CN114562437A - Sliding disc type axial plunger pump - Google Patents

Abstract

The invention discloses a sliding disc type axial plunger pump, which comprises a flow distribution sliding disc pair, a plunger pair and a flow distribution pair, wherein the flow distribution sliding disc pair comprises a swash plate and a sliding disc supported on the swash plate, the sliding disc is of an integral structure, a waist-shaped hole communicated with a central hole of a plunger is arranged on the sliding disc, a low-pressure oil distribution hole serving as an oil inlet channel is arranged on a bearing surface of the swash plate opposite to a low-pressure plunger hole, a bearing surface of the swash plate opposite to a high-pressure plunger hole and the waist-shaped hole of the sliding disc form static pressure bearing, the low-pressure oil distribution hole is communicated with a shell cavity through an oil inlet groove arranged on the swash plate, when the plunger pump works, low-pressure oil enters the plunger hole from a low-pressure flow distribution port and an oil inlet groove or groove-shaped low-pressure port of the swash plate, and the high-pressure oil is discharged from a high-pressure flow distribution port of the flow distribution disc or a groove-shaped high-pressure port of the swash plate in a single way, so as to realize the suction and the discharge of hydraulic oil. The invention can further reduce the axial stress of the bearing, improve the stress working condition of the bearing, improve the self-suction capability and reduce the oil temperature, thereby improving the working reliability and the working life of the plunger pump.

Description

Sliding disc type axial plunger pump

Technical Field

The invention belongs to the technical field of hydraulic transmission and control, and particularly relates to a sliding disc type axial plunger pump.

Background

The axial plunger pump is one of the most widely used hydraulic components in modern hydraulic transmission, and the hingeless inclined shaft pump and the sliding shoe inclined disc type axial plunger pump are two types of axial plunger pumps which are most widely applied and are the most main at present. The inclined shaft pump and the slipper inclined disc type pump have the characteristics respectively, and the two pumps are in competition at present and are continuously improved and developed respectively.

The swash plate type plunger pump has the characteristics of simple and compact structure, small volume, light weight, stepless variable realized by the swinging of the swash plate, small inertia of the variable, high variable response speed and the like, is widely applied, but has the inherent defects of design, such as the problem of dynamic unbalance force in the motion process, poor low-speed performance and the problem of premature wear of a sliding shoe and a valve plate caused by wedge contact motion, and the problems are not fundamentally changed for hundreds of years. Compared with a swash plate type structure, the existing swash shaft structure has less leakage, less dynamic unbalanced force and good low-speed performance due to the fact that a pair of friction pairs are reduced, so that the structure is mainly widely applied to a motor, but the structure is limited to be used as a pump due to the fact that variables are difficult, the variable response time is slow, the shaft cannot be communicated, the service life of a main shaft is short and the like.

A brand new axial plunger pump structure combines the structures of the existing swash plate type and inclined shaft type plunger pumps, the structures of the swash plate type and inclined shaft type plunger pumps are deeply fused, a sliding disc type axial plunger pump is creatively provided, and dozens of patents (CN201910189721.4, CN201910189068.1, CN201910189070.9 and the like) are formed. In order to further improve bearing atress, improve life-span, improve self-priming ability, reduce fluid because of the influence of the pump body high temperature that friction and volumetric efficiency loss caused to the friction is vice, improve the oil absorption end of sliding tray formula plunger pump, this novel sliding tray formula plunger pump is particularly suitable for being applied to in the open plunger pump.

Disclosure of Invention

The invention aims to: the novel axial plunger pump structure aims at further reducing the axial stress of a bearing, improving the stress working condition of the bearing and improving self-absorption capacity, and reducing the influence of overhigh temperature of a pump body caused by friction and volume efficiency loss on friction of oil liquid, thereby improving the working reliability and the service life of the sliding disc type axial plunger pump.

The technical scheme of the invention has the implementation mode that: a sliding-disk axial plunger pump, characterized in that: the hydraulic pump comprises a flow distribution sliding disc pair, a plunger pair and a flow distribution pair, wherein the flow distribution sliding disc pair comprises a swash plate and a sliding disc supported on the swash plate, the sliding disc is of an integral structure, a sliding disc waist-shaped hole communicated with a plunger center hole of the plunger pair is arranged on the sliding disc, a low-pressure oil distribution hole serving as an oil inlet channel is arranged on a swash plate supporting surface opposite to a low-pressure plunger hole, a swash plate supporting surface opposite to a high-pressure plunger hole and the sliding disc waist-shaped hole form static pressure support, the low-pressure oil distribution hole is communicated with a shell cavity through an oil inlet groove arranged on the swash plate, when the plunger pump works, a main shaft drives a cylinder body to synchronously rotate and drives the sliding disc to slide on the swash plate through a plunger, low-pressure oil enters the plunger hole of the cylinder body from a low-pressure flow distribution port of the flow distribution disc and the oil inlet groove or a groove-shaped low-pressure port double-way of the swash plate, and the high-pressure oil is discharged from the high-pressure flow distribution port of the flow distribution disc or the groove-shaped high-pressure port of the swash plate single way, the suction and the discharge of the hydraulic oil are realized.

The invention relates to a sliding disc type axial plunger pump, wherein a sliding disc convex table surface extending to one side of an inclined disc along the axis of the sliding disc is arranged on the sliding disc, a plurality of sliding disc waist-shaped holes and sealing parts for sealing oil are arranged on the sliding disc convex table surface, the sealing parts are arranged on the inner periphery of the sliding disc waist-shaped holes in a state of surrounding the sliding disc waist-shaped holes, and each sealing part comprises a sliding disc inner sealing part, a sliding disc outer sealing part and a sliding disc interval sealing part, wherein the sliding disc inner sealing part, the sliding disc outer sealing part and the sliding disc interval sealing part are arranged between the adjacent sliding disc waist-shaped holes.

The invention relates to a sliding disc type axial plunger pump, wherein a flow distribution pair is a bidirectional high-low pressure flow distribution pair, the flow distribution pair comprises a cylinder body end part and a flow distribution disc supported on a rear end cover, the cylinder body end part and the flow distribution disc end surface form a static pressure oil film support in clearance fit, the flow distribution disc is provided with a low pressure flow distribution port and a high pressure flow distribution port which are separated, and the low pressure flow distribution port and the high pressure flow distribution port are respectively communicated with an oil inlet and an oil outlet of the rear end cover.

The invention relates to a sliding disc type axial plunger pump, wherein a flow distribution sliding disc pair is a one-way low-pressure flow distribution sliding disc pair, the flow distribution sliding disc pair comprises a swash plate and a sliding disc supported on the swash plate, a static pressure oil film support in clearance fit is formed between the swash plate and the end surface of the sliding disc, the swash plate and the sliding disc are in sliding fit, a low-pressure flow distribution window is arranged on one side of the sliding disc opposite to a low-pressure plunger hole, and when the pump sucks oil, low-pressure oil in a shell cavity sequentially flows through the low-pressure flow distribution window, the kidney-shaped hole of the sliding disc, a plunger center hole and a cylinder plunger hole.

