24. Transmission key; 3. Plunger assembly; 31. Pump body; 312. Pumping channel; 313. Suction valve; 314. Discharge valve; 315. Plug hole; 316. Plug; 317. Limiting post; 32. Plunger; 33. Guide sleeve; 331. Connecting hole; 332. Mating surface; 333. Limiting edge; 34. External spiral spring 35. Spring; 4. Internal helical spring; 5. Pressurization assembly; 6. Pressurization shell; 7. Pressurization area; 8. Conveying area; 9. Suction port; 10. Discharge port; 11. Connecting hole; 12. Opening end wall; 13. Complete end wall; 14. Guide ring; 15. Impeller; 16. Mounting part; 17. Wheel plate; 18. Blade; 19. Guide surface; 20. Stepped opening; 21. Pressure plate; 22. Motor; 33. Eccentric structure; 44. Eccentric inner ring; 55. Eccentric mounting hole; 66. Flushing groove; 77. Bearing outer ring; 88. Outer ring body; 99. Wear-resistant layer. Detailed Implementation

[0021] The present invention will be further described in detail below with reference to the embodiments.

[0022] Specific embodiment 1 of the radial plunger pump provided by the present invention: See appendix Figure 1 and attached Figure 2 The radial piston pump includes a housing 1, a rotating shaft 2, a piston assembly 3, and a booster assembly 4.

[0023] The outer casing 1 includes a housing 11 and an end cap 12. The end cap 12 is sealed to one axial end of the housing 11. The housing 11 mainly serves to enclose the inner cavity of the outer casing 1 together with the end cap 12. The end cap 12 mainly serves to install other structures of the radial plunger pump and bear loads. Therefore, the thickness of the end cap 12 is greater than the thickness of the housing 11. A pump inlet 13 is provided at the center of the axial end wall of the housing 11, and a pump outlet 14 is provided on the outer periphery of the end cap 12. A collection channel communicating with the pump outlet 14 and allowing the working medium to be discharged from the pump outlet 14 is provided inside the end cap 12.

[0024] Combined with appendix Figure 3 The end cap 12 has a through hole at its center for the rotating shaft 2 to pass through. The rotating shaft 2 rotatably engages with the through hole on the end cap 12, and a shaft seal structure 15 is provided between the rotating shaft 2 and the end cap 12. One end of the rotating shaft 2 that extends into the inner cavity of the outer casing 1 is suspended. See Appendix Figure 4 In this embodiment, the rotating shaft 2 is the output shaft of the motor 5 configured for the radial piston pump. In other embodiments, the rotating shaft 2 can also be set independently and then connected to the motor 5 through a coupling.

[0025] An eccentric structure 6 is provided on the rotating shaft 2. During the rotation of the rotating shaft 2, the eccentric structure 6 can push each plunger assembly 3 in sequence. In this embodiment, the eccentric structure 6 is an independently machined component installed on the rotating shaft 2. In other embodiments, the eccentric structure 6 can also be an eccentric shaft segment integrally formed on the rotating shaft 2.

[0026] Specifically, see Appendix Figure 5 and attached Figure 6 The eccentric structure 6 consists of an eccentric inner ring 61 fixed on the rotating shaft 2 and a bearing outer ring 62 sleeved around the eccentric inner ring 61 and capable of rotating relative to it. The eccentric inner ring 61 has an eccentric mounting hole 611, which is fitted onto the rotating shaft 2. A keyway is provided on the side wall of the eccentric mounting hole 611 to allow the eccentric inner ring 61 to be circumferentially connected to the rotating shaft 2 via a transmission key 24. Rotation of the rotating shaft 2 causes the eccentric inner ring 61 to rotate together, thereby sequentially pushing each plunger assembly 3. The relative rotation between the eccentric inner ring 61 and the bearing outer ring 62 reduces friction between the bearing outer ring 62 and the plunger assembly 3.

[0027] A flushing groove 612 is provided on the outer periphery of the eccentric inner ring 61, which runs through the circumference. During the axial flow of the working medium in the inner cavity of the outer shell 1, the medium can flow through the flushing groove 612, thereby carrying away the heat generated by the friction between the eccentric inner ring 61 and the bearing outer ring 62, and also enhancing the lubrication effect between the eccentric inner ring 61 and the bearing outer ring 62.

