Plunger axis self-adaptive swing type radial plunger pump

Abstract

The invention relates to the technical field of plunger pumps, in particular to a plunger axis self-adaptive swing type radial plunger pump which comprises a pump body, a driving shaft rotating around an axis is arranged in the pump body, a front end cover is arranged at the front end of the pump body, a first rear end cover is arranged at the rear end of the pump body, and an eccentric shaft is arranged on the driving shaft. A plurality of plunger assemblies are evenly distributed in the circumferential direction of the axis of the eccentric shaft, each plunger assembly comprises an outer plunger sleeve and an inner plunger sleeve, plunger containing cavities are formed in the outer plunger sleeves and the inner plunger sleeves, the eccentric shaft is sleeved with a driving ring, the ends of the outer plunger sleeves are connected with a pump body ball pair, and the inner plunger sleeves are connected with a driving ring ball pair. The plunger assembly is further provided with a reset device in a matched mode, the outer plunger sleeve is tightly attached to the plunger upper cover under the action of the reset device and the pressure of oil in the plunger cavity, and the inner plunger sleeve is tightly attached to the driving ring. A flow channel communicated with the plunger cavity is formed in the pump body, a flow distribution component is arranged in the pump body in a matched mode, the driving shaft rotates, the plunger assembly reciprocates, the volume of the plunger cavity changes periodically, and oil suction and oil discharge are achieved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of plunger pumps, in particular to a plunger axis self-adaptive swing type radial plunger pump. BACKGROUND

[0002] The plunger pump has the advantages of compactness, high efficiency, high power density ratio, etc., and is widely used in the fields of aviation, ship, industry, etc. With the rising trends of electrification, compactness, energy saving, etc. of mechanical equipment, the performance of the plunger pump is required to be further developed towards wide speed, high pressure and high efficiency.

[0003] The currently applied plunger pump has the following problems: there is a large lateral force at the plunger pair, the lateral force increases with the increase of pressure, which causes friction and wear of the plunger; there is a large relative sliding speed at the friction pair between the plunger and the pump body or the plunger and the driving shaft, which easily causes friction and wear at high speed; during the operation of the two plungers, in addition to the axial reciprocating motion, there is a large rotational inertia due to the rotation of the driving shaft, which causes large start-stop impact and poor dynamic performance, etc. The above problems reduce the service life, maximum pressure, maximum speed and other performances of the plunger pump, and reduce its working efficiency. SUMMARY

[0004] In order to overcome the shortcomings and deficiencies in the prior art, the purpose of the present application is to provide a plunger axis self-adaptive swing type radial plunger pump to reduce the lateral force of the plunger, reduce friction and wear, improve the use performance of the pump and improve the working efficiency.

[0005] The technical scheme adopted by the present application is: A plunger axis self-adaptive swing type radial plunger pump, comprising a pump body, a front end cover and a rear end cover arranged on the pump body, a driving shaft arranged in the pump body, an eccentric section arranged on the driving shaft, a plurality of plunger assemblies arranged circumferentially on the eccentric section, the plunger assembly comprising an outer plunger sleeve and an inner plunger sleeve, the outer plunger sleeve and the inner plunger sleeve being mutually sleeved to form a plunger cavity inside, a driving ring being sleeved on the eccentric section, the driving ring being connected with the inner plunger sleeve through a ball pair, and the end of the outer plunger sleeve being connected with the pump body through a ball pair; a sliding transition piece is arranged between the driving ring and the eccentric section; the plunger assembly is further matched with a reset device, and the outer plunger sleeve is tightly attached to the pump body and the inner plunger sleeve is tightly attached to the driving ring under the action of the reset device and the oil pressure in the plunger cavity.

[0006] The driving ring is connected with the inner plunger sleeve through a ball pair, and the end of the outer plunger sleeve is connected with the pump body through a ball pair, and the ball pair connection is a convex spherical surface and a concave spherical surface constraint connection.

[0007] The convex spherical surface is a ball head structure, the end of the outer plunger sleeve and the end of the inner plunger sleeve are provided with a ball head structure, the pump body and the driving ring are provided with a matching concave spherical surface, and the ball head is arranged in the concave spherical surface in abutment.

[0008] The spring force of the spring makes the outer plunger sleeve and the inner plunger sleeve always adhere to the matched spherical pair.

[0009] The spherical head structure arranged at the end of the outer plunger sleeve and the end of the inner plunger sleeve is matched with the mechanical reset device. The mechanical reset device includes an outer plunger mechanical reset component and an inner plunger mechanical reset component. The outer plunger mechanical reset component is arranged at the connecting position of the outer plunger sleeve and the pump body spherical pair, and the inner plunger mechanical reset component is arranged at the connecting position of the inner plunger sleeve and the driving ring spherical pair. The outer plunger mechanical reset component includes a plunger stop ring and an elastic stop ring. The plunger stop ring is arranged on the spherical head at the end of the outer plunger sleeve and abuts against the concave spherical surface arranged on the pump body. The plunger stop ring is arranged on the driving ring. The plunger hoop is provided with a through clamping groove. The position of the clamping groove corresponds to the concave spherical surface arranged on the driving ring. The clamping groove limits the spherical head arranged at the end of the inner plunger sleeve to be clamped in the concave spherical surface arranged on the driving ring.

[0010] The inner ring of the plunger stop ring is provided with a spherical surface. The spherical surface of the inner ring of the plunger stop ring is combined with the concave spherical surface arranged on the pump body. The inner wall of the clamping groove is provided with a spherical surface. The spherical surface of the inner wall of the clamping groove is combined with the concave spherical surface arranged on the driving ring.

[0011] The driving ring end face is provided with a limiting pin. The extending part of the limiting pin faces the front end cover. The front end cover is machined with an inner cylindrical hole. The position of the inner cylindrical hole is matched with the limiting pin.

[0012] The sliding transition piece is a structural piece in the form of low-friction rolling such as a sliding bearing and a needle bearing, or a structural piece in the form of low-friction sliding such as PEEK and diamond.

[0013] The pump body includes a shell and a cover plate assembly. The shell and the cover plate assembly can be an integrally cast piece or a combined piece.