The invention relates to a sliding disc type axial plunger pump, wherein a flow distribution pair is a one-way low-pressure flow distribution pair, the flow distribution pair comprises a cylinder end part and a flow distribution disc supported on a shell, the cylinder end part and the flow distribution disc end surface form a static pressure oil film support in clearance fit and the static pressure oil film support and the flow distribution disc end surface keep sliding fit, one side of the flow distribution disc opposite to a low-pressure plunger hole is provided with a low-pressure flow distribution port, and when the pump absorbs oil, low-pressure oil enters the plunger hole of the cylinder from a cavity of the pump shell through the low-pressure flow distribution port.

The invention relates to a sliding disc type axial plunger pump, wherein a flow distribution sliding disc pair is a bidirectional high-low pressure flow distribution sliding disc pair, the flow distribution sliding disc pair comprises a swash plate and a sliding disc supported on the swash plate, a static pressure oil film support in clearance fit is formed between the swash plate and the end surface of the flow distribution disc, the swash plate and the end surface of the flow distribution disc are in sliding fit, a support surface opposite to a rear end cover on the swash plate is provided with a cylindrical sliding arc surface, a groove-shaped low pressure port and a groove-shaped high pressure port in groove shape are formed on the cylindrical sliding arc surface of the swash plate, and the groove-shaped low pressure port and the groove-shaped high pressure port are respectively and correspondingly communicated with an oil inlet and an oil outlet on the rear end cover.

The thrust disc is supported on the thrust disc and keeps sliding fit with the thrust disc, the thrust disc is provided with a low-pressure flow distribution port and/or a high-pressure flow distribution port, and the flow distribution port of the thrust disc is communicated with a flow distribution oil groove of the swash plate and a kidney-shaped hole of the slip disc.

According to the sliding disc type axial plunger pump, the spring pre-tightening device is arranged between the sliding disc and the cylinder body, and the flow distribution sliding disc pair and the sliding disc pair have certain initial contact force through the spring pre-tightening device.

Or, a restraining device is arranged on the sliding plate and/or the cylinder block, and the restraining device is used for limiting the sliding plate of the distribution sliding plate pair to move away from the swash plate and limiting the cylinder block of the distribution sliding plate pair to move away from the distribution plate.

According to the sliding disc type axial plunger pump, the cylinder body is provided with the impeller device, and the impeller device directionally drives low-pressure oil to enter the plunger hole from the cavity of the shell in an accelerating manner.

The invention relates to a sliding disc type axial plunger pump, which is of a through shaft type structure and specifically comprises a main shaft, a shell, a first bearing, a second bearing, a plunger, a cylinder body, a flow distribution disc and a rear end cover, wherein a communication groove communicated with a cavity of the shell is formed in the rear end cover, the axis of the main shaft is superposed with the axis of the cylinder body, one end of the main shaft penetrates through a flow distribution sliding disc pair to extend out of the shell and is supported on the first bearing, the other end of the main shaft penetrates through the flow distribution pair and is supported on the second bearing, the cylinder body is supported on the main shaft and is in key connection with the main shaft to realize synchronous rotation, and the plunger reciprocates in a plunger cavity of the cylinder body to realize oil suction and discharge work of the pump.

The invention relates to a sliding disc type axial plunger pump, which is of a non-through shaft type structure and specifically comprises a main shaft, a shell, a first bearing, a plunger, a cylinder body, a sliding disc and a rear end cover, wherein a communicating groove communicated with a cavity of the shell is formed in the rear end cover, the axis of the main shaft is superposed with the axis of the cylinder body, one end of the main shaft penetrates through a flow distribution pair and extends out of the shell and is supported on the first bearing, a cantilever at the other end of the main shaft is supported in the cylinder body and is connected with the cylinder body through a key, the main shaft and the cylinder body rotate synchronously, and the plunger reciprocates in the plunger cavity of the cylinder body to realize oil suction and discharge work of the pump.

Based on the technical scheme, the invention has the beneficial effects that:

1. according to the invention, two disc-shaped static pressure bearing surfaces (namely, the flow distribution pair and the flow distribution sliding disc pair structure) are arranged in the pump body, so that mutual offset can be formed in the axial direction, the axial force action of the bearing is greatly reduced, and meanwhile, compared with the traditional sliding shoe pair and flow distribution pair structure, an oil film is more stable, so that the reliability of the pump is further improved, and the service life of the pump is further prolonged.

2. According to the invention, the two-way oil inlet structure is arranged in the pump body, namely, the two ways of oil enters the plunger hole of the cylinder body from the low-pressure flow distribution port of the flow distribution plate and the oil inlet groove of the swash plate or the two ways of the groove-shaped low-pressure port, so that on one hand, the oil inlet amount of the oil suction side is increased, the self-sucking capacity can be greatly improved, and the self-sucking rotating speed is improved; on the other hand, one path of oil which flows through the inner cavity of the pump shell and enters the plunger hole can bring heat converted by friction and volumetric efficiency loss into a hydraulic system, so that the hot oil is not retained in the pump body for a long time, the adverse effect of high temperature on a friction pair is avoided, and the service life is prolonged; moreover, an oil return pipeline is structurally omitted, and the structure is simplified.

3. The invention integrates the functions of flow distribution, variable inclination and static pressure support in the sliding disc pair, and the plunger adopts a conical structure, so that the lateral force of the plunger is greatly reduced, and the overturning phenomenon of the cylinder body is eliminated or reduced; the variable of the pump is realized by changing the inclination mode of the swash plate, and the variable has small inertia, convenient variable and high variable response speed; meanwhile, the structure is simple and compact, the size is small, the weight is light, and the characteristics of the existing swash plate type plunger pump and the existing swash shaft type plunger pump are combined.

4. The invention adopts the structure of the flow distribution sliding disc pair and the flow distribution pair, the two are better than the sliding shoe pair in the aspect of keeping the stability of an oil film, and particularly have better performance in the aspect of low-speed performance, and the characteristic has the advantages of the existing inclined shaft type plunger pump.

5. The invention adopts the flow distribution sliding disc pair with a disc-shaped structure, has the characteristic of large inclination angle of the inclined shaft type plunger pump, and can break through the limitation of the maximum inclination angle of the existing inclined disc type plunger pump, thereby having larger discharge capacity and more prominent power density under the same volume.