[0028] The bearing outer ring 62 includes an outer ring body 621 and a wear-resistant layer 622 wrapped around the surface of the outer ring body 621. The wear-resistant layer 622 can be mainly distributed on the radially inner side of the bearing outer ring 62 to reduce frictional wear between the bearing outer ring 62 and the eccentric inner ring 61. Alternatively, the wear-resistant layer 622 can also be distributed on the axial end face of the bearing outer ring 62 to reduce frictional wear between the bearing outer ring 62 and the plunger assembly 3.

[0029] See appendix Figure 2 Five plunger assemblies 3 are provided, each evenly distributed around the rotating shaft 2. In other embodiments, three, four, or six plunger assemblies 3 may be provided, the specific number depending on the needs. See appendix. Figure 7 and attached Figure 8 The plunger assembly 3 includes a pump body 31, a plunger 32, and a guide sleeve 33. The pump body 31 is fixedly installed on the inner side of the end cover 12, the plunger 32 is installed inside the pump body 31, and the guide sleeve 33 is installed outside the pump body 31.

[0030] Specifically, in conjunction with the appendix Figure 9 and attached Figure 10 The pump body 31 is provided with a pumping channel 312 for pumping the working medium. The pumping channel 312 passes through the pump body 31 along the axial direction of the radial plunger pump. One end of the pumping channel 312 is its inlet and the other end is its outlet. A suction valve 313 and a discharge valve 314 are respectively provided at the inlet and outlet of the pumping channel 312. Both the suction valve 313 and the discharge valve 314 are valves that allow the working medium to pass through in one direction.

[0031] The pump body 31 is also provided with a plug hole 315, which extends radially along the radial direction of the radial piston pump. The end of the plug hole 315 near the rotating shaft 2 is open, and the end away from the rotating shaft 2 is closed. The piston 32 enters the plug hole 315 from the end near the rotating shaft 2 and can reciprocate within the plug hole 315. The plug hole 315 is connected to the middle of the pumping channel 312. As the piston 32 reciprocates within the plug hole 315, the space in the plug hole 315 and the pumping channel 312 changes. When this space increases, a negative pressure is formed, and the pumping channel 312 draws in the working medium from the inlet. When this space decreases, a positive pressure is formed, and the pumping channel 312 discharges the working medium from the outlet.

[0032] The outlet of pumping channel 312 is connected to the collecting channel on end cover 12. The working medium discharged from each plunger assembly 3 enters the collecting channel and is discharged from pump outlet 14 after being gathered together. See Appendix Figure 3The flow collection channel includes an annular channel 121. At each location where a plunger assembly 3 is installed, the end cover 12 has a radially extending connecting channel 122 that communicates with the annular channel 121. The connecting channel 122 serves as the inlet of the flow collection channel and communicates with the outlet of the corresponding pumping channel 312. The flow collection channel also includes a radially extending pumping channel 123. One end of the pumping channel 123 communicates with the annular channel, and the other end penetrates the outer circumference of the end cover 12. The end of the pumping channel 123 furthest from the annular channel constitutes the outlet of the flow collection channel and also forms the pump outlet 14 of the entire radial plunger pump.

[0033] The portion of the pump body 31 near the rotating shaft 2 is a cylindrical structure. The plug hole 315 is coaxial with this cylindrical structure. A guide sleeve 33 is fitted over this cylindrical structure and guides it, enabling the guide sleeve 33 to also reciprocate. The reciprocating motion of the guide sleeve 33 is in the same direction as the reciprocating motion of the plunger 32. During the reciprocating motion of the guide sleeve 33 relative to the pump body 31, the space enclosed by the guide sleeve 33 and the pump body 31 will correspondingly increase or decrease. (See attached diagram.) Figure 11 and attached Figure 12 The guide sleeve 33 has a connecting hole 331 on its side wall for the flow of working medium inside and outside the guide sleeve 33, so that the working medium can flow smoothly when the space changes. In other embodiments, the connecting hole 331 can also be provided on the pump body 31, connecting the end face of the columnar structure of the pump body 31 to the surface of the pump body 31 exposed in the working medium; alternatively, a connecting groove can be provided on the outer circumferential surface of the columnar structure of the pump body 31 or the inner circumferential surface of the guide sleeve 33, so that the working medium flows at the mating interface between the pump body 31 and the guide sleeve 33. Both the connecting hole 331 and the connecting groove are for the purpose of realizing the flow of working medium inside and outside the guide sleeve 33, and are different forms of connecting structures.