[0014] The housing is provided with a concentric disc flow distribution component, the housing, the cover plate assembly, the concentric disc flow distribution component are provided with oil channels communicating with the plunger assembly, the cover plate assembly is a second cover plate assembly, the plunger assembly is a second plunger assembly, the second plunger assembly comprises a second outer plunger sleeve, the bottom end surface of the second cover plate assembly is connected with the ball pair of the second outer plunger sleeve, the lateral sides of the second cover plate assembly are respectively provided with a third flow distribution valve oil channel and a fourth flow distribution valve oil channel, the third flow distribution valve oil channel and the fourth flow distribution valve oil channel are provided with a communicating oil channel, a fifth oil channel, the sixth oil channel is provided through the plunger inner cavity on the central axis of the spherical surface end surface of the second outer plunger sleeve, the central axis of the sixth oil channel is coaxially arranged with the inner cavity central axis of the second outer plunger sleeve, the seventh oil channel is provided on the bottom spherical surface end surface of the second cover plate assembly, the seventh oil channel is communicated with the fifth oil channel, the seventh oil channel is coaxially arranged with the sixth oil channel, the thirteenth oil channel is provided on one side of the second cover plate assembly, the thirteenth oil channel is communicated with the fourth flow distribution valve oil channel, the housing is provided with a twenty-seventh oil channel and a twenty-eighth oil channel, the twenty-seventh oil channel and the twenty-eighth oil channel are communicated, the twenty-seventh oil channel is communicated with the thirteenth oil channel, the concentric disc flow distribution component comprises a first flow distribution disc, a first compensation disc and a first spring, the first flow distribution disc, the first compensation disc and the first spring are arranged in the rear end cover, the rear end cover is a second rear end cover, the central part of the second rear end cover is provided with a twenty-third oil channel, the inner cavity is provided with three groups of cylindrical hole grooves, i.e., a third cylindrical hole groove, a fourth cylindrical hole groove and a fifth cylindrical hole groove, the third cylindrical hole groove is arranged at the bottom, the fourth cylindrical hole groove is arranged above the third cylindrical hole groove, the fifth cylindrical hole groove is arranged above the fourth cylindrical hole groove, the diameter of the third cylindrical hole groove is smaller than that of the fourth cylindrical hole groove, the diameter of the fourth cylindrical hole groove is smaller than that of the fifth cylindrical hole groove, the third cylindrical hole groove, the fourth cylindrical hole groove and the fifth cylindrical hole groove are arranged in a stepped manner, the twenty-fourth oil channel is arranged on the second rear end cover and extends along the radial direction of the second rear end cover and penetrates the hole wall of the fourth cylindrical hole groove and the fifth cylindrical hole groove, the first compensation disc is a flange type structure comprising a flange disc and a cylindrical shaft, the twenty-first oil channel is provided through the center of the first compensation disc, the twenty-first oil channel is communicated with the twenty-third oil channel, the cylindrical shaft of the first compensation disc is arranged in the third cylindrical hole groove, the flange disc of the first compensation disc is arranged in the fourth cylindrical hole groove, the first flow distribution disc is arranged in the fifth cylindrical hole groove, the first flow distribution disc is fixedly arranged on the driving shaft, the two end surfaces of the first flow distribution disc are respectively abutted with the first compensation disc and the end surface of the housing, the first spring is arranged between the bottom end surface of the fourth cylindrical hole groove and the end surface of the flange disc of the first compensation disc, the one end surface of the first flow distribution disc is provided with arc grooves, i.e., a first arc groove and a second arc groove, the other end surface of the first flow distribution disc is provided with a first cylindrical hole groove, a plurality of nineteenth oil channels are radially arranged in the first arc groove, the nineteenth oil channels penetrate the shaft hole and the first cylindrical hole groove in the direction of the central axis, a plurality of twentieth oil channels are radially arranged in the second arc groove, the twentieth oil channels penetrate the outer circular wall of the first flow distribution disc, the end surface of the first cylindrical hole groove of the first flow distribution disc is abutted with the end surface of the first compensation disc, the diameter of the first flow distribution disc is smaller than that of the fifth cylindrical hole groove,The outer wall of the first flow distribution disc and the inner wall of the fifth cylindrical hole groove form a first cavity, the first flow distribution disc is arranged in abutment with the first compensation disc end face, the first cylindrical hole groove forms a second cavity, the second cavity is in communication with the nineteenth oil channel and the twenty-first oil channel respectively, the twenty-eighth oil channel is periodically in communication with the first arc-shaped groove and the second arc-shaped groove with the rotation of the first flow distribution disc, hydraulic oil enters the plunger cavity in the pump through external pipelines, and the path is: external pipeline 23rd oil channel 21st oil channel 2nd cavity 19th oil channel first arc-shaped groove 28th oil channel 27th oil channel 13th oil channel fourth flow valve oil channel fifth oil channel seventh oil channel sixth oil channel plunger cavity, and the hydraulic oil in the plunger cavity is discharged to the external pipeline, and the path is: plunger cavity sixth oil channel seventh oil channel fifth oil channel fourth flow valve oil channel 13th oil channel 27th oil channel 28th oil channel second arc-shaped groove 20th oil channel first cavity 24th oil channel external pipeline.

[0015] The beneficial effects of the present application are: The present application discloses a plunger axis self-adaptive swing type radial plunger pump, which comprises a pump body and a driving shaft, wherein an eccentric shaft is arranged on the driving shaft, a plurality of plunger assemblies are uniformly arranged on the circumference of the eccentric shaft, a driving ring is sleeved on the eccentric shaft, the plunger assemblies are connected with the pump body and the driving ring through ball pairs, the plunger assemblies only swing around the small-angle center of the spherical surface of the upper cover, the ball pairs are used for realizing the axis self-adaptive swing, the lateral force of the plunger is reduced, the friction between the plunger and the pump body or the plunger and the driving shaft is reduced, the relative sliding speed is reduced, the rotational inertia of the plunger pump is reduced, meanwhile, a reset device is matched on the plunger assembly, a friction torque constraint assembly and a limiting constraint assembly are matched between the eccentric shaft and the driving ring, the friction between the plunger and the pump body or the plunger and the driving shaft is further reduced, the performance parameters of the pump are improved, and the working efficiency is improved. BRIEF DESCRIPTION OF DRAWINGS

[0016] In order to make the above-mentioned purpose, characteristics and advantages of the present application more obvious and easy to understand, the following preferred embodiments are described in detail below, and the accompanying drawings are used for reference, but the embodiments in the drawings do not constitute any limitation on the present application, and other drawings can be obtained by those skilled in the art without creative labor.

[0017] Figure 1 It is a whole structure schematic view; Figure 2 It is a whole structure schematic view of embodiment one; Figure 3 It is a whole structure schematic view of embodiment two; Figure 4 It is a first plunger assembly structure schematic view; Figure 5 It is a mechanical reset device structure schematic view; Figure 6 is a schematic view of a position-limiting component structure; Figure 7 is a schematic view of a first convex spherical surface section; Figure 8 is a schematic view of a first ball head section; Figure 9 is a schematic view of a third concave spherical surface section; Figure 10 is a schematic view of a structure of an oil suction state of a flow distribution disc; Figure 11 is a schematic view of a structure of an oil discharge state of a flow distribution disc; Figure 12 is a schematic view of a component installation of a flow distribution disc; Figure 13 is a schematic view of a first flow distribution disc structure; Figure 14 is a schematic view of a first flow distribution disc section structure; Figure 15 is a schematic view of a structure of an oil suction state of an eccentric disc; Figure 16 is a schematic view of a structure of an oil discharge state of an eccentric disc; Figure 17 is a schematic view of a component installation of a flow distribution disc; Figure 18 is a schematic view of a second flow distribution disc structure; Figure 19 is a schematic view of a second flow distribution disc section structure.