6. In the axial plunger pump, the oil inlet and the oil outlet are integrated on the rear end cover, so that the structure is greatly simplified, the size is smaller, the structure is more compact, and the weight of the pump is smaller, so that the unit mass power density of the axial plunger pump is improved; meanwhile, the cylinder body is close to the bearing, so that bending moment acting on the cantilever main shaft is reduced, the stress on the main shaft is more favorable, the service life of the bearing is longer, and mechanical noise is smaller in the working process.

7. In the invention, the functions of flow distribution, variable inclination and static pressure support are integrated in the sliding disc pair, and the plunger ball socket and the plunger ball head on the sliding disc can relatively tilt in the working process, so that the tilting disc can be self-adapted to tilt, the cylinder block tilts and other tilts, the sliding disc can always cling to the tilting disc to complete the functions of flow distribution, variable inclination, support and the like, and wedge-shaped gaps are avoided; simultaneously, compare and change the cylinder body, it is easier, more economical to change sliding plate or valve plate.

8. The oil through hole and the plunger center hole on the sliding disc are large-aperture main oil holes, so that oil stain blockage can be prevented, and oil stain sensitivity is reduced; meanwhile, the large-aperture plunger center hole reduces the mass of the plunger and is beneficial to reducing the centrifugal force of the plunger.

9. The sliding disc structure is an integral structure, and replaces a plurality of independent sliding shoes and a structure utilizing return stroke of a return stroke disc in the prior art, the connection between the plunger and the sliding disc and the connection between the sliding disc and the pressure disc are more reliable, the phenomena of abrasion of the neck and the shoulder of the sliding shoe, shearing damage, cracking of the drilling part of the return stroke disc and the like in the prior art are avoided, and the working reliability of the swash plate type plunger pump is improved. Meanwhile, the centrifugal force and the friction force of each part of the sliding plate are mutually offset, the overturning of a single sliding shoe under the comprehensive action of the centrifugal moment caused by circumferential motion and the friction moment generated along with the rotation of the cylinder body in the high-speed motion process is avoided, the integral sliding plate structure is uniform in abrasion, and the eccentric wear phenomenon of the original sliding shoe pair is eliminated or reduced.

10. The axial plunger pump can be made into a through shaft type structure or a non-through shaft type structure, parts of the two structures are strong in universality, so that the axial plunger pump can well meet various requirements of the market, and the manufacturing cost is not changed obviously. When the shaft is used as a through shaft type structure, an oil supplementing pump can be connected in series at the shaft end to realize the oil supplementing effect.

Drawings

Fig. 1 shows an embodiment of a through-shaft sliding-disc axial piston pump according to the invention.

FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1 according to the present invention.

Fig. 3 is a structural view of a port plate of the present invention.

FIG. 4 is a schematic view of the end face structure of the cylinder block side of the present invention.

FIG. 5 is a cross-sectional view taken along line B-B of FIG. 4 according to the present invention.

FIG. 6 is a schematic view of the other end face structure of the cylinder body according to the present invention.

Fig. 7 is a plan view of one end of the slide plate of the present invention.

FIG. 8 is a cross-sectional view taken along line C-C of the slider structure of FIG. 7 according to the present invention.

Fig. 9 is a plan view of the other end of the slide plate in the present invention.

FIG. 10 is a plan view of the bearing surface of one end of the swashplate of the embodiment of FIG. 1 of the present invention.

FIG. 11 is a view of the swash plate sliding arc bearing surface of the embodiment of FIG. 1 of the present invention.

Fig. 12 shows an embodiment of the present invention of a plunger pump with a center spring pre-tensioning device.

Fig. 13 shows an embodiment of a plunger pump of the present invention having an impeller structure.

Fig. 14 shows another embodiment of the sliding disc axial piston pump according to the invention.

FIG. 15 is a cross-sectional view taken along line A-A of FIG. 14 according to the present invention.

Fig. 16 shows a configuration of the port plate of the embodiment of fig. 14 according to the present invention.

FIG. 17 shows a configuration of one side of the swash plate of the embodiment of FIG. 14 according to the present invention.

FIG. 18 shows a configuration of the other side of the swash plate of the embodiment of FIG. 14 according to the present invention.

FIG. 19 is an embodiment of the non-through-shaft axial plunger pump of the present invention.

The labels in the figure are: 10 is a main shaft, 10C is a main shaft axis, 11 is a first bearing supporting part, 12 is a second bearing supporting part, 21 is a first bearing, 22 is a second bearing, 23 is a third bearing, 24 is a push disc, 31 is a shell, 32 is a front end cover, 33 is a rear end cover, 33a is an oil inlet, 33b is an oil outlet, 35 is a shell cavity, 37 is a communicating groove, 39 is a swash plate oil through hole, 40 is a swash plate, 41 is a swash plate supporting surface, 41a is a supporting baffle part, 42 is a flow distribution oil groove, 43 is a low-pressure flow distribution window, 44 is a high-pressure flow distribution window, 43a is a throttling groove or a throttling hole, 45 is a cylindrical sliding arc surface, 46 is a groove-shaped low-pressure port, 47 is a groove-shaped high-pressure port, 47a is a groove-shaped oil chamber, 48 is an oil inlet groove, 49 is a shaft pin, 50 is a sliding disc, 50C is a sliding disc axis, 51 is a sliding disc static pressure supporting surface, 52 is a sliding disc convex table surface, 53 is a sliding disc outer sealing part, 55 is a sliding plate inner sealing part, 56 is a sliding plate interval sealing part, 57 is a sliding plate auxiliary supporting surface, 57a is a sliding plate annular oil drainage groove, 57b is a sliding plate radial oil drainage groove, 58 is a plunger ball socket, 60 is a pressing plate, 70 is a plunger, 71 is a plunger ball head, 72 is a plunger central hole, 73 is a tapered rod part, 74 is a plunger part, 80 is a cylinder body, 81 is a plunger hole, 82 is a main shaft assembling hole, 83 is a cylinder body static pressure supporting surface, 83a is a cylinder body convex table surface, 84 is an oil through hole, 85 is a cylinder body waist-shaped hole, 86 is a cylinder body outer sealing part, 87 is a cylinder body inner sealing part, 88 is a cylinder body interval sealing part, 80C is a cylinder body shaft center, 90 is a flow distribution plate, 91 is a static pressure supporting surface, 92 is a low pressure flow distribution port, 93 is a high pressure flow distribution port, 94 is an outer sealing belt, 95 is an inner sealing belt, 100 is a central spring, 101 is a retainer ring, 102 is a ball hinge, 140 is a clamping device, 141 is a clamp spring, and 150 is an impeller.

Detailed Description

The present invention will be described in detail below with reference to the accompanying drawings.

While this invention is susceptible of embodiment in many different forms, this specification and the accompanying drawings disclose only some specific forms as examples of the invention. The invention is not intended to be limited to the embodiments so described. The scope of the invention is given by the appended claims.