[0034] One end of the guide sleeve 33 facing the rotating shaft 2 is closed by its end wall. The outer surface of the end wall of the guide sleeve 33 abuts against the outer circumferential surface of the bearing outer ring 62 in the eccentric structure 6. The outer surface of the end wall of the guide sleeve 33 forms a mating surface 332, which is a plane in this embodiment. One end of the plunger 32 extending out of the pump body 31 is located inside the guide sleeve 33 and abuts against the inner surface of the end wall of the guide sleeve 33. In this way, when the eccentric structure 6 pushes the guide sleeve 33, the guide sleeve 33 can transmit the force to the plunger 32. When the contact point between the eccentric structure 6 and the guide sleeve 33 deviates from the axis of the guide sleeve 33, the guide sleeve 33 bears a lateral force. Since the guide sleeve 33 and the pump body 31 can guide and cooperate, the movement posture of the guide sleeve 33 will not change, and the lateral force will not be transmitted to the plunger 32, reducing the wear of the plunger 32.

[0035] However, due to factors such as machining precision, there may be a certain gap between the guide sleeve 33 and the pump body 31, which may cause a certain amount of wobble in the guide sleeve 33 during actual operation. In this embodiment, the end face of the plunger 32 used to abut against the guide sleeve 33 is set as a spherical surface. On the one hand, this can further ensure that the force exerted by the guide sleeve 33 on the plunger 32 is along the axial direction of the plunger 32, further reducing the wear of the plunger 32. On the other hand, it can also reduce the friction between the guide sleeve 33 and the plunger 32, reducing working resistance.

[0036] Two limiting edges 333 are provided at the end of the guide sleeve 33 facing the rotating shaft 2. The limiting edges 333 and the end wall of the guide sleeve 33 together form a groove structure. The bearing outer ring 62 is embedded in this groove structure. The two limiting edges 333 are located on both sides of the axial direction of the bearing outer ring 62, thereby limiting the bearing outer ring 62. The outer circumferential surface of the bearing outer ring 62 and the outer surface of the end wall of the guide sleeve 33 are mainly in rolling contact, while the axial end face of the bearing outer ring 62 and the limiting edges 333 will have a large amount of relative sliding. Therefore, the axial end face of the bearing outer ring 62 is also provided with a wear-resistant layer 622.

[0037] Under the push of the eccentric structure 6, both the guide sleeve 33 and the plunger 32 will move toward the pump body 31. After the push is completed, the guide sleeve 33 and the plunger 32 need to move away from the pump body 31. This process is the reset process of the guide sleeve 33 and the plunger 32. The reset of the guide sleeve 33 and the plunger 32 is achieved by the elastic element.

[0038] Combined with appendix Figure 8 An elastic element is provided between the guide sleeve 33 and the pump body 31 to move the guide sleeve 33 away from the pump body 31 to achieve reset. The elastic element is an external helical spring 34. The two ends of the external helical spring 34 are respectively pressed against the abutment shoulders on the pump body 31 and the guide sleeve 33. When in use, the external helical spring 34 is always in a compressed state.

[0039] An elastic pushing structure is provided between the plunger 32 and the pump body 31. Specifically, the elastic pushing structure is an internal helical spring 35 located in the plug hole 315. During use, the internal helical spring 35 is always in a compressed state.

