CN209855979U

CN209855979U - Axial plunger pump or motor

Info

Publication number: CN209855979U
Application number: CN201920316236.4U
Authority: CN
Inventors: 钟彪
Original assignee: Individual
Current assignee: Shanghai Qiangtian Drive Technology Co ltd
Priority date: 2019-03-13
Filing date: 2019-03-13
Publication date: 2019-12-27
Anticipated expiration: 2029-03-13

Abstract

The utility model discloses an axial plunger pump or motor contains sloping cam plate, supporting sliding plate, cylinder body on the sloping cam plate and follows cylinder body one end male plunger, the sliding plate is overall structure, the terminal surface of sliding plate and sloping cam plate opposition is provided with the static pressure bearing surface, be provided with a plurality of grease chambers on the static pressure bearing surface, another terminal surface of sliding plate is provided with a plurality of plunger ball sockets be provided with the large aperture oil through hole of intercommunication plunger ball socket and grease chamber on the sliding plate, be provided with the communicating oil distribution groove of business turn over hydraulic fluid port on the sloping cam plate, cylinder body other end tip and plunger hole correspond the position and are provided with the check valve, check valve intercommunication cylinder body plunger hole, the check valve only allows fluid to get into the plunger hole from casing second cavity. The utility model discloses to join in marriage class, variable slope, supporting function integration in the sliding tray is vice, reduced the vice quantity of friction to make the structure simplify greatly, add the check valve simultaneously at the cylinder body tip, can improve from the priming ability, reduce fluid temperature and cancel oil return line.

Description

Axial plunger pump or motor

Technical Field

The utility model belongs to the technical field of hydraulic transmission and control, in particular to axial plunger pump or motor.

Background

The axial plunger pump and the motor are one of the most widely used hydraulic components in modern hydraulic transmission, and the hingeless inclined shaft pump and the slipper 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. These two pumps or motors are now competing, and each is constantly improving and developing.

As shown in fig. 1, the typical structure of a conventional non-through-shaft swash plate type axial plunger pump or motor includes a swash plate 40, a shoe 120, a plunger 70, a cylinder block 80, a port plate 90, a main shaft 10, a center spring 100, a return plate 130, and the like, wherein one end of the main shaft 10 is supported by a bearing at one end, the other end thereof penetrates through the port plate 90 and is keyed to the cylinder block 80, the center spring 100 presses the shoe 120 via a sleeve 102 and a steel ball 101, the center spring 100 presses the cylinder block and the port plate via an outer sleeve 103, a cylinder sleeve 84 is provided on an outer circumferential surface of the cylinder block 80, and a second bearing 22 is interposed between the cylinder sleeve 84 and a housing 32. The swash plate type axial plunger pump has the advantages of simple and compact structure, small volume and light weight, realizes stepless variable through the swing of the swash plate, is convenient to change the variable, has more variable forms, small inertia of the variable and high variable response speed, and can be connected with an oil supplementing pump at the shaft end to form a series pump or a motor; swash plate axial piston pumps, however, also have their disadvantages: 1. the number of key friction pairs of the swash plate type axial plunger pump is large, so that the leakage of the swash plate type axial plunger pump is increased, the volume efficiency of the swash plate type axial plunger pump is reduced, and meanwhile, the failure of the friction pairs also causes important factors of the working failure of the pump or the motor; 2. under the action of hydraulic pressure, the lateral force generated by a swash plate of the swash plate type axial plunger pump to a plunger is large, the lateral component force is transmitted to a cylinder body and a main shaft through the plunger, a wedge-shaped gap is generated between the cylinder body and a valve plate, the volume loss of the pump is increased, the sealing surface between the cylinder body and the valve plate is locally contacted, the surface burn between the cylinder body and the valve plate is caused, and the function of the pump is completely lost. 3. The heat generated by the friction pair causes the temperature of the oil to rise, and further affects the efficiency of the pump, the reliability of the friction pair, the performance of the oil and the like. In order to reduce the temperature of the oil, additional cooling equipment is required, and the cost is increased. 4. The existing non-through shaft swash plate type axial plunger pump is limited by the size of an oil inlet, and most of the non-through shaft swash plate type axial plunger pumps are open oil paths, so that the self-priming capability of the non-through shaft swash plate type axial plunger pump is relatively poor. 5. The existing swash plate type axial plunger pump is provided with an oil return oil way independently, and parts such as an oil return pipeline of the plunger pump need to be additionally arranged, so that the manufacturing and using cost is increased.