For ease of description, embodiments of the present invention are shown in a typical orientation such that when the central axis of the main shaft of the axial plunger pump is resting horizontally, with the coupling end side of the main shaft to the left and the rear end cap to the right, the terms "longitudinal," "lateral," "up," "down," "front," "back," "left," "right," "horizontal," "bottom," "inner," "outer," and the like are used in the description with reference to this position only for ease of description and simplicity of description, and do not indicate or imply that the device or component referred to must have a particular orientation, and that particular orientation configuration and operation, it being understood that the present invention may be manufactured, stored, shipped, used, and sold in an orientation other than the position described.

Example 1:

as shown in fig. 1 to 11, which are preferred embodiments of the axial plunger pump of the present invention, in the preferred embodiment shown, the plunger pump is a through-shaft plunger pump, and includes a main shaft 10, a housing 31, a first bearing 21, a second bearing 22, a flow distribution sliding disc pair, a plunger pair, a flow distribution pair, and a rear end cap 33, a communication groove 37 communicating with a housing cavity 35 is provided on the rear end cap 33, a main shaft axis 10C of the main shaft 10 coincides with a cylinder axis 80C of a cylinder 80, one end of the main shaft 10 penetrates through the flow distribution sliding disc pair to extend out of the housing 31 and is supported on the first bearing 21, the other end penetrates through the flow distribution pair and is supported on the second bearing 22, the cylinder 80 is supported on the main shaft 10 and is connected with the main shaft through a key to realize synchronous rotation, and the plunger 70 reciprocates in the plunger cavity of the cylinder 80 to realize oil suction and discharge operation of the pump.

Specifically, the flow distribution sliding disc pair comprises a sliding disc 50 and a swash plate 40, a static pressure supporting surface 51 of the sliding disc 50 is supported on the swash plate 40 and is tightly matched with the supporting surface of the swash plate 40, a plurality of kidney-shaped holes 53 are formed in one end of the sliding disc 50, a plurality of plunger ball sockets 58 are formed in the other end surface of the sliding disc 50, the kidney-shaped holes 53 of the sliding disc 50 penetrate through the plunger ball sockets 58, and a flow distribution oil groove 42 communicated with an oil inlet 33a and an oil outlet 33b is formed in the swash plate 40.

Specifically, the plunger pair comprises a plunger 70 and a cylinder hole wall, the plunger 70 is of a conical structure, and the plunger is provided with a large-hole plunger center hole 72 which is used for oil inlet and outlet and is communicated with a plunger ball socket 58 and a plunger hole 81.

Specifically, the flow distribution pair comprises a cylinder end and a flow distribution plate 90 supporting the rear end cover 33, wherein the end face of the cylinder end opposite to the flow distribution plate 90 is provided with a cylinder static pressure bearing surface 83, the cylinder static pressure bearing surface 83 is supported on the flow distribution plate 90 and is in sliding fit with the flow distribution plate 90, and the flow distribution plate 90 is also provided with a static pressure bearing surface 91, a low-pressure flow distribution port 92, a high-pressure flow distribution port 93, an outer sealing belt 94 and an inner sealing belt 95.

As shown in fig. 1 and 2, the pump body of the embodiment includes a housing 31, and a rear end cap 33 and a front end cap 32 connected to the housing 31. The housing 31 is provided with a housing cavity 35 for accommodating the rotor assembly, the rear end cover 33 is used for closing one end opening of the housing 31, the front end cover 32 is used for closing the other end opening of the housing 31, the rear end cover 33 is provided with an oil inlet 33a and an oil outlet 33b of the pump, the rear end cover 33 is provided with a communication groove 37 for communicating the oil inlet 33a with the housing cavity 35, namely when the pump sucks oil, the oil in the oil inlet 33a is divided into two parts, one part of the oil flows into the plunger hole from the low-pressure distributing port of the distributing plate, the other part of the oil enters the housing cavity 35 through the communication groove 37, and the cold oil of the part cools each friction pair part in the housing cavity, so that the thermal deformation of the friction pair parts is reduced.

Wherein the spindle 10 penetrates the housing 31 to the rear end cap 33 in a cylindrical shape, on which a first bearing support 11 and a second bearing support 12 are provided, a first bearing 21 is interposed between the first bearing support 11 and the housing 31, a second bearing 22 is interposed between the second bearing support 12 and the rear end cover 33, one end of the main shaft 10 penetrates through the flow distribution sliding disc pair and extends out of the shell 31, and is supported on the shell 31 through the first bearing 21, the end is used for connecting an external prime motor (or load), the other end penetrates through the flow distribution pair and then reaches the rear end cover 33 and is supported on the rear end cover 33 through the second bearing 22, the main shaft 10 is rotatable about its own axis with respect to the housing 31 via the first bearing 21 and the second bearing 22, the circumferential surface of the middle area of the main shaft 10 is provided with a key connection structure for connecting the cylinder body 80, and the main shaft 10 drives the cylinder body 80 to synchronously rotate through the key connection structure.

The cylinder body 80 has a cylindrical configuration with a circular cross section along the radial direction and is accommodated in the housing cavity 35 of the housing 31, the cylinder body 80 has a plurality of plunger holes 81 uniformly distributed in a circumferential direction of a cylinder body axis 80C and a main shaft assembling hole 82 for accommodating the main shaft at the center, the cylinder body 80 has a plurality of plunger holes 81, and preferably, the number of the plunger holes is generally set to 7 or 9, as shown in fig. 6; the main shaft 10 passes through a main shaft assembly hole 82 of the cylinder block 80 and is connected to the cylinder block 80 in such a manner that a connection key is provided on the outer circumferential surface of the shaft body, and the cylinder block 80 is supported on the main shaft 10 in such a manner that it moves in synchronization with the main shaft 10.

As shown in fig. 2 and 3, a cylinder static pressure bearing surface 83 is provided on an end surface of the cylinder 80 opposite to the port plate 90, the cylinder static pressure bearing surface 83 is supported on the port plate 90 and always keeps sliding fit with the port plate 90, a plurality of cylinder waist-shaped holes 85 in a waist shape are provided on the cylinder static pressure bearing surface 83, preferably, the cylinder waist-shaped holes 85 are uniformly distributed on the cylinder static pressure bearing surface 83 around a cylinder axis 80C, and oil through holes 84 for communicating the plunger hole 81 and the cylinder waist-shaped holes 85 are provided on the cylinder end.