[0018] In the figure: 1 - housing, 101 - ninth oil channel, 102 - tenth oil channel, 103 - twenty-seventh oil channel, 104 - twenty-eighth oil channel, 2 - drive shaft, 201 - eccentric section, 202 - seventeenth oil channel, 203 - eighteenth oil channel, 3 - first drive ring, 301 - second convex spherical surface, 4 - second drive ring, 401 - fourth concave spherical surface, 5 - first plunger assembly, 501 - first outer plunger sleeve, 5013 - first concave spherical surface, 502 - first inner plunger sleeve, 5023 - second concave spherical surface, 6 - second plunger assembly, 601 - second outer plunger sleeve, 6011 - sixth oil channel, 6013 - first ball head, 602 - second inner plunger sleeve, 6023 - second ball head, 7 - spring return device, 701 - spring, 8 - mechanical return device, 801 - plunger stop ring, 802 - elastic stop ring, 803 - plunger hoop, 8031 - clamping groove, 9 - limit pin, 11 - front end cover, 1101 - inner cylindrical hole, 12 - first rear end cover, 1201 - fifteenth oil channel, 1202 - sixteenth oil channel, 13 - flow distribution valve, 14 - first cover plate assembly, 1401 - first convex spherical surface, 15 - second cover plate assembly, 1501 - third flow distribution valve oil channel, 1502 - fourth flow distribution valve oil channel, 1503 - fifth oil channel, 1504 - seventh oil channel, 1505 - third concave spherical surface, 1506 - thirteenth oil channel, 1507 - fourteenth oil channel, 16 - sliding transition piece, 17 - first flow distribution disc, 1701 - first arc-shaped groove, 1702 - nineteenth oil channel, 1703 - second arc-shaped groove, 1704 - twentieth oil channel, 1705 - first cylindrical hole groove, 18 - first compensation disc, 1801 - twenty-first oil channel, 19 - first spring, 20 - eccentric shaft sleeve, 21 - second flow distribution disc, 2101 - first annular groove, 2102 - twenty-second oil channel, 2103 - second annular groove, 2104 - second cylindrical hole groove, 22 - second compensation disc, 2201 - twenty-seventh oil channel, 23 - second spring, 24 - second rear end cover, 2401 - twenty-third oil channel, 2402 - twenty-fourth oil channel, 2403 - third cylindrical hole groove, 2404 - fourth cylindrical hole groove, 2405 - fifth cylindrical hole groove, 25 - third rear end cover, 2501 - twenty-fifth oil channel, 2502 - twenty-sixth oil channel, 2503 - sixth cylindrical hole groove, 2504 - seventh cylindrical hole groove, 2505 - eighth cylindrical hole groove, 26 - first cavity, 27 - second cavity, 28 - third cavity, 29 - fourth cavity. DETAILED DESCRIPTION

[0019] In order to make the purpose, technical scheme and advantages of the embodiments of the present application more clear, the technical scheme of the embodiments of the present application will be described clearly and completely below with reference to the drawings in the embodiments of the present application.

[0020] It needs to be explained that the structure, proportion, size and the like shown in the drawings attached to the present specification are only used to cooperate with the content disclosed in the specification, so as to be understood and read by those skilled in the art, and do not have technical substantial significance, and any modification of structure, change of proportion relationship or adjustment of size, without affecting the effect and purpose that can be achieved by the present application, should still fall within the scope covered by the disclosed technical content of the present application.

[0021] As shown in Figure 1 , a plunger axis self-adapting swing type radial plunger pump comprises a pump body, a driving shaft 2, the pump body is provided with the driving shaft 2 rotating around an axis, the driving shaft 2 is provided with an eccentric section 201, a plurality of plunger assemblies are arranged in the cavity of the pump body along the axis of the driving shaft 2, the plunger assemblies are matched and arranged around the eccentric section 201, the plunger assemblies comprise an outer plunger sleeve and an inner plunger sleeve, the outer plunger sleeve and the inner plunger sleeve are sleeved with each other, an inner plunger cavity is formed, the end of the outer plunger sleeve is connected with a spherical pair of the pump body, the end of the inner plunger sleeve is matched and arranged with a driving ring, the end of the inner plunger sleeve is connected with a spherical pair of the driving ring, and the driving ring is arranged on the eccentric section 201. The plunger assemblies will reciprocate with the rotation of the eccentric section 201. The plunger assemblies are also matched and arranged with a reset device, and the ends of the outer plunger sleeve and the inner plunger sleeve are tightly attached to the pump body and the driving ring under the action of the reset device and the oil pressure in the plunger cavity. The pump body is provided with a front end cover 11 and a rear end cover, and the pump body, the plunger assemblies, the front end cover 11 and the rear end cover are provided with matched oil passage channels, and the pump body is provided with a flow distribution component, through which the hydraulic oil passes through each oil passage channel to realize the oil suction and discharge action of the plunger assemblies during reciprocation. The number of plunger assemblies is set according to the application scene and required performance parameters.

[0022] The outer plunger sleeve is connected with a spherical pair of the pump body, and the inner plunger sleeve is connected with a spherical pair of the driving ring, and the spherical pair connection can have different types of combinations: one, the outer plunger sleeve and the inner plunger sleeve are concave spherical surfaces, and the pump body and the driving ring are provided with convex spherical surfaces matched therewith; two, the outer plunger sleeve and the inner plunger sleeve are convex spherical surfaces, and the pump body and the driving ring are provided with concave spherical surfaces matched therewith; three, the outer plunger sleeve is a concave spherical surface, the pump body is provided with a convex spherical surface matched therewith, the inner plunger sleeve is a convex spherical surface, and the driving ring is provided with a concave spherical surface matched therewith; four, the outer plunger sleeve is a convex spherical surface, the pump body is provided with a concave spherical surface matched therewith, the inner plunger sleeve is a concave spherical surface, and the driving ring is provided with a convex spherical surface matched therewith.

[0023] The outer plunger sleeve is connected with a spherical pair of the pump body, and the inner plunger sleeve is connected with a spherical pair of the driving ring, and the convex spherical surface and the concave spherical surface can be arranged as shown in Figure 7 , and the cross section of the convex spherical surface is as shown in Figure 7 .As shown, OA, OB, and OC are represented as the radius of the sphere, OA, OB, and OC are on the same cross section, and the angles ∠AOB and ∠AOC are equal, and the length of BC is less than the diameter of the sphere, and the arc BAC forms a convex spherical surface around the spherical axis, and the concave spherical surface is matched with the convex spherical surface.

[0024] The outer plunger sleeve is connected with the pump body spherical pair, and the inner plunger sleeve is connected with the driving ring spherical pair, and the convex spherical surface in the spherical pair connection can be specifically embodied as a ball head. The ball head setting can refer to, for example, Figure 8 As shown, the ball head cross section is as shown in Figure 8 As shown, the ball head is formed by the arc MF around the center axis, and the length of FE is greater than the radius of the sphere and less than the diameter of the sphere. The concave spherical surface matched with the ball head is matched with the ball head, and the concave spherical surface cross section can refer to, for example, Figure 9 As shown, the concave spherical surface is formed by the arc M'F' around the center axis, and the length of F'E' is less than or equal to the radius of the sphere.

[0025] In the following, two specific embodiments of the pump body and the driving ring are set as convex spherical surface and concave spherical surface respectively, and the detailed structure is described.

[0026] The pump body includes a housing 1 and a cover plate assembly, and the pump body can be an integral casting of the housing 1 and the cover plate assembly, or a combination of the housing 1 and the cover plate assembly.

[0027] As shown in Embodiment One, Figure 2 The pump body and the driving ring are set as convex spherical surface, and the outer plunger sleeve and the inner plunger sleeve are set as concave spherical surface; the plunger assembly is a first plunger assembly 5, the first plunger assembly 5 includes a first outer plunger sleeve 501, a first inner plunger sleeve 502, and a first cover plate assembly 14 matched with the first outer plunger sleeve 501, and a first driving ring 3 matched with the first inner plunger sleeve 502.

[0028] As shown in Figure 2 , Figure 4 The first outer plunger sleeve 501 is provided with a first concave spherical surface 5013 at the end, the first cover plate assembly 14 is matched with the first convex spherical surface 1401 at the abutting end of the first outer plunger sleeve 501, the first inner plunger sleeve 502 is provided with a second concave spherical surface 5023 at the end, and the first driving ring 3 is matched with the second convex spherical surface 301 at the abutting area of the end of the first inner plunger sleeve 502. The cross sections of the first concave spherical surface 5013, the first convex spherical surface 1401, the second concave spherical surface 5023, and the second convex spherical surface 301 refer to the structure as shown in Figure 7

[0029] As shown in Figure 3 ​The second embodiment is shown. The pump body and the driving ring are provided with concave spherical surfaces, and the outer plunger sleeve and the inner plunger sleeve are provided with convex spherical surfaces, and the outer plunger sleeve and the inner plunger sleeve are provided with ball head structures. The plunger assembly is a second plunger assembly 6. The second plunger assembly 6 includes a second outer plunger sleeve 601, a second inner plunger sleeve 602, a second cover plate assembly 15 matched with the second outer plunger sleeve 601, and a second driving ring 4 matched with the second inner plunger sleeve 602.