SUMMERY OF THE UTILITY MODEL

The invention of the utility model aims to: in order to solve the problems of the existing swash plate type axial plunger pump or motor, a novel axial plunger pump or motor structure is provided, and the axial plunger pump or motor aims to reduce the number of friction pairs, reduce the lateral force of a plunger, improve the self-absorption capacity of the plunger, reduce the temperature of oil, facilitate the variation and reduce the sensitivity of oil pollution.

The utility model discloses technical scheme implementation of technique: an axial plunger pump or motor, characterized in that: comprises a swash plate, a sliding disc supported on the swash plate, a cylinder body and a plunger, wherein the sliding disc is of an integral structure, the end surface of the sliding disc opposite to the swash plate is provided with a static pressure bearing surface, the other end surface of the sliding disc is provided with a plurality of plunger ball sockets, the sliding disc is provided with an oil through hole for communicating the plunger ball socket and the static pressure bearing surface, the swash plate is provided with a flow distribution oil groove, the oil distribution groove is communicated with an oil inlet and an oil outlet which are arranged on the end part of one side of the plunger pump or the motor shell close to the swash plate, one end of the plunger is arranged in the plunger ball socket, the other end of the plunger is inserted from the opening end of the cylinder body, one end of a plunger center hole in the plunger is communicated with the oil through hole, the other end of the plunger center hole is communicated with the plunger hole in the cylinder body, the closed end of the cylinder body is provided with a one-way valve, the one-way valve is used for communicating a plunger hole of the cylinder body with an inner cavity of the shell, and the one-way valve only allows hydraulic oil to enter the plunger hole from the cavity of the shell.

Axial plunger pump or motor, its the check valve contains the valve body be connected with the cylinder body, set up at the inside case of valve body, fix retaining ring on the valve body and set up the spring between case and retaining ring, the check valve only allows hydraulic oil to flow to the plunger hole direction of cylinder body from the second cavity of casing.

Axial plunger pump or motor, its the oil groove that flows that joins in marriage that sets up on the sloping cam plate contains and advances, the low pressure oil groove that flows that the oil-out communicates respectively and high pressure oil groove that flows, during the oil absorption, low pressure fluid gets into the plunger hole of cylinder body from the check valve of low pressure oil groove that flows and cylinder body tip, during the oil extraction, high pressure fluid only discharges to the oil-out from high pressure oil groove that flows.

Axial plunger pump or motor, it is in be provided with a plurality of grease chambers on the static pressure bearing surface, the opening of joining in marriage on the sloping cam plate terminal surface with the sliding tray opposition of flow oil groove takes shape to be the low pressure of waist shape and the high pressure of waist shape and joins in marriage a class window, high, low pressure join in marriage a class window with grease chamber intermittent type intercommunication, have on the sloping cam plate and take shape to be columniform cylindrical bearing face with the bearing surface of plunger pump or motor housing's end cover opposition, have the flute profile low pressure mouth and the flute profile high-pressure mouth of configuration for the flute profile on the cylindrical bearing face of sloping cam plate, flute profile low pressure mouth and flute profile high-pressure mouth correspond the intercommunication with oil inlet and oil-out respectively.

Axial plunger pump or motor, its the intercommunication notch that has intercommunication flute profile low pressure mouth and casing second cavity on the cylinder supporting surface of sloping cam plate.

Axial plunger pump or motor, its plunger centre bore on oil through hole on the sliding plate and the plunger is large aperture main oilhole structure.

Axial plunger pump or motor, its the oil groove that flows that sets up on the sloping cam plate only sets up the high pressure oil groove that flows that feeds through with the oil-out, during the oil absorption, low pressure fluid gets into the plunger hole of cylinder body from the check valve of cylinder body tip, during the oil extraction, high pressure fluid is from high pressure oil groove to the oil-out that flows.

