阅读说明：本技术 一种径向柱塞泵 (Radial plunger pump ) 是由 常志 于 2020-11-23 设计创作，主要内容包括：本发明公开了一种径向柱塞泵,包括壳体、配油轴、转子以及用于带动转子旋转的传动轴,还包括套设于转子外周的定子组件、以及用于调节定子组件与转子之间偏心距的滑座组件,所述配油轴设于所述壳体内,所述传动轴设于所述壳体上,所述配油轴上设有用于平衡所述配油轴所受到的径向作用力的第一配油窗口和第二配油窗口,所述转子上设有与所述第一配油窗口和所述第二配油窗口相对应的多个柱塞。通过配油轴径向受力平衡设计,配油轴弯曲变形的问题被极大改善,减小了转子与配油轴的磨损,提高了径向柱塞泵的压力等级。(The invention discloses a radial plunger pump, which comprises a shell, an oil distribution shaft, a rotor, a transmission shaft, a stator component and a sliding seat component, wherein the transmission shaft is used for driving the rotor to rotate, the stator component is sleeved on the periphery of the rotor, the sliding seat component is used for adjusting the eccentric distance between the stator component and the rotor, the oil distribution shaft is arranged in the shell, the transmission shaft is arranged on the shell, the oil distribution shaft is provided with a first oil distribution window and a second oil distribution window which are used for balancing the radial acting force applied to the oil distribution shaft, and the rotor is provided with a plurality of plungers corresponding to the first oil distribution window and the second oil distribution window. Through the design of the radial stress balance of the oil distribution shaft, the problem of bending deformation of the oil distribution shaft is greatly improved, the abrasion of a rotor and the oil distribution shaft is reduced, and the pressure grade of the radial plunger pump is improved.)

1. The utility model provides a radial plunger pump, includes casing (1), joins in marriage oily axle (3), rotor (5) and is used for driving transmission shaft (4) that rotor (5) are rotatory, its characterized in that: still locate stator module (15) of rotor (5) periphery and be used for adjusting slide subassembly (16) of eccentricity between stator module (15) and rotor (5) including the cover, oil distribution shaft (3) are located in casing (1), transmission shaft (4) are located on casing (1), be equipped with on oil distribution shaft (3) and be used for balancing first oil distribution window (31) and second oil distribution window (32) of the radial effort that oil distribution shaft (3) received, be equipped with on rotor (5) with first oil distribution window (31) with a plurality of plungers (11) that second oil distribution window (32) are corresponding.

2. The radial plunger pump of claim 1, wherein: the first oil distribution window (31) comprises a front oil discharge area (311) and a rear oil suction area (312), the second oil distribution window (32) comprises a front oil suction area (321) and a rear oil discharge area (322), the front oil discharge area (311) is located above the front oil suction area (321), the rear oil suction area (312) is located above the rear oil discharge area (322), the front oil suction area (321) is communicated with the rear oil suction area (312), and the front oil discharge area (311) is communicated with the rear oil discharge area (322).

3. The radial plunger pump of claim 2, wherein: the oil distribution shaft (3) is further provided with an oil suction port (33), an oil discharge port (34), a first channel (35) and a second channel (36), one end of the first channel (35) is communicated with the oil suction port (33), the front oil suction area (321) and the rear oil suction area (312) are both communicated with the other end of the first channel (35), one end of the second channel (36) is communicated with the oil discharge port (34), and the front oil discharge area (311) and the rear oil discharge area (322) are both communicated with the other end of the second channel (36); or, the oil distribution shaft (3) is further provided with an oil suction port (33), an oil discharge port (34), a first channel (35), a second channel (36), a third channel (37) and a fourth channel (38), one end of the first channel (35) is communicated with the oil suction port (33), the other end of the first channel is communicated with the front oil suction area (321), one end of the second channel (36) is communicated with the oil discharge port (34), the other end of the second channel is communicated with the rear oil discharge area (322), one end of the third channel (37) is communicated with the first channel (35), the other end of the third channel is communicated with the rear oil suction area (312), one end of the fourth channel (38) is communicated with the second channel (36), and the other end of the fourth channel is communicated with the front oil discharge area (311).

4. The radial plunger pump of claim 2, wherein: servo variable mechanism (13) and thrust piston (14) that are used for promoting slide subassembly (16) along rotor (5) radial movement are connected respectively to the both sides that slide subassembly (16) is relative, be equipped with on casing (1) and be used for preceding oil absorption district (321) with oil absorption district (312) make up oil supplementing switching-over valve (19) of fluid after, be equipped with pump cover (2) on casing (1), transmission shaft (4) are located on pump cover (2), be equipped with on pump cover (2) and be used for providing oil feeding unit (18) of pressure oil for servo variable mechanism (13), thrust piston (14) and oil supplementing switching-over valve (19).