[0030] As shown in Figure 3 , Figure 5 , the first ball head 6013 is arranged at the end of the second outer plunger sleeve 601, the third concave spherical surface 1505 is arranged at the second cover plate assembly 15 matched with the first ball head 6013, the first ball head 6013 is arranged in the third concave spherical surface 1505, the second ball head 6023 is arranged at the end of the second inner plunger sleeve 602, the fourth concave spherical surface 401 is arranged at the second driving ring 4 matched with the second ball head 6023, and the second ball head 6023 is arranged in the fourth concave spherical surface 401. The cross sections of the first ball head 6013, the third concave spherical surface 1505, the second ball head 6023, and the fourth concave spherical surface 401 are arranged as shown in Figure 8 , Figure 9 .

[0031] The plunger assembly reciprocates with the rotation of the eccentric section 201. The outer plunger sleeve and the inner plunger sleeve are matched with reset devices. Under the action of the reset devices and the oil pressure in the plunger cavity, the two plungers are tightly attached to the pump body and the driving ring.

[0032] The reset device is a spring reset device 7. As shown in Figure 2 , the spring reset device 7 includes a spring 701 arranged in the plunger cavity formed by the outer plunger sleeve and the inner plunger sleeve. The volume of the plunger cavity increases and decreases with the rotation of the eccentric section 201. When the volume of the plunger cavity decreases, the spring 701 is compressed. When the volume of the plunger cavity increases, the spring 701 is stretched. The spring force makes the outer plunger sleeve and the inner plunger sleeve always fit the matched spherical pair.

[0033] In the structure with a ball head arranged in the spherical pair connection, the reset device can also be provided with a mechanical reset device 8. The mechanical reset device 8 clamps the ball head in the concave spherical surface matched with the ball head. The mechanical reset device 8 includes an outer plunger mechanical reset component and an inner plunger mechanical reset component. The outer plunger mechanical reset component is matched and arranged on the ball head structure in the spherical pair connection between the outer plunger sleeve and the pump body. The inner plunger mechanical reset component is matched and arranged on the ball head structure in the spherical pair connection between the inner plunger sleeve and the driving ring.

[0034] As shown in Figure 3 , 5As shown, the outer plunger mechanical reset component includes a plunger stop ring 801 and an elastic stop ring 802. The plunger stop ring 801 is sleeved on the first ball head 6013 and abuts against the end surface of the third concave spherical surface 1505. The inner ring of the plunger stop ring 801 is provided with a spherical surface which is matched with the third concave spherical surface 1505. The third concave spherical surface 1505 and the spherical surface provided on the inner ring of the plunger stop ring 801 are combined to form a spherical surface which is matched with the first ball head 6013. The first ball head 6013 is arranged in the third concave spherical surface 1505. The spherical surface of the plunger stop ring 801 limits the first ball head 6013 to be clamped in the third concave spherical surface 1505. The elastic stop ring 802 is pressed on the plunger stop ring 801 to press the plunger stop ring 801 on the second cover plate assembly 15.

[0035] As shown in the figures, Figure 3 , 5 As shown, the inner plunger mechanical reset component includes a plunger hoop 803. A plurality of first concave spherical surfaces 401 are arranged on the outer ring of the second driving ring 4. The second ball head 6023 is arranged in the first concave spherical surface 401. The plunger hoop 803 is sleeved on the second driving ring 4. A plurality of clamping grooves 8031 are arranged on the plunger hoop 803. The positions of the clamping grooves 8031 correspond to the first concave spherical surfaces 401 one by one. The inner walls of the clamping grooves 8031 are provided with spherical surfaces at positions corresponding to the first concave spherical surfaces 401. The spherical surfaces are matched with the first concave spherical surfaces 401. The first concave spherical surfaces 401 and the spherical surfaces provided on the inner walls of the clamping grooves 8031 are combined to form a spherical surface which is matched with the second ball head 6023. The second ball head 6023 is sleeved in the first concave spherical surface 401. The clamping grooves 8031 of the plunger hoop 803 clamp the second ball head 6023. The spherical surfaces arranged in the clamping grooves 8031 limit the second ball head 6023 to be clamped in the first concave spherical surface 401. In this embodiment, the plunger hoop 803 is sleeved on the second driving ring 4 from one side. The plunger hoop 803 can also be provided in a two-piece structure and be sleeved on the second driving ring 4 from both sides.

[0036] The mechanical reset device 8 can be applied alone and can also be matched with the spring reset device 7.

[0037] When the driving shaft 2 rotates, the eccentric section 201 drives the driving ring to revolve around the axis of the driving shaft 2. Due to the constraint of the ball pair, the driving ring does not rotate or the rotation angle and rotation speed are very small. In order to reduce the wear between the driving ring and the eccentric section 201, further reduce the lateral force at the plunger pair, improve the constraint performance of the ball pair, a friction torque constraint assembly and a limiting constraint assembly can also be matched and arranged between the eccentric section 201 and the driving ring.

[0038] Friction torque constraint assembly: the friction torque applied by the plurality of inner plungers on the driving ring is greater than the friction torque applied by the eccentric section 201 on the driving ring through the design of the material and surface roughness.

[0039] AsFigure 9 , Figure 10 As shown, a friction torque constraint assembly is provided between the drive ring and the eccentric section 201. The friction torque constraint assembly includes a sliding transition piece 16, which is fixedly installed on the eccentric section 201. The drive ring is set on the sliding transition piece 16, which transforms the frictional force between the eccentric section 201 and the drive ring into the frictional force between the sliding transition piece 16 and the drive ring. The sliding transition piece 16 can be a low-friction rolling structure such as a sliding bearing or a needle roller bearing; the sliding transition piece 16 can also be a wear-resistant and low-friction sliding structure such as PEEK or diamond, which greatly reduces the frictional force applied to the drive ring by the eccentric section 201. Through the action of the sliding transition piece 16, the drive ring drives the drive shaft 2 to revolve around the axis of the drive shaft 2 during rotation, while it does not rotate on its own axis or its rotation angle and angular velocity are very small.

[0040] like Figure 12 As shown, a limit constraint assembly is matched and installed on the drive ring. The limit constraint assembly includes a limit pin 9, which is fixedly installed on the end face of the drive ring or plunger collar 803. The protruding part of the limit pin 9 faces the front end cover 11. The front end cover 11 has an inner cylindrical hole 1101 machined on it. The limit pin 9 restricts movement within the inner cylindrical hole 1101, thereby limiting the rotation angle and angular velocity of the drive ring. One or more limit pins 9 can be provided.

[0041] The housing 1 is also equipped with a flow distribution component. The housing 1 is machined with flow channels that connect the plunger cavity and the low-pressure oil zone and the high-pressure oil zone. Oil control valves are installed on the flow channels respectively to connect the low-pressure oil zone and the high-pressure oil zone. When the drive shaft 2 rotates and the drive ring revolves, the plunger assembly reciprocates along it, and the volume of the plunger cavity changes periodically to achieve flow distribution. Under the action of the flow distribution component, oil suction and oil discharge are formed.