Axial plunger pump or motor, its the opening of joining in marriage a class oil groove on the sloping cam plate terminal surface with the sliding tray opposition takes shape to be the high pressure of waist shape and joins in marriage a class window, the high pressure join in marriage a class window with grease chamber intermittent type intercommunication, join in marriage a class oil groove and take shape to the flute profile high-pressure port of flute profile for opening on the cylindrical bearing surface with the end cover opposition, flute profile high-pressure port corresponds the intercommunication with the oil-out.

Axial plunger pump or motor, its the plunger contains the connecting rod plunger or the spherical plunger's of universal hinge of connecting rod plunger or area that all is provided with the bulb of taking the toper structure both ends, but plunger one end cylinder body reciprocating sliding's mode inserts relatively the plunger of cylinder body is downthehole, and the other end is kept away from the state limited and that can topple over with relative sliding plate terminal surface and is fixed on the plunger ball socket of sliding plate, be provided with the large aperture plunger centre bore in intercommunication plunger ball socket and plunger hole on the plunger.

Axial plunger pump or motor, its press from both sides between sliding tray and the sloping cam plate and be equipped with the valve plate, the sliding tray supporting just keeps sliding fit with the valve plate on the valve plate, be provided with high, low pressure valve port or high-pressure valve port on the valve plate, the valve port of valve plate is linked together with the oil distribution oil groove of sloping cam plate and the grease chamber of sliding tray.

Based on the technical scheme, the beneficial effects of the utility model are that:

1. the utility model discloses to join in marriage class, variable slope, static pressure supporting function integration in the sliding tray is vice, and main friction is vice for sliding tray is vice and the plunger is vice, compares current slide shoe swash plate axial plunger pump technique, has following advantage: firstly, a flow distribution pair is reduced, so that the leakage of oil is reduced, and the volume efficiency is improved; secondly, the lateral force of the plunger is greatly reduced, and the overturning phenomenon of the cylinder body is eliminated or reduced; both of these advantages integrate the advantages of a bent axis pump or motor. Compared to a bent-axis pump or motor: firstly, the variable of the pump or the motor is realized by changing the inclination mode of the swash plate, and the variable is convenient and has faster response speed because the inertia of the variable of the swash plate is small; secondly, the structure is simple and compact, the volume is small, and the weight is light; these two advantages integrate the advantages of current slipper swash plate axial plunger pumps.

2. The utility model discloses an axial plunger pump or motor sets up the oil feed passageway at the cylinder body tip, during the oil absorption, can pass through the check valve with the fluid in the casing cavity and get into the plunger hole, make it participate in the hydraulic pressure work system, and such benefit lies in: firstly, the oil takes away heat generated by each part of the pump in time, and the oil temperature in the pump is prevented from rising to cause failure; secondly, an oil suction channel can be added, and the self-priming capacity of the pump is improved; and thirdly, an oil return pipeline and a cooling device of the pump can be eliminated, and the manufacturing and using cost of the pump is reduced.

3. The utility model discloses an axial plunger pump or motor can make the structure simplify greatly, and the size is littleer, the structure is compacter, and the weight of pump or motor is littleer, has consequently improved its unit mass power density. The structure enables the cylinder body to be 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.

4. The utility model integrates the functions of flow distribution, variable inclination and static pressure support in the sliding plate pair, and the sliding plate ball socket and the plunger ball head can relatively incline in the working process, so that the sliding plate can self-adapt to various inclinations such as inclined plate inclination, cylinder body inclination and the like, the sliding plate can always cling to the inclined plate to complete the functions of flow distribution, variable inclination, support and the like, and the occurrence of wedge-shaped gaps is avoided; simultaneously, compare and change the cylinder body, it is easier, more economical to change sliding plate or valve plate.

5. The utility model discloses oil through hole, plunger centre bore on the well sliding tray are the large aperture, consequently can prevent the jam of greasy dirt, have reduced the sensitivity of greasy dirt, and large aperture plunger centre bore has reduced the quality of plunger simultaneously, helps reducing the centrifugal force effect of plunger.