Further, a protruding cylinder boss surface 83a extending toward the port plate 90 side along the cylinder axis 80C is provided on the end surface of the cylinder 80 facing the port plate 90, the cylinder boss surface 83a is formed by a region surrounded by an inner diameter R1 and an outer diameter R2, the cylinder boss surface 83a and the port plate 90 support surface are slidably abutted against each other, a plurality of cylinder kidney holes 85 are provided on the cylinder boss surface 83a at positions corresponding to the plunger holes 81, and the cylinder kidney holes 85 are preferably distributed on the cylinder boss surface 83a at regular intervals on a common circumference centering on the cylinder axis 80C.

The cylinder boss surface 83a and the support surface of the valve plate 90 form effective static pressure oil film support, a sealing part for sealing oil is arranged on the cylinder boss surface 83a, the sealing part is arranged on the inner periphery of the cylinder kidney-shaped hole 85 in a state of surrounding the cylinder kidney-shaped hole 85, the sealing part comprises an inner cylinder sealing part 87 distributed inside and outside the cylinder kidney-shaped hole 85 in the radial direction, an outer cylinder sealing part 86 and a cylinder interval sealing part 88 distributed between the adjacent cylinder kidney-shaped holes 85, the inner cylinder sealing part 87 is a region enclosed by the inner edge of the cylinder kidney-shaped hole 85 and the inner diameter R1 of the cylinder boss surface 83a, the outer cylinder sealing part 86 is a region enclosed by the outer edge of the cylinder kidney-shaped hole 85 and the outer diameter R2 of the cylinder boss surface 83a, and the cylinder interval sealing part 88 is a region of the interval boss surface between the adjacent cylinder kidney-shaped holes 85, a certain reasonable clearance is always kept between the sealing part of the cylinder body boss surface 83a and the supporting surface of the thrust plate 90, so that oil film leakage is in a reasonable level.

In this embodiment, the flow distribution pair is a bidirectional high-low pressure flow distribution pair, the flow distribution pair includes a cylinder end and a flow distribution plate 90 supported on the rear end cover 33, the cylinder end and the end surface of the flow distribution plate 90 form a static pressure oil film support in clearance fit, the flow distribution plate 90 is provided with a low pressure flow distribution port 92 and a high pressure flow distribution port 93 which are separated, and the low pressure flow distribution port 92 and the high pressure flow distribution port 93 are respectively communicated with the oil inlet 33a and the oil outlet 33b of the rear end cover, as shown in fig. 3. The flow distribution sliding disc pair is a one-way low-pressure flow distribution sliding disc pair, the flow distribution sliding disc pair comprises a swash plate 40 and a sliding disc 50 supported on the swash plate 40, a static pressure oil film support in clearance fit is formed on the end faces of the swash plate 40 and the sliding disc 50, the static pressure oil film support and the sliding disc 50 are in sliding fit, a low-pressure flow distribution window 43 is arranged on one side of the sliding disc 50 opposite to a low-pressure plunger hole, the low-pressure plunger hole is a corresponding plunger hole into which low-pressure oil enters, conversely, the high-pressure plunger hole is a corresponding plunger hole into which high-pressure oil enters, and when a pump sucks oil, low-pressure oil in the shell cavity 35 sequentially flows through the low-pressure flow distribution window 43, the sliding disc kidney-shaped hole 53, the plunger center hole 72 and the cylinder plunger hole 81.

In operation, hydraulic pressure acts on the cylinder end and is further transmitted to the port plate 90. in general, the axial force of the hydraulic pressure acting on the cylinder end is greater than the bearing force of the port plate 90 acting on the cylinder end through an oil film, so that the cylinder end slides against the port plate 90 through a layer of oil film all the time.

Specifically, the plunger 70 includes a plunger ball 71 having one end supported by the plunger ball socket 58 of the slide plate 50 and fixed to the end face of the slide plate via a pressing plate 60, a plunger center hole 72 for communicating the plunger hole 81 and the plunger ball socket 58, a tapered rod portion 73 having a conical outer peripheral surface, and a plunger portion 74 that is in clearance fit with the cylinder plunger hole wall and is reciprocatable therein, and the plunger ball 71 is supported by the plunger ball socket 58 of the slide plate 50 in a spherical shape and is slidable; the central hole 72 of the plunger is a large-aperture through hole structure and is used as an oil suction and/or discharge channel; at least one sealing ring is often arranged on the plunger part 74 for sealing liquid, the tapered rod part 73 is in a tapered shape which increases from the ball end of the plunger to the plunger part 74, and when the plunger 70 moves to a certain position, the tapered rod part 74 is in contact with the inner ring periphery of the plunger hole 81 to play a force transmission role. It should be noted that the plunger 70 is not limited to a tapered plunger type, and may include a rod-plunger with a ball-end or a spherical plunger with a universal joint.

Specifically, a plurality of plunger ball sockets 58 are provided at positions opposing the plungers 70 in the circumferential direction of the end surface of the slide plate 50 on the cylinder side, and as shown in fig. 7, 8 and 9, the plunger ball sockets 58 form recesses having an approximately hemispherical opening in the end surface of the slide plate 50, the plunger ball sockets 58 support the plunger balls 71 in a state of being uniformly distributed at intervals on the common circumference of the slide plate axial center 50C, and after the plungers 70 are attached to the plunger ball sockets 58, they are fixed to the end surface of the slide plate 50 by a pressing plate 60, so that the movement of the plungers 70 away from the end surface of the slide plate 50 is restricted. In particular, the means for fastening the plunger 70 to the front face of the slide plate 50 are also not limited to the use of a pressure plate, but, for example, a form-locking holding device (not shown) can also be provided on the slide plate 50, which can fasten the plunger ball 71 by a covering of more than 180 degrees.

As shown in fig. 7, a swash plate static pressure bearing surface 51 is provided on an end surface of the swash plate 50 facing the swash plate 40, a swash plate axis 50C forms a certain angle with the main shaft axis 10C, the swash plate static pressure bearing surface 51 is supported on the swash plate 40 and always slidably engages with the swash plate 40, a plurality of swash plate kidney holes 53 having a kidney shape are provided on the swash plate static pressure bearing surface 51, preferably, the swash plate kidney holes 53 are uniformly distributed on the swash plate static pressure bearing surface 51 centering on the swash plate axis 50C, and the swash plate kidney holes 53 are communicated to the plunger ball socket 58.

Further, a projected slide plate land 52 extending toward the swash plate 40 side along the slide plate axis 50C is provided on the end surface of the slide plate 50 facing the swash plate 40, the slide plate land 52 is constituted by a region surrounded by an inner diameter R1 and an outer diameter R2, the slide plate land 52 and the swash plate 40 support surface are slidably abutted against each other, a plurality of slide plate waist holes 53 are provided on the slide plate land 52 at positions corresponding to the plunger ball sockets 58, and the slide plate waist holes 53 are preferably distributed on the slide plate land 52 at regular intervals on a common circumference centering on the slide plate axis 50C.