[0042] This embodiment provides the following flow distribution method to realize the pump's oil suction and discharge functions.

[0043] I. Flow distribution via distribution valve: like Figure 2 , 3 In the embodiment shown, the flow distribution method is flow distribution via a flow distribution valve. The following will refer to... Figure 3 The following is a description of the flow distribution using a flow distribution valve as an example.

[0044] like Figure 3 As shown, the flow distribution device includes a flow distribution valve 13, which is installed on the pump body. The flow distribution valve 13 is a one-way flow distribution valve used to control the flow direction of hydraulic oil. It connects the plunger cavity and the flow channels of the low-pressure oil zone and the high-pressure oil zone through the oil passage matched on the rear end cover of the pump body to achieve flow distribution.

[0045] like Figure 3 , Figure 5As shown, the second cover plate assembly 15 is a T-shaped member fixedly arranged on the housing 1, the bottom end surface of the second cover plate assembly 15 is connected with the spherical pair of the second outer plunger sleeve 601, the lateral sides of the second cover plate assembly 15 are respectively provided with a third distribution valve oil channel 1501 and a fourth distribution valve oil channel 1502, a communicating oil channel fifth oil channel 1503 is arranged between the third distribution valve oil channel 1501 and the fourth distribution valve oil channel 1502, a sixth oil channel 6011 is arranged through the plunger inner cavity on the central axis of the spherical end surface of the second outer plunger sleeve 601, the central axis of the sixth oil channel 6011 is coaxially arranged with the central axis of the inner cavity of the second outer plunger sleeve 601, a seventh oil channel 1504 is arranged on the bottom spherical end surface of the second cover plate assembly 15, the seventh oil channel 1504 communicates with the fifth oil channel 1503, and the seventh oil channel 1504 is coaxially arranged with the sixth oil channel 6011. An eighth oil channel 6021 is arranged through the plunger inner cavity on the central axis of the spherical end surface of the second inner plunger sleeve 602, and the central axis of the eighth oil channel 6021 is coaxially arranged with the central axis of the inner cavity of the second inner plunger sleeve 602.

[0046] As shown in Figure 3 , Figure 5 shown, the two sides of the second cover plate assembly 15 are also provided with a thirteenth oil channel 1506 and a fourteenth oil channel 1507, the thirteenth oil channel 1506 communicates with the fourth distribution valve oil channel 1502, and the fourteenth oil channel 1507 communicates with the third distribution valve oil channel 1501.

[0047] As shown in Figure 3 , the rear end cover arranged on the rear side of the housing 1 is a first rear end cover 12, the first rear end cover 12 is provided with a fifteenth oil channel 1201 and a sixteenth oil channel 1202, the housing 1 is provided with a ninth oil channel 101 and a tenth oil channel 102, one end of the ninth oil channel 101 communicates with the fourteenth oil channel 1507, and one end of the ninth oil channel 101 communicates with the oil cavity inside the housing 1, one end of the tenth oil channel 102 communicates with the thirteenth oil channel 1506, and one end of the tenth oil channel 102 communicates with the fifteenth oil channel 1201; the tail end surface of the drive shaft 2 is provided with a seventeenth oil channel 202 along the axis, a plurality of eighteenth oil channels 203 are circumferentially arranged at the end of the seventeenth oil channel 202, the eighteenth oil channels 203 communicate with the seventeenth oil channel 202, the seventeenth oil channel 202 communicates with the oil cavity inside the housing 1, the sixteenth oil channel 1202 communicates with the oil cavity inside the housing 1, and the seventeenth oil channel 202 and the sixteenth oil channel 1202 are correspondingly arranged.

[0048] As shown in Figure 3As shown, the flow distribution valve 13 is located at the end of the inner bore of the third flow distribution valve oil passage 1501 and the fourth flow distribution valve oil passage 1502. In this embodiment, the flow distribution valve 13 controls the flow direction of the oil from the third flow distribution valve oil passage 1501 to the fourth flow distribution valve oil passage 1502. In this embodiment, the fifteenth oil passage 1201 is the oil outlet, and the port of the fifteenth oil passage 1201 is connected to the external oil pipeline. The sixteenth oil passage 1202 is the oil inlet, and the port of the sixteenth oil passage 1202 is connected to the external oil pipeline. It is used to draw oil from the external oil tank into the pump. When the drive shaft 2 rotates, the eccentric section 201 rotates, and the drive ring revolves, the plunger assembly reciprocates along it, and the volume of the plunger cavity changes periodically, realizing flow distribution. Under the action of the flow distribution component, oil suction and oil discharge are formed.

[0049] Its oil suction path is as follows: external pipeline hydraulic pressure → sixteenth oil passage 1202 → seventeenth oil passage 202 → eighteenth oil passage 203 → internal oil cavity of housing 1 → ninth oil passage 101 → fourteenth oil passage 1507 → third distribution valve oil passage 1501 → distribution valve 13 → fifth oil passage 1503 → seventh oil passage 1504 → sixth oil passage 6011 → plunger cavity. Its oil discharge path is as follows: plunger cavity → sixth oil passage 6011 → seventh oil passage 1504 → fifth oil passage 1503 → distribution valve 13 → fourth distribution valve oil passage 1502 → thirteenth oil passage 1506 → tenth oil passage 102 → fifteenth oil passage 1201 → external oil pipeline.

[0050] This cycle repeats to complete the pump's oil suction and discharge operations.

[0051] II. Distribution plate distribution includes concentric plate distribution and eccentric plate distribution. Concentric plate distribution means that the distribution plate and the drive shaft are set concentrically, while eccentric plate distribution means that the distribution plate and the drive shaft are set eccentrically.

[0052] Concentric disk distribution: like Figure 10~12 As shown, the components of the concentric disk distribution include a first distribution disk 17, a first compensation disk 18, and a first spring 19. The first distribution disk 17, the first compensation disk 18, and the first spring 19 are disposed inside the rear end cover, which is the second rear end cover 24.

[0053] like Figure 11As shown, the second rear end cover 24 is provided with a second twenty-third oil passage 2401 in the center, and the inner cavity is provided with three groups of cylindrical hole grooves: a third cylindrical hole groove 2403, a fourth cylindrical hole groove 2404, and a fifth cylindrical hole groove 2405. The third cylindrical hole groove 2403 is provided with a bottom, the fourth cylindrical hole groove 2404 is arranged above the third cylindrical hole groove 2403, and the fifth cylindrical hole groove 2405 is arranged above the fourth cylindrical hole groove 2404. The diameter of the third cylindrical hole groove 2403 is smaller than that of the fourth cylindrical hole groove 2404, and the diameter of the fourth cylindrical hole groove 2404 is smaller than that of the fifth cylindrical hole groove 2405. The third cylindrical hole groove 2403, the fourth cylindrical hole groove 2404, and the fifth cylindrical hole groove 2405 are arranged in a stepped manner. The second rear end cover 24 is further provided with a second twenty-fourth oil passage 2402, which is arranged radially along the second rear end cover 24 and penetrates the wall of the fourth cylindrical hole groove 2404 and the fifth cylindrical hole groove 2405.

[0054] As shown in Figure 11 , the first compensation disc 18 is a flange type structure including a flange disc and a cylindrical shaft. The first compensation disc 18 is provided with a twenty-first oil passage 1801 in the center, and the twenty-first oil passage 1801 is in communication with the twenty-third oil passage 2401. The cylindrical shaft of the first compensation disc 18 is arranged in the third cylindrical hole groove 2403, and the flange disc of the first compensation disc 18 is arranged in the fourth cylindrical hole groove 2404.