5. The radial plunger pump of claim 4, wherein: the oil supplementing reversing valve (19) comprises an input port and two output ports, the input port is communicated with the oil supply component (18), one of the output ports is communicated with the first oil suction one-way valve (29), the other output port is communicated with the second oil suction one-way valve (30), the input port of the first oil suction one-way valve (29) is connected with the first oil pipe (39), the output port is communicated with the oil suction port (33), the input port of the second oil suction one-way valve (30) is connected with the second oil pipe (40), and the output port is communicated with the oil discharge port (34).

6. The radial plunger pump of claim 4, wherein: an oil supply part overflow valve (41) is arranged on the oil discharge side of the oil supply part (18), an oil supply pressure valve (42) is arranged between the oil supply reversing valve (19) and the oil supply part overflow valve (41), a first safety overflow valve (43) is arranged between the oil suction port (33) and the first oil suction one-way valve (29), a second safety overflow valve (44) is arranged between the oil discharge port (34) and the second oil suction one-way valve (30), a first oil port (52) and a second oil port (53) are further arranged on the shell (1), the first oil port (52) is communicated with the oil suction port (33), the second oil port (53) is communicated with the oil discharge port (34), and an unloading valve (45) is arranged between the first oil port (52) and the second oil port (53).

7. The radial plunger pump of claim 4, wherein: the stator assembly (15) comprises a front stator (6) and a rear stator (8), the sliding seat assembly (16) comprises a front sliding seat (7), a rear sliding seat (9) and a linkage lever (10) for realizing reverse movement of the front sliding seat and the rear sliding seat, the front stator (6) is connected with the front sliding seat (7), the rear stator (8) is connected with the rear sliding seat (9), the front stator (6) is positioned on the periphery of the front oil suction area (321), and the rear stator (8) is positioned on the periphery of the rear oil suction area (312); the servo variable mechanism (13) and the thrust piston (14) are abutted against two opposite sides of the front sliding seat (7); or the servo variable mechanism (13) and the thrust piston (14) are abutted against two opposite sides of the rear sliding seat (9).

8. The radial plunger pump of claim 7, wherein: the servo variable mechanism (13) comprises a linear motor (22), a servo piston (21), a servo valve core (23), a valve body (25) and a valve cover (51), the valve body (25) and the valve cover (51) are matched to form a pressure oil cavity (24), the servo valve core (23) is connected with the linear motor (22), an oil inlet groove (27), an oil drainage groove (271) and an oil drainage port (28) are arranged on the servo valve core (23), a bulge (231) is formed between the oil inlet groove (27) and the oil drainage groove (271), the servo piston (21) is sleeved on the periphery of the servo valve core (23), the servo piston (21) is abutted against the front sliding seat (7) or the rear sliding seat (9), a piston inner groove (211) corresponding to the bulge (231) is arranged on the servo piston (21), and a pressure oil channel (26) is arranged on the circumference of the piston inner groove (211), the thrust of the thrust piston (14) is smaller than the thrust of the servo piston (21).

9. The radial plunger pump of claim 7, wherein: the two opposite sides of the front sliding seat (7) are respectively provided with a first eccentricity indicator (47) and a third eccentricity indicator (49), and the two opposite sides of the rear sliding seat (9) are respectively provided with a second eccentricity indicator (48) and a fourth eccentricity indicator (50).

10. The radial piston pump as claimed in any one of claims 1 to 9, wherein: the rotor (5) is provided with four rows of plunger holes (20) in the radial direction, each row of plunger holes comprises a plurality of plunger holes (20) and is uniformly arranged along the circumferential direction of the rotor (5), the rows of plunger holes (20) are staggered with each other, the plungers (11) are arranged in the plunger holes (20), and the inner wall of the stator assembly (15) is provided with inclined planes (17) corresponding to the rows of plunger holes (20).

Technical Field

The invention relates to the technical field of plunger pumps, in particular to a radial plunger pump.

Background

The plunger pump realizes oil suction and oil discharge through the change of the sealed working volume when the plunger reciprocates in the plunger hole. Because the plunger and the inner hole of the cylinder are both cylindrical surfaces, and the matching precision of the sliding surfaces is high, the pump has the characteristics of small leakage, high volumetric efficiency and capability of working under a high-pressure condition.

In the prior art, the radial plunger pump adopting the shaft flow distribution mode has the problems that the flow distribution gap is continuously increased and the leakage problem is serious day by day due to the abrasion of the flow distribution shaft caused by the machining and assembling of the oil distribution shaft and the cylinder body, and the volumetric efficiency of the radial plunger pump is greatly influenced. Particularly, the oil distribution shaft is under the action of radial unbalanced hydraulic pressure, so that the bending deformation of the oil distribution shaft is large, the abrasion of the oil distribution shaft is large, the service life of the radial plunger pump is further shortened, and meanwhile, the improvement of the speed and the pressure grade of the radial plunger pump is limited due to the large radial size and the complex structure of the radial plunger pump and the poor self-absorption capacity.

Disclosure of Invention

The invention aims to overcome the defects in the prior art and provide a radial plunger pump which can overcome the problem of unbalanced radial force applied to an oil distribution shaft and improve the pressure grade of the radial plunger pump.