6. The utility model provides a sliding tray structure is overall structure, has replaced a plurality of independent piston shoes among the prior art and has utilized the structure of return stroke dish return stroke, the utility model provides a plunger is connected more reliably with sliding tray, sliding tray and pressure disk, has avoided piston shoe neck and shoulder wearing and tearing among the prior art, has sheared destruction and return stroke dish drilling position to take place phenomenons such as fracture to the operational reliability of swash plate type plunger pump or motor has been 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.

Drawings

Fig. 1 is a schematic structural diagram of a prior art oblique axis type axial plunger pump or motor.

Fig. 2 is a schematic diagram of the axial plunger pump or motor of the present invention.

Fig. 3 shows an embodiment of the present invention of a middle axial plunger pump or motor.

Fig. 4 is a cross-sectional view a-a of the axial piston pump or motor of fig. 3 according to the present invention.

Fig. 5 is a plan view of one end of the middle slide plate of the present invention.

Fig. 6 is a cross-sectional view of the sliding plate structure B-B in fig. 5 according to the present invention.

Fig. 7 is a plan view of the other end of the middle sliding plate of the present invention.

Fig. 8 is a plan view of the bearing surface of one end of the swash plate opposite the slide plate according to the present invention.

Fig. 9 is another plan view of the bearing surface of the swash plate opposite the slide plate according to the present invention.

Fig. 10 is a plan view of the swash plate of the present invention opposite to the end cover.

Fig. 11 is a plan view of the swash plate with communication notches opposite the end caps according to the present invention.

Fig. 12 is a cross-sectional view of the swash plate of fig. 10 and 11 according to the present invention.

FIG. 13 is a plan view of the swash plate with high-pressure flow grooves

FIG. 14 is a plan view of the other end of the swash plate with high-pressure flow grooves

Fig. 15 shows another embodiment of an axial piston pump or motor of the present invention incorporating a port plate.

Fig. 16 is a plan view of one of the port plates of the embodiment of fig. 13 according to the present invention.

Fig. 17 is a plan view of another port plate of the embodiment of fig. 13 according to the present invention.

The labels in the figure are: 10 is a main shaft, 10C is a main shaft axis, 11 is a bearing support portion, 12 is a main shaft shoulder, 21 is a first bearing, 22 is a second bearing, 31 is a front shell, 32 is a shell body, 33 is an end cover, 33a is an oil inlet, 33b is an oil outlet, 33C is a slide valve, 33d is a flow passage, 33e is a sliding arc surface, 34 is a first cavity, 35 is a second cavity, 40 is a swash plate, 41 is a swash plate support surface, 42 is a flow distribution oil groove, 42a is a low-pressure flow distribution oil groove, 42b is a high-pressure flow distribution oil groove, 43 is a low-pressure flow distribution window, 43a is a throttling groove or hole, 44 is a high-pressure flow distribution window, 45 is a cylindrical support surface, 46 is a groove-shaped low-pressure port, 47 is a groove-shaped high-pressure port, 48 is a communicating oil chamber notch, 49 is a shaft pin, 50 is a sliding disc, 50C is a sliding disc axis, 51 is a static pressure support surface, 52 is a boss surface, 53a through hole, 55 is an inner sealing part, 56 is a spacing sealing part, 58 is a plunger ball socket, 60 is a pressure plate, 70 is a plunger, 71 is a plunger ball, 72 is a plunger center 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 spindle assembly hole, 83 is a communication hole, 84 is a cylinder sleeve, 80C is a cylinder body center axis, 90 is a flow distribution plate, 91 is a flow distribution bearing surface, 92 is a low pressure flow distribution port, 93 is a high pressure flow distribution port, 100 is a center spring, 101 is a steel ball, 102 is a sleeve, 103 is an outer sleeve, 110 is a check valve, 111 is a valve body, 112 is a valve core, 113 is a spring, 114 is a retainer ring, 120 is a sliding shoe, and 130 is a return plate.