[0055] As shown in Figure 11 , the first compensation disc 18 is a flange type structure including a flange disc and a cylindrical shaft. The first compensation disc 18 is provided with a twenty-first oil passage 1801 in the center, and the twenty-first oil passage 1801 is in communication with the twenty-third oil passage 2401. The cylindrical shaft of the first compensation disc 18 is arranged in the third cylindrical hole groove 2403, and the flange disc of the first compensation disc 18 is arranged in the fourth cylindrical hole groove 2404.

[0056] As shown in Figure 10 , the fourth cylindrical hole groove 2404 is provided with a first spring 19 between the bottom end face and the end face of the flange disc of the first compensation disc 18. The first spring 19 pushes the first compensation disc 18 and the first compensation disc 18 to abut, so as to balance the pressure generated by the low-pressure oil area and the high-pressure oil area on the first compensation disc 18.

[0057] As shown in Figure 13 , 14As shown, the first distribution disc 17 is provided with a through shaft hole in the center for setting the first distribution disc 17 on the drive shaft 2, and a circular arc groove: a first arc groove 1701 and a second arc groove 1703 is arranged on one end face of the first distribution disc 17, and a first cylindrical hole groove 1705 is arranged on the other end face of the first distribution disc 17, a plurality of nineteenth oil channels 1702 are radially arranged in the first arc groove 1701 and penetrate the through shaft hole and the first cylindrical hole groove 1705 in the direction of the central axis, and a plurality of twentieth oil channels 1704 are radially arranged in the second arc groove 1703 and penetrate the outer circular wall of the first distribution disc 17.

[0058] As shown in the figure, Figure 10 The end face of the first distribution disc 17 provided with the first cylindrical hole groove 1705 abuts against the end face of the first compensation disc 18.

[0059] As shown in the figure, Figure 10 , 11 The diameter of the first distribution disc 17 is smaller than the diameter of the fifth cylindrical hole groove 2405, a first cavity 26 is formed between the outer wall of the first distribution disc 17 and the inner wall of the fifth cylindrical hole groove 2405 for the flow of hydraulic oil, the first distribution disc 17 is arranged in abutment with the end face of the first compensation disc 18, the first cylindrical hole groove 1705 forms a second cavity 27, and the second cavity 27 is in communication with the nineteenth oil channel 1702 and the twenty-first oil channel 1801 respectively.

[0060] As shown in the figure, Figure 10 , Figure 11 The housing 1 is provided with a twenty-seventh oil channel 103 and a twenty-eighth oil channel 104, the twenty-seventh oil channel 103 and the twenty-eighth oil channel 104 are in communication, the twenty-seventh oil channel 103 is in communication with the thirteenth oil channel 1506, and as the first distribution disc 17 rotates, the twenty-eighth oil channel 104 is periodically in communication with the first arc groove 1701 and the second arc groove 1703.

[0061] The first distribution disc 17 rotates periodically with the drive shaft 2, and the flow channels thereon communicate the flow channels of the plunger cavity and the low-pressure oil area and the high-pressure oil area through the oil channel matching on the housing 1, thereby realizing the functions of oil suction and oil discharge.

[0062] As shown in the figure, Figure 10 is a schematic diagram of the oil suction state of the distribution disc distribution mode, at this time, the hydraulic oil enters the pump through the external pipeline and flows into the plunger cavity, and the path is: external pipeline→twenty-third oil channel 2401→twenty-first oil channel 1801→second cavity 27→nineteenth oil channel 1702→first arc groove 1701→twenty-eighth oil channel 104→twenty-seventh oil channel 103→thirteenth oil channel 1506→fourth distribution valve oil channel 1502→fifth oil channel 1503→seventh oil channel 1504→sixth oil channel 6011→plunger cavity.

[0063] As Figure 11 shown, the oil discharge state schematic diagram of the distribution disc distribution mode, at this time, the hydraulic oil in the plunger cavity is discharged to the external pipeline, its path is: plunger cavity→sixth oil channel 6011→seventh oil channel 1504→fifth oil channel 1503→fourth distribution valve oil channel 1502→thirteenth oil channel 1506→twenty-seventh oil channel 103→twenty-eighth oil channel 104→second arc-shaped groove 1703→twentieth oil channel 1704→first cavity 26→twenty-fourth oil channel 2402→external pipeline.

[0064] In this embodiment, the fourth distribution valve oil channel 1502 is not provided with a distribution valve 13.

[0065] The cycle completes the oil suction and discharge operation of the pump.

[0066] Eccentric disc distribution: As Figure 15~17 shown, the eccentric disc distribution includes an eccentric shaft sleeve 20, a second distribution disc 21, a second compensation disc 22, and a second spring 23. The eccentric shaft sleeve 20 is fixedly arranged on the drive shaft 2. The second distribution disc 21 is arranged on the eccentric shaft sleeve 20. The second distribution disc 21, the second compensation disc 22, and the second spring 23 are arranged in the rear end cover, which is a third rear end cover 25.

[0067] A sliding transition piece can also be arranged between the eccentric shaft sleeve 20 and the second distribution disc 21. The sliding transition piece can be a low-friction rolling structure such as a sliding bearing or a needle bearing. The sliding transition piece can also be a low-friction sliding structure such as PEEK or diamond.

[0068] As Figure 16 shown, the third rear end cover 25 is provided with a twenty-fifth oil channel 2501 in the center. The inner cavity is provided with three groups of cylindrical hole grooves: a sixth cylindrical hole groove 2503, a seventh cylindrical hole groove 2504, and an eighth cylindrical hole groove 2505. The sixth cylindrical hole groove 2503 is provided with a bottom. The seventh cylindrical hole groove 2504 is arranged above the sixth cylindrical hole groove 2503. The eighth cylindrical hole groove 2505 is arranged above the seventh cylindrical hole groove 2504. The diameter of the sixth cylindrical hole groove 2503 is smaller than that of the seventh cylindrical hole groove 2504. The diameter of the seventh cylindrical hole groove 2504 is smaller than that of the eighth cylindrical hole groove 2505. The sixth cylindrical hole groove 2503, the seventh cylindrical hole groove 2504, and the eighth cylindrical hole groove 2505 are arranged in a stepped manner. The third rear end cover 25 is also provided with a twenty-sixth oil channel 2502. The twenty-sixth oil channel 2502 is arranged along the radial direction of the third rear end cover 25 and penetrates the hole wall of the seventh cylindrical hole groove 2504 and the eighth cylindrical hole groove 2505.

[0069] As Figure 15As shown, the second compensation plate 22 is a flange-type structure including a flange and a cylindrical shaft. The center of the second compensation plate 22 is provided with a twenty-seventh oil passage 2201, which is connected to the twenty-fifth oil passage 2501. The cylindrical shaft of the second compensation plate 22 is located in the sixth cylindrical hole groove 2503, and the flange of the second compensation plate 22 is located in the seventh cylindrical hole groove 2504.

[0070] like Figure 15 As shown, the second compensation disk 22 is disposed in the eighth cylindrical slot 2505, and the two end faces of the second distribution disk 21 are respectively abutted against the end faces of the second compensation disk 22 and the housing 1.

[0071] like Figure 15 As shown, a second spring 23 is also provided between the bottom end face of the seventh cylindrical slot 2504 and the flange end face of the second compensation plate 22. The second spring 23 pushes the second compensation plate 22 to abut against the second distribution plate 21 to balance the pressure generated by the low-pressure oil zone and the high-pressure oil zone on the second distribution plate 21.