The sliding plate convex table surface 52 and the bearing surface of the swash plate 40 form effective static pressure oil film support, a sealing part used for sealing oil is arranged on the sliding plate convex table surface 52, the sealing part is arranged on the inner periphery and the outer periphery of the sliding plate kidney-shaped hole 53 in a state of surrounding the sliding plate kidney-shaped hole 53, the sealing part comprises a sliding plate inner sealing part 55, a sliding plate outer sealing part 54 and a sliding plate interval sealing part 56, the sliding plate inner sealing part 55 is distributed on the radial inner side and the radial outer side of the sliding plate kidney-shaped hole 53, the sliding plate inner sealing part 55 is a region formed by surrounding the inner edge of the sliding plate kidney-shaped hole 53 and the inner diameter R1 of the sliding plate convex table surface 52, the sliding plate outer sealing part 54 is a region formed by surrounding the outer edge of the sliding plate kidney-shaped hole 53 and the outer diameter R2 of the sliding plate convex table surface 52, the sliding plate interval sealing part 56 is a region of the interval convex table surface between the adjacent sliding plate kidney-shaped holes 53, and a certain reasonable clearance is always kept between the sealing part of the sliding plate convex table surface 52 and the bearing surface of the swash plate 40 to ensure that the oil film support is kept, so that the sliding plate convex table surface is kept The oil film leakage is at a reasonable level.

In operation, hydraulic pressure acts on the plunger 70 and is further transmitted to the slide plate 50, and in general, the axial force of the plunger 70 acting on the slide plate 50 is greater than the sum of the supporting force of the swash plate 40 acting on the slide plate 50 through oil film reaction and the return force of the plunger 70, so that the slide plate 50 always slides against the swash plate 40 through a layer of oil film.

Considering that the initial sealing is still needed between the sliding plate and the swash plate when the plunger pump is started to build up the oil pressure as soon as possible, an initial sealing device is needed on the side of the flow distribution sliding plate pair.

Preferably, one of the initial sealing devices, as shown in fig. 12, is provided with a spring preloading device between the sliding plate 50 and the cylinder 80, and the spring preloading device enables a certain initial contact force between the flow distribution sliding plate pair and the flow distribution pair. The spring pre-tightening device comprises a central spring 100, a retainer ring 101 and a spherical hinge 102, wherein one end of the pre-tightening spring force of the central spring 100 acts on the pressure plate 60 through the spherical hinge 102 and is further transmitted to the sliding disc 50, and the other end of the pre-tightening spring force acts on the end part of the cylinder body and the port plate 90 through the retainer ring 101.

Preferably, another initial sealing device, as shown in fig. 1 and 2, may also be provided on said sliding plate 50 and/or cylinder block 80 with a restraining device having a function of limiting the movement of the sliding plate 50 of said port pair away from the swash plate 40 and limiting the movement of the cylinder block 80 of said port pair away from the port plate 90.

The restricting means further includes a swash plate stopper projecting outward on the side of the slide plate 50 closer to the slide plate static pressure bearing surface 51, and an engaging means 140 provided on the swash plate bearing stopper 41 a. The stopper portion 57 is used for limiting the movement of the third bearing 23, and the engaging means includes an engaging peripheral groove provided on the bearing stopper portion 41a adjacent to the third bearing 23 and a snap spring (not shown) provided on the engaging peripheral groove, which limits the slide plate from being away from the end surface of the swash plate 40 in such a manner as to restrict the outward movement of the third bearing 23.

It is also conceivable to arrange a spring washer (not shown) between the stop and the third bearing 23 or between the circlip and the third bearing 23, so that the restraint assembly, in addition to limiting the displacement of the slide plate away from the end face of the swash plate, also has a certain initial pretension to maintain the pretension of the slide plate and the swash plate. Similarly, the constraint mode of the constraint device 140 can also be realized by interference fit of the third bearing 23 and the swash plate support stop part 41a, and a clamping circumferential groove and a clamping spring matched with the clamping circumferential groove are arranged on the swash plate support stop part 41a and adjacent to the third bearing 23 to further perform a constraint function. On the cylinder side, the restriction device further comprises a circlip 141 for restricting the cylinder end from moving away from the thrust plate.

As shown in fig. 10, the swash plate 40 has a swash plate bearing surface 41 matching with a swash plate static pressure bearing surface 51, and in this embodiment, a kidney-shaped low-pressure distribution window 43 is provided on the swash plate bearing surface 41, and the low-pressure distribution window 43 may be provided as a plurality of windows having kidney shapes. In order to provide the swash plate 40 with a certain pre-pressure-increasing and pre-pressure-decreasing effect, a throttle groove or throttle hole 43a may be provided at the end of the low-pressure distribution window 43. Meanwhile, an oil inlet groove 48 is formed in the swash plate 40, and the oil inlet groove communicates the housing cavity 35 and the low-pressure flow distribution window 43 of the swash plate 40.

As shown in fig. 11, the other side of the swash plate 40 is provided with a cylindrical smooth arc surface 45 formed in a cylindrical shape. The housing 31 has a sliding arc surface (not shown) with the same radius as the sliding arc surface 45 of the swash plate cylinder, so that the sliding arc surface 45 of the swash plate cylinder always keeps a close contact state when sliding on the sliding arc surface of the housing 31. The cylindrical sliding arc surface 45 on the high-pressure side of the swash plate 40 is provided with a groove-shaped oil chamber 47a in a groove shape and a swash plate oil through hole 39, and the swash plate oil through hole 39 introduces high-pressure oil into the groove-shaped oil chamber 47a to form oil film support.

When the pump works, the oil flow is as follows: when oil is absorbed, one path of low-pressure oil entering from an oil inlet 33a of the rear end cover 33 enters the plunger hole 81 from a low-pressure flow distribution port 92 of the flow distribution plate 90, and the other path of low-pressure oil enters from the oil inlet groove 48 of the swash plate and sequentially passes through the low-pressure flow distribution window 43 of the swash plate, the waist-shaped hole 53 of the sliding plate, the central large hole of the conical plunger and the plunger hole; when oil is discharged, the sliding disc waist-shaped hole 53 at one side of the swash plate 40 is sealed by the swash plate supporting surface, and high-pressure oil only flows out from the plunger hole 81 side of the cylinder body through the high-pressure flow distribution port of the flow distribution disc 90 and is finally discharged from the oil outlet 33b of the rear end cover 33.

Example 2:

as shown in fig. 13, another embodiment of the present invention is shown, which is different from embodiment 1 in that an impeller 150 is provided on the outer periphery of a cylinder 80, and the structure described with reference to embodiment 1 is otherwise provided.