Detailed Description

The present invention will be described in detail 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 convenience of description, embodiments of the present invention are shown in a typical orientation such that when the central axis of the main shaft of an axial piston pump or motor is resting horizontally, with the coupling end side of the main shaft to the left and the 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, merely to facilitate description and simplify the description, but not to indicate or imply that the device or element being referred to must have a particular orientation, and a particular orientation configuration and operation, it being understood that the invention can be manufactured, stored, shipped, used, and sold in an orientation other than the position described.

For convenience of explanation, the axial plunger pump will be described with emphasis on the structure of the axial plunger motor, and the structure of the axial plunger motor may be changed as necessary with reference to the structure of the axial plunger pump, but it should be noted that all axial plunger pumps or motors utilizing the principles of the present invention may be considered to be included.

Example 1:

as shown in fig. 2 to 9, in the illustrated preferred embodiment, the axial plunger pump of the present invention is an embodiment of a non-through-shaft axial plunger pump or a motor, the axial plunger pump includes a main shaft 10, a housing, a first bearing 21, a swash plate 40, a sliding plate 50, a plunger 70 and a cylinder 80, the main shaft 10C of the main shaft 10 coincides with the cylinder center 80C of the cylinder 80, one end of the main shaft 10 is supported on the first bearing 21, the other end of the main shaft is cantilever-supported on the cylinder 80 and is connected with the cylinder 80 by a key, a static pressure bearing surface 51 of the sliding plate 50 is supported on the swash plate 40 and is tightly fitted with a working surface of the swash plate 40, one end of the sliding plate 50 is provided with a plurality of kidney-shaped oil chambers 53a, the other end of the sliding plate 50 is provided with a plurality of plunger ball sockets 58, the sliding plate 50 is provided with a large-diameter oil through hole 53 communicating the plunger ball sockets 58 and the oil chambers 53a, one end of a large-aperture plunger center hole 72 inside the plunger 70 is communicated with the oil through hole 53, the other end of the large-aperture plunger center hole is communicated with a plunger hole 81 in the cylinder body 80, the swash plate 40 is provided with a flow distribution oil groove 42 communicated with the oil inlet 33a and the oil outlet 33b, the other end of the cylinder body 80 close to the first bearing 21 is provided with a one-way valve 110 only allowing oil to enter the plunger hole 81 from the cavity of the shell, and under the reciprocating action of the plunger, low-pressure oil flows in from a flow distribution groove 42 and the one-way valve 110 of the swash plate and flows out from the flow distribution groove 42 to finish the suction and discharge of. Obviously, the structural principle can also be applied to a through-shaft axial plunger pump or motor.

Wherein, it is required to explain that the large aperture in large aperture logical oilhole 53 and the large aperture plunger centre bore 72 is for the size of corresponding position aperture in the existing structure, and the aperture in the existing structure is long and thin aperture, and high-pressure fluid in the plunger hole is only the subtotal through this hole, and under the effect in long and thin aperture, and oil hydraulic pressure reduces, and consequently the aperture in the existing structure mainly plays throttle, decompression effect to fluid, the utility model provides a large aperture logical oilhole 53 and large aperture plunger centre bore 72 are as main oilhole structure, and the suction and the discharge of hydraulic oil all flow through this main oilhole structure, and fluid does not have obvious pressure drop through large aperture logical oilhole 53 and large aperture plunger centre bore 72, and its structure has essential difference consequently. Specifically, in the present embodiment, the hole diameter of the oil passage hole 53 is increased to be close to or equal to the width-direction dimension of the kidney oil chamber 53a, as compared with the hole diameter of the corresponding portion in the conventional structure.