[0072] like Figure 18 , 19 As shown, the second distribution plate 21 has a through shaft hole at its center for mounting the second distribution plate 21 on the eccentric bushing 20. Symmetrical annular grooves are provided on both end faces of the second distribution plate 21: a first annular groove 2101 and a second annular groove 2103. The first annular groove 2101 contains several twenty-second oil passages 2102, which penetrate the first annular groove 2101 and the second annular groove 2103. A second cylindrical hole groove 2104 is also provided on the end face of the second annular groove 2103, penetrating the inner wall of the second annular groove 2103. (The text repeats itself here.) Figure 15 As shown, the end face of the second distribution plate 21 with the second cylindrical slot 2104 abuts against the end face of the second compensation plate 22.

[0073] like Figure 15 , 16 As shown, the diameter of the second distribution plate 21 is smaller than the diameter of the eighth cylindrical groove 2505. A third cavity 28 is formed between the outer wall of the second distribution plate 21 and the inner wall of the eighth cylindrical groove 2505. The third cavity 28 is supplied with hydraulic oil. The end face of the second distribution plate 21 with the second cylindrical groove 2104 abuts against the end face of the second compensation plate 22 to form a fourth cavity 29. The fourth cavity 29 is connected to the second annular groove 2103 and the twenty-seventh oil passage 2201 respectively.

[0074] like Figure 15 , Figure 16As shown, the housing 1 is provided with a 27th oil passage 103 and a 28th oil passage 104, which are connected. The 27th oil passage 103 is connected to the 13th oil passage 1506. The oil passages on the second distribution plate 21 are periodically switched with the eccentric bushing 20. The 28th oil passage 104 is periodically connected to the first annular groove 2101 and the third cavity 28.

[0075] The oil passages of the second distribution plate 21 alternate periodically with the eccentric bushing 20. The flow passages on it connect the plunger cavity and the flow passages of the low-pressure oil zone and the high-pressure oil zone through the oil circuit matched on the housing 1, so as to realize the oil suction and oil discharge functions.

[0076] like Figure 15 The diagram shows the oil suction state of the eccentric disc distribution method. At this time, the hydraulic oil enters the pump through the external pipeline and flows into the plunger cavity. The path is as follows: external pipeline → 25th oil passage 2501 → 27th oil passage 2201 → 4th cavity 29 → 2nd annular groove 2103 → 22nd oil passage 2102 → 1st annular groove 2101 → 28th oil passage 104 → 27th oil passage 103 → 13th oil passage 1506 → 4th distribution valve oil passage 1502 → 5th oil passage 1503 → 7th oil passage 1504 → 6th oil passage 6011 → plunger cavity.

[0077] like Figure 16 The diagram shows the oil discharge state of the eccentric disc distribution method. At this time, the hydraulic oil in the plunger cavity is discharged to the external pipeline. The path is as follows: plunger cavity → sixth oil passage 6011 → seventh oil passage 1504 → fifth oil passage 1503 → fourth distribution valve oil passage 1502 → thirteenth oil passage 1506 → twenty-seventh oil passage 103 → twenty-eighth oil passage 104 → third cavity 28 → twenty-sixth oil passage 2502 → external pipeline.

[0078] This cycle repeats to complete the pump's oil suction and discharge operations.

[0079] In this embodiment, the fourth distribution valve oil passage 1502 is not equipped with a distribution valve 13.

[0080] In the above embodiments, the flow distribution method enables the plunger assembly to reciprocate and perform oil suction and discharge operations when the drive shaft rotates. However, the flow distribution method is not limited to the embodiments mentioned herein, and other flow distribution methods are also within the protection scope of this invention.

Claims

1. A plunger axis self-adapting swing type radial plunger pump, comprising a pump body, a front end cover (11) arranged on the pump body, a rear end cover, a drive shaft (2) arranged in the pump body, an eccentric section (201) arranged on the drive shaft (2), a plurality of plunger assemblies arranged circumferentially on the eccentric section (201), the plunger assembly comprising an outer plunger sleeve and an inner plunger sleeve, the outer plunger sleeve and the inner plunger sleeve being sleeved with each other to form a plunger cavity inside, characterized in that: The eccentric section (201) is sleeved with a driving ring, the driving ring is connected with a ball pair of the inner plunger sleeve, and the end of the outer plunger sleeve is connected with a ball pair of the pump body; ​ A sliding transition piece (16) is arranged between the driving ring and the eccentric section (201); The plunger assembly is further provided with a reset device, and the outer plunger sleeve is tightly attached to the pump body and the inner plunger sleeve is tightly attached to the driving ring under the action of the oil pressure in the plunger cavity and the reset device.

2. A self-adapting oscillating radial piston pump according to claim 1, characterized in that: The driving ring is connected with a ball pair of the inner plunger sleeve, and the end of the outer plunger sleeve is connected with a ball pair of the pump body, and the ball pair connection is a convex spherical surface and a concave spherical surface constraint connection.

3. A self- adaptive oscillating radial piston pump with a variable piston axis according to claim 2, characterized in that: The convex spherical surface is a ball head structure, the end of the outer plunger sleeve and the end of the inner plunger sleeve are provided with a ball head structure, the pump body and the driving ring are provided with a matching concave spherical surface, and the ball head is arranged in abutment with the concave spherical surface.

4. A self- adaptive oscillating radial piston pump with adaptive plunger axis according to claim 1, characterized in that: A spring (701) is arranged in the plunger cavity of the outer plunger sleeve and the inner plunger sleeve, and the spring force of the spring (701) always makes the outer plunger sleeve and the inner plunger sleeve abut with the matching spherical pair.

5. A self- adaptive oscillating radial piston pump with adaptive plunger axis according to claim 3, characterized in that: The ball head structure provided at the end of the outer plunger sleeve and the end of the inner plunger sleeve is provided with a mechanical reset device (8), the mechanical reset device (8) comprises an outer plunger mechanical reset component and an inner plunger mechanical reset component, the outer plunger mechanical reset component is arranged at the ball pair connection position of the outer plunger sleeve and the pump body, the inner plunger mechanical reset component is arranged at the ball pair connection position of the inner plunger sleeve and the driving ring, the outer plunger mechanical reset component comprises a plunger stop ring (801) and an elastic stop ring (802), the plunger stop ring (801) is sleeved on the ball head of the end of the outer plunger sleeve and is arranged in abutment with the concave spherical surface provided on the pump body, the plunger stop ring (801) clamps the ball head of the end of the outer plunger sleeve in the concave spherical surface provided on the pump body, and the elastic stop ring (802) is pressed on the plunger stop ring (801); the inner plunger mechanical reset component comprises a plunger hoop (803), the plunger hoop (803) is sleeved on the driving ring, the plunger hoop (803) is provided with a clamping groove (8031) penetrating therethrough, the position of the clamping groove (8031) corresponds to the concave spherical surface provided on the driving ring, and the clamping groove (8031) clamps the ball head provided at the end of the inner plunger sleeve in the concave spherical surface provided on the driving ring.

6. A plunger axis self-adapting wobble radial piston pump according to claim 5, characterized in that: The inner circle of the plunger stop ring (801) is provided with a spherical surface, the spherical surface of the inner circle of the plunger stop ring (801) is combined with the concave spherical surface provided on the pump body, the ball head of the end of the outer plunger sleeve is clamped in the concave spherical surface provided on the pump body, the inner wall of the clamping groove (8031) is provided with a spherical surface, and the spherical surface of the inner wall of the clamping groove (8031) is combined with the concave spherical surface provided on the driving ring to clamp the ball head provided at the end of the inner plunger sleeve in the concave spherical surface provided on the driving ring.