[0040] The pump body 31 includes a main body and a plug 316. The plug hole 315 is a through hole that extends through the main body along its extension direction. The plug 316 is installed at the end of the plug hole 315 away from the guide sleeve 33. The plug 316 is connected to the plug hole 315 by threads. A sealing ring is also installed on the plug 316 to form a good seal between the plug 316 and the inner wall of the plug hole 315, preventing pressure leakage. By machining the through hole first and then installing the plug 316, the machining difficulty of the plug hole 315 can be reduced.

[0041] The two ends of the internal helical spring 35 are respectively abutted against the plug 316 and the plunger 32. The end of the plug 316 extending into the plug hole 315 is provided with a limiting post 317 that inserts into the internal helical spring 35 and provides radial restraint for the helical spring. Due to the compact design of the pump body 31, the pumping channel 312 is designed as close as possible to the end of the plug hole 315. Without the limiting post 317, after the internal helical spring 35 is installed in the plug hole 315, the end of the internal helical spring 35 furthest from the plunger 32 is prone to instability and tilting, entering the pumping channel 312 and affecting its normal use. The limiting post 317 effectively prevents this phenomenon. Setting the limiting post 317 on the plug 316 facilitates the machining of the limiting post 317.

[0042] The pressurization assembly 4 is used to pre-pressurize the working medium entering the plunger assembly 3, so that the working medium can enter the plunger assembly 3 more easily and quickly. The pressurization assembly 4 includes a pressurization housing 41 and an impeller 42. In use, the pressurization housing 41 is fixed relative to the outer housing 1, while the impeller 42 rotates with the shaft 2.

[0043] See appendix Figure 13 Appendix Figure 14 and attached Figure 15 The pressurizing housing 41 has an inner cavity including a central pressurizing region 411 and a conveying region 412 surrounding the pressurizing region 411. The impeller 42 is located in the pressurizing region 411. The housing wall corresponding to the pressurizing region 411 is provided with an intake port 413 for drawing in the working medium, and the housing wall corresponding to the conveying region 412 is provided with an outlet port 414 for discharging the working medium. When the impeller 42 rotates, the working medium is drawn axially from the intake port 413 into the pressurizing housing 41, then flows radially outwards under the drive of the impeller 42, and the pressure increases, finally being discharged from the outlet port 414.

[0044] The portion of the booster housing 41 corresponding to the booster area 411 is a disc-shaped structure, while the portion of the booster housing 41 corresponding to the conveying area 412 is a leg-shaped structure. The number of leg-shaped structures is the same as the number of plunger assemblies 3. Each leg-shaped structure has a connecting hole 415 at its end for fixing the booster housing 41 to the corresponding plunger assembly 3. An opening can be provided on the pump body 31 at the position corresponding to the connecting hole 415 to fix the booster housing 41, pump body 31, and end cover 12 together using the same screw; alternatively, a threaded hole 23 can be provided on the pump body 31 at the position corresponding to the connecting hole 415, allowing the booster housing 41 to be connected separately to the pump body 31, while the pump body 31 has an additional opening for mounting to the end cover 12. Furthermore, each leg-shaped structure has a discharge port 414, which connects to the inlet of the pumping channel 312 of the corresponding plunger assembly 3, allowing the pressurized working medium to directly enter the pumping channel 312.

[0045] The pressurization housing 41 has a disc-shaped structure with two end walls in the axial direction. One end wall is an open end wall 416 with a central opening, and the other end wall is a complete end wall 417. The central hole of the open end wall 416 forms the suction port 413 and also a through hole for the rotating shaft 2 to pass through. The end of the rotating shaft 2 passes through the central hole of the open end wall 416 into the pressurization housing 41. The impeller 42 is fixedly installed at the end of the rotating shaft 2 and can rotate with the rotating shaft 2. An annular space is left between the wall of the central hole on the open end wall 416 and the rotating shaft 2, through which the working medium can enter the pressurization housing 41.