In order to solve the technical problems, the invention adopts the following technical scheme: the oil distribution device comprises a shell, an oil distribution shaft, a rotor and a transmission shaft used for driving the rotor to rotate, and further comprises a stator assembly sleeved on the periphery of the rotor and a sliding seat assembly used for adjusting the eccentricity between the stator assembly and the rotor, wherein the oil distribution shaft is arranged in the shell, the transmission shaft is arranged on the shell, a first oil distribution window and a second oil distribution window which are used for balancing the radial acting force applied to the oil distribution shaft are arranged on the oil distribution shaft, and a plurality of plungers corresponding to the first oil distribution window and the second oil distribution window are arranged on the rotor.

As a further improvement of the above technical solution: the first oil distribution window comprises a front oil discharge area and a rear oil suction area, the second oil distribution window comprises a front oil suction area and a rear oil discharge area, the front oil discharge area is located above the front oil suction area, the rear oil suction area is located above the rear oil discharge area, the front oil suction area is communicated with the rear oil suction area, and the front oil discharge area is communicated with the rear oil discharge area.

As a further improvement of the above technical solution: the oil distribution shaft is also provided with an oil suction port, an oil discharge port, a first channel and a second channel, one end of the first channel is communicated with the oil suction port, the front oil suction area and the rear oil suction area are both communicated with the other end of the first channel, one end of the second channel is communicated with the oil discharge port, and the front oil discharge area and the rear oil discharge area are both communicated with the other end of the second channel; or, the oil distribution shaft is also provided with an oil suction port, an oil discharge port, a first channel, a second channel, a third channel and a fourth channel, one end of the first channel is communicated with the oil suction port, the other end of the first channel is communicated with the front oil suction area, one end of the second channel is communicated with the oil discharge port, the other end of the second channel is communicated with the rear oil discharge area, one end of the third channel is communicated with the first channel, the other end of the third channel is communicated with the rear oil suction area, one end of the fourth channel is communicated with the second channel, and the other end of the fourth channel is communicated with the front oil discharge area.

As a further improvement of the above technical solution: the two opposite sides of the sliding seat assembly are respectively connected with a servo variable mechanism and a thrust piston which are used for pushing the sliding seat assembly to move along the radial direction of the rotor, the shell is provided with an oil supplementing reversing valve which is used for supplementing oil to the front oil absorption area and the rear oil absorption area, the shell is provided with a pump cover, the transmission shaft is arranged on the pump cover, and the pump cover is provided with an oil supply component which is used for providing pressure oil for the servo variable mechanism, the thrust piston and the oil supplementing reversing valve.

As a further improvement of the above technical solution: the oil supplementing reversing valve comprises an input port and two output ports, the input port is communicated with the oil supply component, one output port is communicated with the first oil suction one-way valve, the other output port is communicated with the second oil suction one-way valve, the input port of the first oil suction one-way valve is connected with the first oil pipe, the output port is communicated with the oil suction port, the input port of the second oil suction one-way valve is connected with the second oil pipe, and the output port is communicated with the oil discharge port.

As a further improvement of the above technical solution: the oil supply device is characterized in that an oil supply part overflow valve is arranged on the oil discharge side of the oil supply part, an oil supply pressure valve is arranged between the oil supply reversing valve and the oil supply part overflow valve, a first safety overflow valve is arranged between the oil suction port and the first oil suction one-way valve, a second safety overflow valve is arranged between the oil discharge port and the second oil suction one-way valve, a first oil port and a second oil port are further arranged on the shell, the first oil port is communicated with the oil suction port, the second oil port is communicated with the oil discharge port, and a zero unloading valve is arranged between the first oil port and the second oil port.

As a further improvement of the above technical solution: the stator assembly comprises a front stator and a rear stator, the sliding seat assembly comprises a front sliding seat, a rear sliding seat and a linkage lever for realizing reverse movement of the front sliding seat and the rear sliding seat, the front stator is connected with the front sliding seat, the rear stator is connected with the rear sliding seat, the front stator is positioned on the periphery of the front oil absorption area, and the rear stator is positioned on the periphery of the rear oil absorption area; the servo variable mechanism and the thrust piston are abutted against two opposite sides of the front sliding seat; or the servo variable mechanism and the thrust piston are abutted against two opposite sides of the rear sliding seat.

As a further improvement of the above technical solution: the servo variable mechanism comprises a linear motor, a servo piston, a servo valve core, a valve body and a valve cover, wherein the valve body and the valve cover are matched to form a pressure oil cavity, the servo valve core is connected with the linear motor, an oil inlet groove, an oil drainage groove and an oil drainage port are formed in the servo valve core, a bulge is formed between the oil inlet groove and the oil drainage groove, the servo piston is sleeved on the periphery of the servo valve core, the servo piston is abutted against a front sliding seat or a rear sliding seat, a piston inner groove corresponding to the bulge is formed in the servo piston, a pressure oil channel is formed in the circumference of the piston inner groove, and the thrust of the thrust piston is smaller than the thrust of the servo piston.