7. A self- adaptive oscillating radial piston pump with adaptive plunger axis according to claim 1, characterized in that: A limiting pin (17) is arranged on the end face of the driving ring, the extending part of the limiting pin (17) faces the front end cover (11), an inner cylindrical hole (1101) is machined on the front end cover (11), and the position of the inner cylindrical hole (1101) matches the arrangement of the limiting pin (17).

8. A self- adaptive oscillating radial piston pump with adaptive plunger axis according to claim 1, characterized in that: The sliding transition piece (16) is a structural member in the form of low-friction rolling such as a sliding bearing and a needle bearing or a structural member in the form of low-friction sliding such as PEEK and diamond.

9. A self- adaptive oscillating radial piston pump with adaptive plunger axis according to claim 1, characterized in that: The pump body comprises a shell (1) and a cover plate assembly, which can be an integrally cast part or a combined part.

10. A self- adaptive oscillating radial piston pump with a variable piston axis according to claim 9, characterized in that: The shell (1) is provided with a concentric disc flow distribution component, the shell (1), the cover plate assembly, the concentric disc flow distribution component are provided with oil channels communicating with the plunger assembly, the cover plate assembly is a second cover plate assembly (15), the plunger assembly is a second plunger assembly (6), the second plunger assembly (6) includes a second outer plunger sleeve (601), the bottom end surface of the second cover plate assembly (15) is connected with the spherical pair of the second outer plunger sleeve (601), the second cover plate assembly (15) is provided with a third flow distribution valve oil channel (1501) and a fourth flow distribution valve oil channel (1502) on the transverse two sides respectively, a communicating oil channel fifth oil channel (1503) is arranged between the third flow distribution valve oil channel (1501) and the fourth flow distribution valve oil channel (1502), a sixth oil channel (6011) is arranged on the central axis of the spherical end surface of the second outer plunger sleeve (601) and penetrates the plunger inner cavity, the central axis of the sixth oil channel (6011) is coaxially arranged with the inner cavity central axis of the second outer plunger sleeve (601), a seventh oil channel (1504) is arranged on the bottom spherical end surface of the second cover plate assembly (15), the seventh oil channel (1504) is communicated with the fifth oil channel (1503), the seventh oil channel (1504) is coaxially arranged with the sixth oil channel (6011), a thirteenth oil channel (1506) is arranged on one side of the second cover plate assembly (15), the thirteenth oil channel (1506) is communicated with the fourth flow distribution valve oil channel (1502), the shell (1) is provided with a twenty-seventh oil channel (103) and a twenty-eighth oil channel (104), the twenty-seventh oil channel (103) and the twenty-eighth oil channel (104) are communicated, the twenty-seventh oil channel (103) is communicated with the thirteenth oil channel (1506), the concentric disc flow distribution component includes a first flow distribution disc (17), a first compensation disc (18) and a first spring (19), the first flow distribution disc (17), the first compensation disc (18) and the first spring (19) are arranged in the rear end cover, the rear end cover is a second rear end cover (24), the second rear end cover (24) is provided with a twenty-third oil channel (2401) penetrating the center, and three groups of cylindrical hole grooves, i.e., a third cylindrical hole groove (2403), a fourth cylindrical hole groove (2404) and a fifth cylindrical hole groove (2405) are arranged in the inner cavity, the third cylindrical hole groove (2403) is arranged at the bottom, the fourth cylindrical hole groove (2404) is arranged above the third cylindrical hole groove (2403), the fifth cylindrical hole groove (2405) is arranged above the fourth cylindrical hole groove (2404), the diameter of the third cylindrical hole groove (2403) is smaller than that of the fourth cylindrical hole groove (2404), the diameter of the fourth cylindrical hole groove (2404) is smaller than that of the fifth cylindrical hole groove (2405), the third cylindrical hole groove (2403), the fourth cylindrical hole groove (2404) and the fifth cylindrical hole groove (2405) are arranged in a stepped manner, the second rear end cover (24) is provided with a twenty-fourth oil channel (2402), the twenty-fourth oil channel (2402) is arranged along the radial direction of the second rear end cover (24) and penetrates the hole wall of the fourth cylindrical hole groove (2404) and the fifth cylindrical hole groove (2405),The first compensation disc (18) is a flange type structure including a flange disc and a cylindrical shaft. A twenty-first oil channel (1801) is arranged through the center of the first compensation disc (18), and the twenty-first oil channel (1801) is in communication with a twenty-third oil channel (2401). The cylindrical shaft of the first compensation disc (18) is arranged in a third cylindrical hole groove (2403), and the flange disc of the first compensation disc (18) is arranged in a fourth cylindrical hole (2404) groove. A first flow distribution disc (17) is arranged in a fifth cylindrical hole (2405), and the first flow distribution disc (17) is fixedly arranged on a driving shaft (2). The two end faces of the first flow distribution disc (17) are respectively abutted with the end faces of the first compensation disc (18) and a shell (1). A first spring (19) is arranged between the bottom end face of the fourth cylindrical hole (2404) groove and the end face of the flange disc of the first compensation disc (18). An arc groove, i.e., a first arc groove (1701) and a second arc groove (1703), is arranged on one end face of the first flow distribution disc (17). A first cylindrical hole groove (1705) is arranged on the other end face of the first flow distribution disc (17). A plurality of nineteenth oil channels (1702) are radially arranged in the first arc groove (1701) and penetrate the shaft hole and the first cylindrical hole groove (1705) in the direction of the central axis. A plurality of twentieth oil channels (1704) are radially arranged in the second arc groove (1703) and penetrate the outer circular wall of the first flow distribution disc (17). The end face of the first flow distribution disc (17) where the first cylindrical hole groove (1705) is arranged is abutted with the end face of the first compensation disc (18). The diameter of the first flow distribution disc (17) is smaller than the diameter of the fifth cylindrical hole groove (2405). A first cavity (26) is formed between the outer wall of the first flow distribution disc (17) and the inner wall of the fifth cylindrical hole groove (2405). The end faces of the first flow distribution disc (17) and the first compensation disc (18) are abutted. The first cylindrical hole groove (1705) forms a second cavity (27). The second cavity (27) is in communication with the nineteenth oil channels (1702) and the twenty-first oil channels (1801). With the rotation of the first flow distribution disc (17), the twenty-eighth oil channel (104) is periodically communicated with the first arc groove (1701) and the second arc groove (1703). Hydraulic oil enters the pump through an external pipeline and flows into a plunger cavity. The path is: external pipeline→twenty-third oil channel (2401)→twenty-first oil channel (1801)→second cavity (27)→nineteenth oil channel (1702)→first arc groove (1701)→twenty-eighth oil channel (104)→twenty-seventh oil channel (103)→thirteenth oil channel (1506)→fourth flow distribution valve oil channel (1502)→fifth oil channel (1503)→seventh oil channel (1504)→sixth oil channel (6011)→plunger cavity. The hydraulic oil in the plunger cavity is discharged to the external pipeline.Its path is: the plunger cavity→the sixth oil channel (6011)→the seventh oil channel (1504)→the fifth oil channel (1503)→the fourth distribution valve oil channel (1502)→the thirteenth oil channel (1506)→the twenty-seventh oil channel (103)→the twenty-eighth oil channel (104)→the second arc-shaped groove (1703)→the twentieth oil channel (1704)→the first cavity (26)→the twenty-fourth oil channel (2402)→the external pipeline.

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