[0046] The central hole on the end wall 416 faces away from the pump inlet 13 and towards the eccentric structure 6. The end wall of the outer shell 1 with the pump inlet 13 is adjacent to and opposite to the complete end wall 417 of the booster shell 41. A gap is left between the end wall of the outer shell 1 with the pump inlet 13 and the complete end wall 417 of the booster shell 41 to allow the working medium to flow in all directions. In this way, the working medium entering the inner cavity of the outer shell 1 from the pump inlet 13 will first spread out and flow in all directions, then bypass the booster shell 41 and flow radially towards the rotating shaft 2, and finally enter the booster shell 41 axially. During this process, a part of the working medium will pass through the eccentric structure 6 and flow through the flushing groove 612 of the eccentric inner ring 61. The working medium flows fully in the inner cavity of the outer shell 1, which can remove the heat generated by each part of the operation, and at the same time enhance the flow rate of the working medium in the flushing groove 612, improving the heat dissipation and lubrication effect of the eccentric structure 6.

[0047] A guide ring 418 extending axially outward from the pressure shell 41 is provided at the center hole wall of the opening end wall 416. The inner surface radius of the guide ring 418 is greater than the maximum distance from the outer circumference of the bearing outer ring 62 to the axis of the rotating shaft 2, so that all parts of the eccentric structure 6 are within the inner diameter range of the guide ring 418, thereby allowing more working medium to pass through the eccentric structure 6.

[0048] The complete end wall 417 of the booster housing 41 is machined separately from other parts and then assembled together. A sealing strip is provided between the two parts to ensure a reliable seal. This arrangement facilitates the machining of the booster housing 41 and the installation of the impeller 42.

[0049] See appendix Figure 16 and attached Figure 17The impeller 42 includes an annular mounting portion 421, a wheel plate 422 fixed to the outer periphery of the mounting portion 421, and blades 423 fixed to one side of the wheel plate 422. The thickness direction of the wheel plate 422 is parallel to the axial direction of the rotating shaft 2. The blades 423 have an arc-shaped structure and are located on the side of the wheel plate 422 facing the suction port 413. The side of the wheel plate 422 facing away from the suction port 413 is set close to the complete end wall 417, with a certain gap between it and the complete end wall 417 to ensure normal rotation of the wheel plate 422. The wheel plate 422 provides reliable support for the blades 423, and the gapless connection between the wheel plate 422 and the blades 423 restricts the axial flow of the working medium, thereby enhancing the pressurization effect on the working medium.

[0050] A guide surface 424 is provided on the outer periphery of the mounting part 421. The diameter of the guide surface 424 gradually increases from the end near the suction port 413 to the end near the wheel plate 422 to guide the working medium to change from axial flow to radial flow. In this embodiment, the taper of the guide surface 424 in the direction from the suction port 413 to the wheel plate 422 gradually increases, then decreases again, then increases again, and then connects with the plate surface of the wheel plate 422.

[0051] Additionally, the guide surface 424 facilitates the installation of the stepped opening 425 at the center of the mounting section 421. The stepped opening 425 at the center of the mounting section 421 is for easy installation of the impeller 42. The smaller diameter section of the stepped opening 425 is used to fit onto the rotating shaft 2, while the larger diameter section is used to insert the pressure plate 43. The pressure plate 43 is located at the axial end face of the rotating shaft 2. The diameter of the pressure plate 43 is larger than the end diameter of the rotating shaft 2, and a screw passes through the center of the pressure plate 43. A threaded hole 23 for installing this screw is provided on the end face of the rotating shaft 2.

[0052] The rotating shaft 2 includes a rotating engagement section 21 and a mounting transmission section 22. The rotating engagement section 21 is used to rotate with the end cover 12, and the mounting transmission section 22 is used to mount the eccentric structure 6 and the impeller 42. The diameter of the mounting transmission section 22 is smaller than that of the rotating engagement section 21, so that a shoulder for blocking the eccentric structure 6 is formed between the rotating engagement section 21 and the mounting transmission section 22. The mounting part 421 of the impeller 42 is axially abutted against the eccentric inner ring 61 of the eccentric structure 6. The impeller 42 is pressed by the pressure plate 43. In this way, the pressure plate 43 and the shoulder abut against the impeller 42 and the eccentric structure 6 from both ends, respectively, so that the impeller 42 and the eccentric structure 6 are axially fixed.