As a further improvement of the above technical solution: the two opposite sides of the front sliding seat are respectively provided with a first eccentric indicator and a third eccentric indicator, and the two opposite sides of the rear sliding seat are respectively provided with a second eccentric indicator and a fourth eccentric indicator.

As a further improvement of the above technical solution: the rotor is provided with four rows of plunger holes in the radial direction, each row of plunger holes comprises a plurality of plunger holes and is uniformly arranged along the circumferential direction of the rotor, the rows of plunger holes are staggered with each other, the plungers are arranged in the plunger holes, and the inner wall of the stator assembly is provided with inclined planes corresponding to the rows of plunger holes.

Compared with the prior art, the invention has the beneficial effects that: when the radial plunger pump works, under the action of pressure oil, two radial acting forces which are opposite in direction and mutually offset are formed at the circumferences of the first oil distribution window 31 and the second oil distribution window 32, and the problem of unbalanced radial acting force borne by the oil distribution shaft 3 is solved. Through the radial stress balance design of the oil distribution shaft 3, the problem of bending deformation of the oil distribution shaft 3 is greatly improved, and the abrasion of the rotor 5 and the oil distribution shaft 3 is reduced, so that the bidirectional variable plunger pump can reach a high pressure level.

Drawings

FIG. 1 is a front view of the radial piston pump of the present invention.

Fig. 2 is a top view of the radial piston pump of the present invention.

Fig. 3 is a cross-sectional view taken at a-a in fig. 1.

Fig. 4 is a partially enlarged view of fig. 3 at B.

Fig. 5 is a cross-sectional view at C-C in fig. 2.

Fig. 6 is a partial enlarged view of fig. 5 at D.

Fig. 7 is a schematic structural diagram of an area of an oil supply reversing valve in the radial plunger pump.

Fig. 8 is a schematic structural view of an oil distribution shaft in the radial plunger pump of the present invention.

Fig. 9 is a bottom view of the oil distribution shaft of the radial piston pump of the present invention.

Fig. 10 is a cross-sectional view taken at E-E of fig. 9.

Fig. 11 is a cross-sectional view at F-F in fig. 9.

Fig. 12 is a schematic structural view of a rotor in the radial piston pump of the present invention.

Fig. 13 is a cross-sectional view at G-G in fig. 12.

FIG. 14 is a rear view of the radial piston pump of the present invention.

Fig. 15 is a schematic view showing the plunger abutting against the stator in the present invention.

Fig. 16 is a schematic diagram of a radial piston pump of the present invention.

Fig. 17 is a schematic view of the structure of the plunger of the present invention.

The reference numerals in the figures denote: 1. a housing; 2. a pump cover; 3. an oil distribution shaft; 4. a drive shaft; 5. a rotor; 6. a front stator; 7. a front slide; 8. a rear stator; 9. a rear slide seat; 10. a linkage lever; 11. a plunger; 12. an Oldham coupling; 13. a servo variable mechanism; 14. a thrust piston; 15. a stator assembly; 16. a carriage assembly; 17. a bevel; 18. an oil supply unit; 19. an oil-supplementing reversing valve; 20. a plunger hole; 21. a servo piston; 22. a linear motor; 23. a servo spool; 24. a pressure oil chamber; 25. a valve body; 26. a pressure oil passage; 27. an oil inlet groove; 28. an oil drainage port; 29. a first oil suction check valve; 30. a second oil suction one-way valve; 31. a first oil distribution window; 32. a second oil distribution window; 33. an oil suction port; 34. an oil discharge port; 35. a first channel; 36. a second channel; 37. a third channel; 38. a fourth channel; 39. a first oil pipe; 40. a second oil pipe; 41. an oil supply unit relief valve; 42. an oil-supplementing pressure valve; 43. a first safety overflow valve; 44. a second safety overflow valve; 45. a zero unloading valve; 46. a shaft cover; 47. a first eccentricity indicator; 48. a second eccentricity indicator; 49. a third eccentricity indicator; 50. a fourth eccentricity indicator; 51. a valve cover; 52. a first oil port; 53. a second oil port; 54. a radial plunger pump; 211. an inner piston groove; 231. a protrusion; 271. an oil drainage groove; 311. a front oil drain region; 312. a post oil absorption zone; 321. a front oil suction zone; 322. and a back oil discharge area.

Detailed Description

The invention is described in further detail below with reference to the figures and specific examples of the specification.

Fig. 1 to 17 show an embodiment of a radial plunger pump according to the present invention, where the radial plunger pump of this embodiment includes a housing 1, an oil distribution shaft 3, a rotor 5, a transmission shaft 4 for driving the rotor 5 to rotate, a stator assembly 15 sleeved on the periphery of the rotor 5, and a slider assembly 16 for adjusting an eccentric distance between the stator assembly 15 and the rotor 5, the oil distribution shaft 3 is disposed in the housing 1, the transmission shaft 4 is disposed on the housing 1, the oil distribution shaft 3 is provided with a first oil distribution window 31 and a second oil distribution window 32 for balancing a radial acting force applied to the oil distribution shaft 3, and the rotor 5 is provided with a plurality of plungers 11 corresponding to the first oil distribution window 31 and the second oil distribution window 32.