The impeller 150 is fixed to the cylinder 80 and rotates in synchronization with the cylinder. Under the action of the impeller, the oil inside the housing forms a certain oil pressure and moves directionally, i.e., the oil is driven towards the oil inlet groove 48 of the swash plate 40. The structure has the advantages that: firstly, the flow of hot oil in the cavity 35 of the shell is accelerated, so that the hot oil leaves the vicinity of the friction pair as soon as possible, and the influence of high temperature on the friction pair is reduced; and secondly, the side oil suction flow of the sliding disc is improved, and the oil suction performance is enhanced.

Example 3:

as shown in fig. 14 to 18, another embodiment of the present invention is shown, which is different from embodiment 1 in that the portions of the slide plate pair and the flow distribution pair which are opposed and abutted against each other are different, and the flow distribution passage is different therefrom, and the structure described in embodiment 1 can be otherwise referred.

The flow distribution pair comprises a cylinder body 80 and a flow distribution plate 90 abutted against the shell 31, the cylinder body 80 and the flow distribution plate 90 are supported in a hydrostatic manner and transmit axial force to the shell, the flow distribution pair is a one-way low-pressure flow distribution pair, the flow distribution pair comprises a cylinder body end part and the flow distribution plate 90 supported on the shell 31, the cylinder body end part and the end surface of the flow distribution plate 90 form a hydrostatic oil film support in clearance fit and keep sliding fit, a low-pressure flow distribution port 92 is arranged on one side of the flow distribution plate opposite to the low-pressure plunger hole, and when the pump sucks oil, low-pressure oil enters the cylinder plunger hole 81 from the cavity 35 of the pump shell through the low-pressure flow distribution port 92.

The flow distribution sliding disc pair is a bidirectional high-low pressure flow distribution sliding disc pair, the flow distribution sliding disc pair comprises a swash plate 40 and a sliding disc 50 supported on the swash plate 40, the swash plate 40 and the end face of the flow distribution disc 90 form a static pressure oil film support in clearance fit and the static pressure oil film support and the sliding disc 50 keep sliding fit, a support surface, opposite to the rear end cover 33, of the swash plate 40 is provided with a cylindrical sliding arc surface 45, a groove-shaped low pressure opening 46 and a groove-shaped high pressure opening 47 are formed in the cylindrical sliding arc surface 45 of the swash plate 40, and the groove-shaped low pressure opening 46 and the groove-shaped high pressure opening 47 are respectively communicated with an oil inlet 33a and an oil outlet 33b in the rear end cover 33 correspondingly.

When the pump works, the oil flow is as follows: when oil is absorbed, one path of low-pressure oil entering from the oil inlet 33a of the rear end cover 33 enters the plunger hole from the low-pressure distribution window 43 of the swash plate 40, the waist-shaped hole 53 of the sliding plate and the central large hole of the conical plunger, and the other path of low-pressure oil enters the plunger hole 81 from the low-pressure distribution port 92 of the distribution plate 90; when oil is discharged, the plunger hole of the cylinder block is sealed by the bearing surface of the valve plate, and high-pressure oil can only flow out from one side of the plunger hole 81 of the cylinder block through the conical plunger center hole 72, the sliding disc waist-shaped hole 53 and the groove-shaped high-pressure port 47 of the swash plate and is finally discharged from the oil outlet 33b of the rear end cover.

Example 4:

as shown in fig. 19, the main difference from the other embodiments is that the embodiment is a non-through-shaft type axial plunger pump. The main shaft axis 10C of the main shaft 10 coincides with the cylinder body axis 80C of the cylinder body 80, one end of the main shaft 10 extends out of the housing 31 and is supported on the first bearing 21, and the other end of the main shaft is supported in the cylinder body 80 in a cantilever manner and is connected with the cylinder body 80 through a key.

At this time, if the plunger pump is a variable displacement pump, a variable displacement mechanism for variable displacement oscillation may be provided on the rear end cover 33, the variable displacement mechanism may include a spool 33c slidable in an end seat, a shaft pin 49 of the swash plate 40 may be connected to the spool 33c in a relatively tiltable state, and the swash plate 40 and the spool 50 may be rotated in the housing cavity 35 via the shaft pin 49 by the variable displacement mechanism.

Example 5:

as shown in fig. 19, the main difference from the other embodiments is that a thrust plate 24 is interposed between a sliding plate 50 and a swash plate 40 in a sliding plate pair, the sliding plate 51 is supported on the thrust plate 24 and is in sliding engagement with the thrust plate 24, the thrust plate 90 is fixed to the swash plate 40 by means of pins or the like, a high-pressure port and a low-pressure port (not shown) are provided in the thrust plate 24, the high-pressure port and the low-pressure port are respectively communicated with a low-pressure port 43 and a high-pressure port 44 in the swash plate 40, and the interposition of the thrust plate 24 between the sliding plate 50 and the swash plate 40 is advantageous in that the later replacement of the thrust plate 24 is easier and more cost-effective than the replacement of the swash plate 40.

The foregoing is a more detailed description of the present invention that is presented in conjunction with specific preferred embodiments, and is not intended to limit the practice of the invention to those descriptions. For those skilled in the art to which the invention pertains, numerous and varied simplifications or substitutions can be made without departing from the spirit and scope of the invention, and all such modifications and changes as fall within the scope of the claims are intended to be embraced therein.

Claims (11)

1. A sliding-disk axial plunger pump, characterized in that: the oil distribution sliding disc pair comprises a flow distribution sliding disc pair, a plunger pair and a flow distribution pair, wherein the flow distribution sliding disc pair comprises a swash plate (40) and a sliding disc (50) supported on the swash plate (40), the sliding disc (50) is of an integral structure, a sliding disc waist-shaped hole (53) communicated with a plunger center hole (72) of the plunger pair is formed in the sliding disc (50), a low-pressure oil distribution hole (43) serving as an oil inlet channel is formed in a bearing surface of the swash plate (40) opposite to the low-pressure plunger hole, a bearing surface of the swash plate (40) opposite to the high-pressure plunger hole and the sliding disc waist-shaped hole (53) form a static pressure bearing, the low-pressure oil distribution hole (43) is communicated with a shell cavity (35) through an oil inlet groove (48) formed in the swash plate (40), when a plunger pump works, a main shaft drives a cylinder body to synchronously rotate, the sliding disc (50) is driven to slide on the swash plate (40) through the plunger, and low-pressure oil flows from a low-pressure flow distribution port (92) of the flow distribution disc (90) and an oil inlet groove (48) or a low-pressure port (48) of the swash plate (40) 46) The two ways enter a cylinder plunger hole (81) of a cylinder body (80), and high-pressure oil is discharged from a high-pressure flow distribution port (93) of a flow distribution plate (90) or a groove-shaped high-pressure port (47) of a swash plate (40) in a single way, so that the suction and discharge of the hydraulic oil are realized.