[0053] A keyway is provided at the rotating section 21 of the rotating shaft 2, and a transmission key 24 is provided in the keyway. The length of the transmission key 24 covers the impeller 42 and the eccentric structure 6. Keyways that mate with the transmission key 24 are provided at corresponding positions of the impeller 42 and the eccentric structure 6. In this way, the impeller 42 and the eccentric structure 6 can achieve circumferential transmission through the same transmission key 24.

[0054] Specific embodiment 2 of the radial plunger pump provided by the present invention: This embodiment is based on embodiment 1. The difference between this embodiment and embodiment 1 is that the end face of the plunger that contacts the inner surface of the guide sleeve end wall is a plane. In this embodiment, the friction between the plunger and the guide sleeve is reduced by strictly controlling the roughness of the plunger end face and the machining accuracy of the plunger, pump body and guide sleeve.

[0055] Specific embodiment 3 of the radial plunger pump provided by the present invention: This embodiment is based on embodiment 1. The difference between this embodiment and embodiment 1 is that the plug hole is a blind hole directly machined on the pump body. In order to position the internal helical spring, the position where the plug hole connects to the pumping channel is not at the end of the plug hole, but near the middle of the plug hole. In this way, a certain space can be left at the end of the plug hole to embed the internal helical spring and provide radial limit for the internal helical spring.

[0056] Specific embodiment 4 of the radial plunger pump provided by the present invention: This embodiment is based on Embodiment 1, but differs in that the eccentric structure in this embodiment is an eccentric shaft segment integrally machined on the rotating shaft. The outer circumferential surface of the eccentric shaft segment abuts against and slides against the mating surface on the guide sleeve. Before entering the pressurization shell, the working medium in the inner cavity of the outer shell also passes through the outer circumference of the eccentric shaft segment, thereby carrying away the frictional heat at the eccentric shaft segment.

[0057] Specific embodiment 5 of the radial plunger pump provided by the present invention: This embodiment is based on Embodiment 1. The difference between this embodiment and Embodiment 1 is that the outer peripheral surface of the mounting part is a cylindrical surface and the outer peripheral surface of the mounting part is perpendicular to the plate surface of the wheel plate. In this embodiment, the working medium is guided by twisting one end of the blade near the mounting part.

[0058] Specific embodiment 6 of the radial plunger pump provided by the present invention: This embodiment is based on embodiment 1. The difference between this embodiment and embodiment 1 is that the impeller does not have a wheel plate in this embodiment, and the blades are fixed on the mounting part. In order to ensure the structural strength of the blades, the thickness of the blades can be increased.

[0059] Specific embodiment 7 of the radial plunger pump provided by the present invention: This embodiment is based on embodiment 1. The difference between this embodiment and embodiment 1 is that the pump inlet is located on the circumferential sidewall of the housing. In order to ensure uniform flow of the working medium, multiple pump inlets can be provided on the circumferential sidewall of the housing.

[0060] Specific embodiment 8 of the radial plunger pump provided by the present invention: This embodiment is based on Embodiment 1. The difference between this embodiment and Embodiment 1 is that the center of both axial end walls of the booster housing is opened in this embodiment. The center opening of the end wall near the pump inlet is the suction port, and the center opening of the end wall away from the pump inlet is a mating hole for rotating with the shaft and sealingly engaging. The blades of the impeller are arranged on the side of the wheel plate facing the suction port. In this embodiment, the working medium that enters the inner cavity of the outer shell through the pump inlet directly enters the booster housing.

[0061] Specific embodiments of the booster assembly for radial plunger pumps provided by the present invention: The booster assembly for the radial piston pump is the same as the booster assembly in the specific embodiment of the radial piston pump described above, and will not be described again.