When the radial plunger pump works, under the action of pressure oil, two opposite radial acting forces which are mutually offset are formed at the circumferences of the first oil distribution window 31 and the second oil distribution window 32, and the problem of unbalanced radial acting force borne by the oil distribution shaft 3 is solved.

Further, in this embodiment, the first oil distribution window 31 includes a front oil exhaust area 311 and a rear oil exhaust area 312, the second oil distribution window 32 includes a front oil exhaust area 321 and a rear oil exhaust area 322, the front oil exhaust area 311 is located above the front oil exhaust area 321, the rear oil exhaust area 312 is located above the rear oil exhaust area 322, the front oil exhaust area 321 is communicated with the rear oil exhaust area 312, and the front oil exhaust area 311 is communicated with the rear oil exhaust area 322. Under the action of the pressure oil, two acting forces with opposite directions and mutually offset are generated at the circumferences of the front oil discharge area 311 and the rear oil discharge area 322, and the problem of unbalanced radial acting force applied to the oil distribution shaft 3 is further solved. A plurality of corresponding triangular unloading grooves (not shown in the figure) are arranged at the junction of the closed volumes of the first oil distribution window 31 and the second oil distribution window 32 corresponding to the rotation direction of the rotor 5, so that the problem of oil trapping in the closed volume region is solved, and the noise, vibration and pulsation of the operation of the plunger pump are reduced.

Further, in this embodiment, the oil distribution shaft 3 is further provided with an oil suction port 33, an oil discharge port 34, a first passage 35 and a second passage 36, one end of the first passage 35 is communicated with the oil suction port 33, the front oil suction area 321 and the rear oil suction area 312 are both communicated with the other end of the first passage 35, one end of the second passage 36 is communicated with the oil discharge port 34, and the front oil discharge area 311 and the rear oil discharge area 322 are both communicated with the other end of the second passage 36; or, the oil distribution shaft 3 is further provided with an oil suction port 33, an oil discharge port 34, a first passage 35, a second passage 36, a third passage 37 and a fourth passage 38, one end of the first passage 35 is communicated with the oil suction port 33, the other end of the first passage 35 is communicated with the front oil suction area 321, one end of the second passage 36 is communicated with the oil discharge port 34, the other end of the second passage 36 is communicated with the rear oil discharge area 322, one end of the third passage 37 is communicated with the first passage 35, the other end of the third passage is communicated with the rear oil suction area 312, one end of the fourth passage 38 is communicated with the second passage 36, and the other end of the fourth passage 38 is communicated with the front oil discharge area 311. When the rotor 5 rotates to the front oil suction area 321 and the rear oil suction area 312, the oil flows into the first passage 35 through the oil suction port 33 and further flows into the front oil suction area 321 and the rear oil suction area 312, and when the rotor 5 rotates to the front oil discharge area 311 and the rear oil discharge area 322, the pressure oil flows into the second passage 36 through the front oil discharge area 311 and the rear oil discharge area 322 and is further discharged through the oil discharge port 34; alternatively, when the rotor 5 rotates to the front oil suction area 321 and the rear oil suction area 312, the oil flows into the first passage 35 and the third passage 37 through the oil suction port 33, and then flows into the front oil suction area 321 and the rear oil suction area 312, respectively, and when the rotor 5 rotates to the front oil discharge area 311 and the rear oil discharge area 322, the pressure oil flows into the fourth passage 38 and the second passage 36 through the front oil discharge area 311 and the rear oil discharge area 322, and then is discharged through the oil discharge port 34.

Further, in this embodiment, two opposite sides of the slide seat assembly 16 are respectively connected to a servo variable mechanism 13 and a thrust piston 14, which are used for pushing the slide seat assembly 16 to move along the radial direction of the rotor 5, the casing 1 is provided with an oil compensation reversing valve 19, which is used for supplementing oil to the front oil absorption area 321 and the rear oil absorption area 312, the casing 1 is provided with a pump cover 2, the transmission shaft 4 is arranged on the pump cover 2, and the pump cover 2 is provided with an oil supply component 18, which is used for providing pressure oil to the servo variable mechanism 13, the thrust piston 14 and the oil compensation reversing valve 19.