2. The sliding disc axial plunger pump of claim 1, wherein: be provided with on sliding tray (50) along its axle to sliding tray convex table face (52) that sloping cam plate (40) one side extended sliding tray waist shape hole (53) and the sealing that is used for sealed fluid are provided with on sliding tray convex table face (52), the sealing sets up the inside and outside periphery in sliding tray waist shape hole (53) with the state that surrounds sliding tray waist shape hole (53), sealing (56) are separated at sliding tray including setting up in the radial inside and outside sliding tray sealing (55), sliding tray external seal portion (54) in sliding tray waist shape hole (53) and setting between adjacent sliding tray waist shape hole (53).

3. The sliding disc axial plunger pump of claim 1, wherein: the flow distribution pair is a bidirectional high-low pressure flow distribution pair, the flow distribution pair comprises a cylinder body end and a flow distribution disc (90) supported on a rear end cover (33), the cylinder body end and the flow distribution disc (90) end form a static pressure oil film support in clearance fit, the flow distribution disc (90) is provided with a low pressure flow distribution port (92) and a high pressure flow distribution port (93) which are separated, and the low pressure flow distribution port (92) and the high pressure flow distribution port (93) are respectively communicated with an oil inlet (33a) and an oil outlet (33b) of the rear end cover.

4. A sliding-disc axial piston pump according to claim 3, characterized in that: the flow distribution sliding disc pair is a one-way low-pressure flow distribution sliding disc pair, the flow distribution sliding disc pair comprises a swash plate (40) and a sliding disc (50) supported on the swash plate (40), the swash plate (40) and the end face of the sliding disc (50) form a static pressure oil film support in clearance fit, the static pressure oil film support and the sliding disc (50) are in sliding fit, a low-pressure flow distribution window (43) is arranged on one side of the sliding disc (50) opposite to a low-pressure plunger hole, and when oil is pumped, low-pressure oil in the shell cavity (35) flows through the low-pressure flow distribution window (43), the sliding disc waist-shaped hole (53), the plunger center hole (72) and the cylinder plunger hole (81) in sequence.

5. The sliding disc axial plunger pump of claim 1, wherein: the flow distribution pair is a one-way low-pressure flow distribution pair, the flow distribution pair comprises a cylinder end part and a flow distribution disc (90) supported on a shell (31), the cylinder end part and the end surface of the flow distribution disc (90) form a static pressure oil film support in clearance fit, the static pressure oil film support and the flow distribution disc support keep sliding fit, one side of the flow distribution disc (90) opposite to the low-pressure plunger hole is provided with a low-pressure flow distribution port (92), and when oil is pumped, low-pressure oil enters the cylinder plunger hole (81) from a pump shell cavity (35) through the low-pressure flow distribution port (92).

6. The sliding disc axial plunger pump of claim 5, wherein: the flow distribution sliding disc pair is a bidirectional high-low pressure flow distribution sliding disc pair, the flow distribution sliding disc pair comprises a swash plate (40) and a sliding disc (50) supported on the swash plate (40), a static pressure oil film support in clearance fit is formed on the end faces of the swash plate (40) and the flow distribution disc (90), the static pressure oil film support and the static pressure oil film support are in sliding fit, a cylindrical sliding arc face (45) is formed on a supporting face, opposite to the rear end cover (33), of the swash plate (40), a groove-shaped low-pressure port (46) and a groove-shaped high-pressure port (47) in groove shapes are formed in the cylindrical sliding arc face (45) of the swash plate (40), and the groove-shaped low-pressure port (46) and the groove-shaped high-pressure port (47) are correspondingly communicated with an oil inlet (33a) and an oil outlet (33b) in the rear end cover respectively.

7. The sliding disc axial plunger pump of claim 1, wherein: a thrust disc (24) is clamped between the sliding disc (50) and the swash plate (40), the sliding disc (50) is supported on the thrust disc (24) and keeps sliding fit with the thrust disc (24), a low-pressure flow distribution port and/or a high-pressure flow distribution port are/is arranged on the thrust disc (24), and the flow distribution port of the thrust disc (24) is communicated with a flow distribution oil groove (42) of the swash plate (40) and a slide disc kidney-shaped hole (53) of the sliding disc (50).

8. The sliding disc axial plunger pump of claim 1, wherein: a spring pre-tightening device is arranged between the sliding disc (50) and the cylinder body (80), and a certain initial contact force is formed between the flow distribution sliding disc pair and the sliding disc pair through the spring pre-tightening device.

Or, a restraining device is arranged on the sliding plate (50) and/or the cylinder body (80), and the restraining device is used for limiting the sliding plate (50) of the distribution sliding plate pair to move away from the swash plate (40) and limiting the cylinder body (80) of the distribution stopping pair to move away from the distribution plate (90).

9. The sliding disc axial plunger pump of claim 1, wherein: an impeller device is arranged on the cylinder body (80) and directionally drives low-pressure oil to accelerate from the shell cavity (35) into the plunger hole (81).

10. A sliding disc axial piston pump according to any of claims 1 to 9, characterized in that: the sliding disc type axial plunger pump is of a through shaft type structure and specifically comprises a main shaft (10), a shell (31), a first bearing (21), a second bearing (22), a plunger (70), a cylinder body (80), a valve plate (90) and a rear end cover (33), the rear end cover (33) is provided with a communicating groove (37) communicated with the shell cavity (35), the main shaft axis (10C) of the main shaft (10) is superposed with the cylinder body axis (80C) of the cylinder body (80), one end of the main shaft (10) penetrates through the flow distribution sliding disc pair to extend out of the shell (31) and is supported on the first bearing (21), the other end penetrates through the flow distribution pair and is supported on the second bearing (22), the cylinder body (80) is supported on the main shaft (10) and synchronously rotates with the main shaft through key connection, the plunger (70) reciprocates in a plunger cavity of the cylinder body (80) to realize the oil suction and discharge work of the pump.

11. A sliding disc axial piston pump according to any of claims 1 to 9, characterized in that: the sliding disc type axial plunger pump is of a non-through shaft type structure and specifically comprises a main shaft (10), a shell (31), a first bearing (21), a plunger (70), a cylinder body (80), a sliding disc (90) and a rear end cover (33), wherein a communicating groove (37) communicated with a shell cavity (35) is formed in the rear end cover (33), a main shaft axis (10C) of the main shaft (10) is overlapped with a cylinder body axis (80C) of the cylinder body (80), one end of the main shaft (10) penetrates through a flow distribution pair to extend out of the shell (31) and is supported on the first bearing (21), a cantilever at the other end of the main shaft is supported in the cylinder body (80) and is in key connection with the cylinder body (80), the main shaft (10) and the cylinder body (80) rotate synchronously, and the plunger (70) does reciprocating motion in a plunger cavity of the cylinder body (80) to achieve oil sucking and discharging work of the pump.

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