[0062] Finally, it should be noted that the above descriptions are merely preferred embodiments of the present invention and are not intended to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still make modifications to the technical solutions described in the foregoing embodiments without creative effort, or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A radial piston pump, comprising a housing, a rotating shaft, and piston assemblies arranged around the rotating shaft, wherein the rotating shaft has an eccentric structure for pushing the piston assemblies, characterized in that, A pressurizing assembly is provided inside the housing. The pressurizing assembly includes a pressurizing shell and an impeller. The pressurizing shell is fixed to the housing or the plunger assembly. The pressurizing shell has an inner cavity, which includes a pressurizing area for accommodating the impeller and a conveying area connected to the pressurizing area. The shell wall of the pressurizing shell corresponding to the pressurizing area is provided with an inlet for drawing in the working medium. The shell wall of the pressurizing shell corresponding to the conveying area is provided with an outlet for discharging the working medium. The outlet is connected to the inlet of the plunger assembly. The impeller is fixed to the shaft and can rotate with the shaft in the pressurizing area to pressurize the working medium in the pressurizing shell before discharging it.

2. The radial piston pump according to claim 1, characterized in that, The impeller is fixed to the end of the rotating shaft. The two axial end walls of the pressurization shell are respectively the open end wall with a central opening and the complete end wall with a complete structure. The central hole of the open end wall constitutes the suction port and also constitutes the through hole for the rotating shaft to pass through. An annular space is left between the central hole wall of the open end wall and the rotating shaft for the working medium to pass through.

3. The radial piston pump according to claim 2, characterized in that it is eccentric. The structure includes an eccentric inner ring fixed on a rotating shaft and a bearing outer ring sleeved outside the eccentric inner ring and capable of rotating relative to the eccentric inner ring. An axially penetrating flushing groove is provided on the rotational mating interface of at least one of the bearing outer ring and the eccentric inner ring. During use, the working medium flows through the flushing groove before being sucked in by the pressurization component to lubricate and cool the eccentric inner ring and the bearing outer ring.

4. The radial plunger pump according to claim 2 or 3, characterized in that, A flow guide ring extending outward from the center hole wall of the opening end wall is provided, and all parts of the eccentric structure are within the inner diameter range of the flow guide ring.

5. The radial piston pump according to claim 2 or 3, characterized in that, The pump inlet of the radial piston pump is located on the end wall of one axial end of the housing. The end wall of the housing with the pump inlet is adjacent to the complete end wall of the booster housing, and a gap is left between them to allow the working medium to flow freely.

6. The radial piston pump according to any one of claims 1-3, characterized in that, The impeller includes an annular mounting portion, a wheel plate fixed to the outer periphery of the mounting portion with its thickness direction parallel to the axial direction, and blades fixed to one side of the wheel plate along the axial direction. The side of the wheel plate with blades faces the suction port on the booster housing.

7. A booster assembly for a radial piston pump, characterized in that, It includes a pressure chamber and an impeller. In use, the pressure chamber is fixed to the outer shell or plunger assembly of the radial plunger pump. The pressure chamber has an inner cavity, which includes a pressure-boosting area for accommodating the impeller and a conveying area connected around the pressure-boosting area. The shell wall of the pressure chamber corresponding to the pressure-boosting area is provided with an inlet for drawing in the working medium, and the shell wall of the pressure chamber corresponding to the conveying area is provided with an outlet for discharging the working medium. In use, the outlet is connected to the inlet of the plunger assembly. In use, the impeller can rotate with the shaft in the pressure-boosting area, so that the working medium is pressurized in the pressure-boosting shell and then discharged.

8. The booster assembly for a radial piston pump according to claim 7, characterized in that, The two axial end walls of the pressurization housing are an open end wall with a central opening and a complete end wall with a complete structure. The central hole of the open end wall forms the suction port and also forms a through hole for the rotating shaft to pass through. During use, an annular space is left between the central hole wall of the open end wall and the rotating shaft for the working medium to pass through.

9. The booster assembly for a radial plunger pump according to claim 8, characterized in that it has an opening. A flow guide ring extending outward from the center hole of the end wall is provided. The size of the flow guide ring is such that all parts of the eccentric structure in the radial plunger pump are within the inner diameter range of the flow guide ring during use.

10. The booster assembly for a radial piston pump according to any one of claims 7-9, characterized in that, The impeller includes an annular mounting portion, a wheel plate fixed to the outer periphery of the mounting portion with its thickness direction parallel to the axial direction, and blades fixed to one side of the wheel plate along the axial direction. The side of the wheel plate with blades faces the suction port on the booster housing.

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