In the radial plunger pump, an oil supply part 18 preferably selects a gear pump as an auxiliary pump, coaxially rotates with a transmission shaft 4, continuously and alternately supplies oil to two oil suction areas through an oil supply reversing valve 19, and simultaneously supplies pressure oil to a servo variable mechanism 13 and a thrust piston 14; when the stator assembly 15 and the rotor 5 are coaxially arranged, the plunger pump is in a zero position state, and the transmission shaft 4 preferably drives the rotor 5 to rotate around the oil distribution shaft 3 through the Oldham coupling 12; as shown in fig. 5, when the servo variable mechanism 13 pushes the slide carriage assembly 16 to the right to break through the zero position, an eccentric distance occurs between the stator assembly 15 and the rotor 5, when the rotor 5 rotates to two oil suction areas, oil enters the plunger cavities corresponding to the two oil suction areas through the oil distribution shaft 3 to complete an oil suction process, when the rotor 5 rotates to two oil discharge areas, the generated pressure oil is discharged from the plunger cavities corresponding to the two oil discharge areas through the oil distribution shaft 3 to complete an oil discharge process, at this time, two acting forces which are opposite in direction and mutually offset are generated at the circumferences of the front oil discharge area 311 and the rear oil discharge area 322 to achieve the purpose of radial force balance of the oil distribution shaft 3, when the servo variable mechanism 13 retracts to the left to break through the zero position, the thrust piston 14 pushes the sliding seat assembly 16 to the left to enable the eccentric distance to move reversely, the oil paths for oil suction and oil discharge are also changed reversely, and the oil suction and oil discharge functions of the two oil suction areas and the two oil discharge areas are mutually exchanged; when the servo variable mechanism 13 or the thrust piston 14 pushes the sliding seat assembly 16 to break through zero positions leftwards and rightwards, an eccentric distance is generated between the stator assembly 15 and the rotor 5, the larger the eccentric distance is, the larger the stroke of the reciprocating motion of the plunger 11 is, and therefore the more the pressure oil quantity pumped by the plunger pump is; therefore, the radial plunger pump can realize the functions of unidirectional quantification, unidirectional variable, bidirectional quantification, bidirectional variable and the like.

Further, in this embodiment, the oil-replenishing reversing valve 19 includes an input port and two output ports, the input port is communicated with the oil supply unit 18, one of the output ports is communicated with the first oil-sucking one-way valve 29, the other output port is communicated with the second oil-sucking one-way valve 30, the input port of the first oil-sucking one-way valve 29 is connected with the first oil pipe 39, the output port is communicated with the oil-sucking port 33, the input port of the second oil-sucking one-way valve 30 is connected with the second oil pipe 40, and the output port is communicated with the oil-discharging port 34. The oil supply component 18 is preferably a gear pump which supplies pressure oil to two oil suction areas of the oil distribution shaft 3 continuously and alternately through the oil compensation reversing valve 19, so that the phenomenon that the oil suction port 33 cannot suck oil in the oil suction process is avoided. When the eccentricity between the rotor 5 and the stator assembly 15 is small and the oil output by the gear pump can meet the oil quantity required by the two oil suction areas, the first oil suction one-way valve 29 is in a closed state under the action of the oil pressure of the two oil suction areas, the oil supplemented by the gear pump flows into the oil suction port 33 through the first oil suction one-way valve 29, and meanwhile, the second oil suction one-way valve 30 is closed under the action of the pressure oil discharged from the oil discharge port 34; when the eccentricity between the rotor 5 and the stator assembly 15 is large and the oil output by the gear pump cannot meet the oil quantity required by the two oil suction areas, negative pressure is generated in the two oil suction areas, the first oil suction one-way valve 29 is opened, oil sucked from the oil tank and oil supplemented by the gear pump are converged and enter the oil suction port 33, and meanwhile, the second oil suction one-way valve 30 is closed under the action of pressure oil discharged from the oil discharge port 34; when the oil sucking and discharging is reversed, the oil sucking port 33 and the oil discharging port 34 are exchanged, and the opening or closing state of the first oil sucking check valve 29 and the second oil sucking check valve 30 is changed.

Further, in this embodiment, an oil supply unit relief valve 41 is disposed on an oil discharge side of the oil supply unit 18, an oil supply pressure valve 42 is disposed between the oil supply reversing valve 19 and the oil supply unit relief valve 41, a first safety relief valve 43 is disposed between the oil suction port 33 and the first oil suction check valve 29, a second safety relief valve 44 is disposed between the oil discharge port 34 and the second oil suction check valve 30, a first oil port 52 and a second oil port 53 are further disposed on the housing 1, the first oil port 52 is communicated with the oil suction port 33, the second oil port 53 is communicated with the oil discharge port 34, and a zero unloading valve 45 is disposed between the first oil port 52 and the second oil port 53. The oil supply part overflow valve 41 controls the pressure of oil output by the oil supply part 18, the oil supplementing pressure valve 42 controls the oil supplementing pressure of the oil supplementing reversing valve 19 to ensure the normal operation of the plunger pump, the first safety overflow valve 43 and the second safety overflow valve 44 control the oil pressure of each actuating mechanism, when the rotor 5 and the stator are coaxially in a zero position state, the unloading zero position valve 45 is opened, and the first oil port 52 is communicated with the second oil port 53. As shown in fig. 5, when the servo variable mechanism 13 pushes the slide carriage assembly 16 to break through the zero position to the right, the zero position unloading valve 45 is closed, and the pressure oil discharged from the oil discharge port 34 is delivered to the actuator through the second oil port 53; when the thrust piston 14 pushes the sliding seat assembly 16 to break through the zero position leftwards, the oil path is also changed reversely, and the pressure oil discharged by the oil distribution shaft 3 is conveyed to the actuating mechanism through the first oil port 52.

Further, in this embodiment, the stator assembly 15 includes a front stator 6 and a rear stator 8, the slide base assembly 16 includes a front slide base 7, a rear slide base 9, and a linkage lever 10 for realizing opposite movement of the front slide base and the rear slide base, the front stator 6 is connected to the front slide base 7, the rear stator 8 is connected to the rear slide base 9, the front stator 6 is located at the periphery of the front oil suction area 321, and the rear stator 8 is located at the periphery of the rear oil suction area 312; the servo variable mechanism 13 and the thrust piston 14 are abutted against two opposite sides of the front sliding seat 7; alternatively, the servo variable mechanism 13 and the thrust piston 14 are abutted against opposite sides of the rear slide 9. The two sliding seats and the two stators are preferably correspondingly connected through deep groove ball bearings, the front sliding seat 7 and the rear sliding seat 9 are preferably connected through a linkage lever 10, as shown in fig. 5, when the servo variable mechanism 13 pushes the front sliding seat 7 to move rightwards, the rear sliding seat 9 is enabled to move leftwards through the action of the linkage lever 10, and when the thrust piston 14 pushes the front sliding seat 7 to move leftwards, the rear sliding seat 9 also moves reversely, so that the eccentric distance between the two stators and the rotor 5 can be flexibly changed; the servo variable mechanism 13 and the thrust piston 14 can also be abutted against two opposite sides of the rear sliding seat 9, so that the moving directions of the front sliding seat 7 and the rear sliding seat 9 are reversely changed, and the oil paths for sucking and discharging oil are also reversely changed along with the change.

Further, in this embodiment, the servo variable mechanism 13 includes a linear motor 22, a servo piston 21, a servo valve element 23, a valve body 25 and a valve cover 51, the valve body 25 and the valve cover 51 cooperate to form a pressure oil chamber 24, the servo valve element 23 is connected to the linear motor 22, the servo valve element 23 is provided with an oil inlet groove 27, an oil drain groove 271 and an oil drain port 28, a protrusion 231 is formed between the oil inlet groove 27 and the oil drain groove 271, the servo piston 21 is sleeved on the periphery of the servo valve element 23, the servo piston 21 is abutted to the front sliding seat 7 or the rear sliding seat 9, the servo piston 21 is provided with a piston inner groove 211 corresponding to the protrusion 231, the piston inner groove 211 is provided with a pressure oil passage 26 on the periphery, and the thrust of the thrust piston 14 is smaller than the thrust of the servo piston 21. As shown in fig. 5, preferably, the servo variable mechanism 13 and the thrust piston 14 abut against the left and right sides of the front slide base 7, the pressure oil output by the oil supply part 18 enters the oil inlet groove 27 of the servo valve core 23 through the passage of the valve cover 51, the linear motor 22 is connected with the servo valve core 23, when the linear motor 22 pushes the servo valve core 23 to the right, the protrusion 231 and the piston inner groove 211 are dislocated to form an oil inlet opening, the pressure oil flows into the pressure oil chamber 24 from the oil inlet groove 27 through the pressure oil passage 26, and then pushes the servo piston 21 to move the front slide base 7 to the right, when the piston inner groove 211 moves to the right to a position corresponding to the protrusion 231, the oil inlet opening is closed, and the servo piston; when the linear motor 22 is retracted to the left, the servo valve core 23 is also retracted along with the linear motor, the protrusion 231 and the piston inner groove 211 are staggered to form an oil drainage opening, pressure oil in the pressure oil cavity 24 is discharged into the pump body through the oil drainage opening and the oil drainage port 28 from the pressure oil passage 26, the servo piston 21 is retracted to the left along with the pressure oil discharging process, the thrust piston 14 pushes the front sliding seat 7 to move to the left, and when the piston inner groove 211 moves to the left to a position corresponding to the protrusion 231, the oil drainage opening is closed, and the servo piston 21 stops moving; therefore, when the plunger pump works, the purpose that the front sliding seat 7 is pushed leftwards and rightwards in the horizontal direction by the thrust piston 14 and the servo piston 21 can be achieved only by adjusting the linear motor 22, the purpose that the electric control stepless variable of the plunger pump is achieved by changing the size of the eccentric distance between the stator and the rotor 5, and accurate displacement and positioning are achieved; the servo variable mechanism 13 and the thrust piston 14 can be abutted against two corresponding sides of the rear slide seat 9, so that the moving directions of the front slide seat 7 and the rear slide seat 9 are changed reversely, and the oil paths for sucking and discharging oil are changed reversely.

Further, in the present embodiment, the front slide 7 is provided with a first eccentricity indicator 47 and a third eccentricity indicator 49 on opposite sides thereof, and the rear slide 9 is provided with a second eccentricity indicator 48 and a fourth eccentricity indicator 50 on opposite sides thereof. The four eccentricity indicators conveniently indicate the eccentricity of the two slides with respect to the rotor 5.

Further, in this embodiment, the rotor 5 is provided with four rows of plunger holes 20 in the radial direction, each row includes a plurality of plunger holes 20 and is uniformly arranged along the circumferential direction of the rotor 5, the rows of plunger holes 20 are staggered with each other, the plungers 11 are disposed in the plunger holes 20, and the inner wall of the stator assembly 15 is provided with inclined planes 17 corresponding to the rows of plunger holes 20. The ramp 17 is preferably a chevron ramp. As shown in fig. 12, the four rows of plunger holes 20 are arranged in a staggered manner, and the four rows of plungers 11 correspond to the four surfaces of the chevron-shaped inclined surfaces of the front stator 6 and the rear stator 8, respectively. When the plunger pump is in a zero-position state, due to the rotation of the rotor 5, the plunger 11 extends outwards and abuts against the herringbone inclined planes corresponding to the two stators under the action of centrifugal force and oil pressure of the two oil absorption areas, friction force is generated between the plunger head of the plunger 11 and the herringbone inclined planes at the moment, the friction force drives the two stators to rotate relative to the two sliding seats, a certain rotation speed difference can be formed between the two stators and the rotor 5, the plunger 11 can form autorotation in the plunger hole 20, and rolling friction is formed between the plunger head and the herringbone inclined planes of the stators, so that the abrasion and heating of the plunger head and the herringbone inclined planes are further reduced.

This radial plunger pump is equipped with the shaft cap 46 on the oil distribution shaft 3, and four passageways of oil distribution shaft 3 are equipped with four corresponding blockings respectively near shaft cap 46, and the jam welds with the passageway, plays sealed passageway's effect. In a zero-position state, the transmission shaft 4 drives the rotor 5 to rotate around the oil distribution shaft 3 through the Oldham coupling 12, the four rows of plungers 11 extend outwards under the action of centrifugal force and oil pressure of the two oil suction areas and are propped against four surfaces of herringbone inclined planes of the corresponding front stator 6 and the rear stator 8, friction force is generated between plunger heads of the plungers 11 and the herringbone inclined planes at the moment, the friction force drives the front stator 6 and the rear stator 8 to rotate relative to the front sliding seat 7 and the rear sliding seat 9, and abrasion and heating between the plungers 11 and the front stator 6 and the rear stator 8 are reduced; as shown in fig. 5, when the servo variable mechanism 13 pushes the front sliding seat 7 to the right, so that opposite eccentricity occurs between the front stator 6 and the rear stator 8 and the rotor 5, when the rotor 5 rotates to the front oil suction area 321 and the rear oil suction area 312, oil flows into the plunger holes 20 on the lower side of the front oil suction area 321 and the upper side of the rear oil suction area 312 through the oil suction port 33 and the first passage 35 and the third passage 37 respectively to complete the oil suction process, and when the rotor 5 rotates to the front oil discharge area 311 and the rear oil discharge area 322, the generated pressure oil respectively enters the fourth passage 38 and the second passage 36 from the plunger holes 20 on the upper side of the front oil discharge area 311 and the lower side of the rear oil discharge area 322 to complete the oil discharge process through the oil discharge port 34; at this time, two acting forces with opposite directions and mutually offset are generated at the circumferences of the front oil discharge area 311 and the rear oil discharge area 322, so as to achieve the purpose of radial force balance of the oil distribution shaft 3. When the servo variable mechanism 13 retracts to the left to break through the zero position, the thrust piston 14 pushes the front sliding seat 7 to the left to enable the eccentric distance to move reversely, and the oil path for oil suction and oil discharge is also changed reversely; when the servo variable mechanism 13 or the thrust piston 14 pushes the front sliding seat 7 to break through zero positions left and right, reverse eccentric motion is generated between the two stators and the rotor 5, the larger the eccentric distance is, the larger the stroke of the reciprocating motion of the plunger 11 is, so that the more the pressure oil pumped by the plunger pump is, and the bidirectional variable function of the plunger pump is realized repeatedly and alternately; through the radial stress balance design of the oil distribution shaft 3, the bending deformation of the oil distribution shaft 3 is greatly improved, and the abrasion of the rotor 5 and the oil distribution shaft 3 is reduced, so that the radial plunger pump can reach a very high pressure level, and can realize functions of unidirectional quantification, unidirectional variable, bidirectional quantification, bidirectional variable and the like.

Although the present invention has been described with reference to the preferred embodiments, it is not intended to be limited thereto. Those skilled in the art can make numerous possible variations and modifications to the present invention, or modify equivalent embodiments to equivalent variations, without departing from the scope of the invention, using the teachings disclosed above. Therefore, any simple modification, equivalent change and modification made to the above embodiments according to the technical spirit of the present invention should fall within the protection scope of the technical scheme of the present invention, unless the technical spirit of the present invention departs from the content of the technical scheme of the present invention.