In this embodiment, the housing is a three-part structure, and includes a front shell 31 with an opening at one end, a hollow shell 32, and an end cover 33 connected to the shell, where the front shell 31 has a first cavity 34 for accommodating the first bearing 21, the shell 32 has a second cavity 35 for accommodating the cylinder block 80 and for accommodating the flow distribution sliding plate pair, the end cover 33 is used to close the opening at one end of the shell 32, the shell 32 is respectively connected to the front shell 31 and the end cover 33 through bolts, and the end cover 33 is provided with an oil inlet 33a and an oil outlet 33b of the pump, a flow passage 33d communicated with the swash plate flow distribution oil groove 42, and a sliding arc surface 33e for supporting the swash plate 40. When the axial piston pump is a variable displacement pump, a variable displacement mechanism for variable displacement oscillation may be provided on the end cover 33 or the housing, the variable displacement mechanism including a spool 33c slidable in an end seat, and a shaft pin 49 of the swash plate 40 is connected to the spool 33c in a relatively tiltable state, and the swash plate 40 and the spool 50 are rotatable in the second cavity 35 via the shaft pin 49 by the variable displacement mechanism. In particular, the housing of the axial piston pump may be configured as a two-body structure, i.e., the front housing 31 and the housing body 32 are formed as a single body, as shown in fig. 15.

The main shaft 10 is cylindrical and penetrates through the first cavity 34 of the front shell 31, the main shaft 10 is provided with a bearing support part 11, a first bearing 21 is clamped between the bearing support part 11 and the front shell 31, one end of the main shaft 10 extends out of the shell to be used for externally connecting a prime mover (or load) and is supported on the front shell 31 through the first bearing 21, the other end of the main shaft is in cantilever support with a cylinder body 80 and is in key connection with the cylinder body 80, the main shaft 10 freely rotates around the axis of the main shaft through the first bearing 21, the first bearing 21 at least comprises a radial thrust ball bearing or a tapered roller bearing or a thrust bearing, and a main shaft blocking shoulder 12 is arranged on the main shaft close to the end part of the.

The cylinder body 80 has a cylindrical configuration with a circular cross section in the radial direction and is accommodated in the second cavity 35 of the housing body 32, and the cylinder body 80 has a plurality of plunger holes 81 circumferentially and uniformly distributed about a cylinder body center axis 80C and a spindle fitting hole 82 at the center for accommodating a spindle, and preferably, the number of the plunger holes is generally set to 7 or 9. The main shaft 10 passes through a main shaft fitting hole 82 of the cylinder block 80 and is connected to the cylinder block 80 with a connection key provided on the outer circumferential surface of the shaft body, and the cylinder block 80 is supported on the main shaft 10 so as to move synchronously with the main shaft 10.

The other end of the cylinder 80 is provided with a communication hole 83 communicated with the plunger hole 81, the communication hole 83 is provided with a check valve 110, the check valve 110 is fixedly connected with the cylinder 80, the check valve 110 comprises a valve body 111 fixedly connected with the cylinder 80, a valve core 112 arranged inside the valve body 111, a retaining ring 114 fixed on the valve body 111 and a spring 113 arranged between the valve core 112 and the retaining ring 114, the check valve 110 only allows low-pressure oil to flow into the plunger hole 81 from the second cavity 35 of the housing, namely when the cylinder 80 is in an oil absorption state, the valve core 112 of the check valve 110 is opened, the low-pressure oil enters the plunger hole 81 from the second cavity 35 of the housing, and when the cylinder 80 is in an oil discharge state, the valve core 112 of the check valve 110 is closed.

When the pump works, the end of the cylinder 80 is abutted against the main shaft shoulder 12 and rotates synchronously with the main shaft 10, and the axial hydraulic pressure and the acting force of the central spring are transmitted to the radial thrust ball bearing or the tapered roller bearing or the thrust bearing 21b through the main shaft shoulder 12 and further transmitted to the shell.

It should be noted that the transmission of the axial load by the cylinder 80 through the spindle shoulder 12 is not a condition limiting the application thereof, and it is possible to alternatively, for example, the cylinder 80 directly abuts on the radial thrust bearing 21b and transmits the axial force to the housing 32, as will be apparent to those skilled in the art.

The utility model has obvious difference with the prior art that: the end part of the cylinder body 80 is not provided with a valve plate, so that a friction pair is reduced, the volume efficiency is improved, and a space is reserved for arranging a one-way valve; the end part of the cylinder body 80 does not need to be precisely machined, so that the manufacturing and using cost is reduced; the end of the cylinder body 80 is not provided with a port plate, and even if partial lateral force exists, the problems of failure and the like caused by eccentric wear can be avoided.

The plunger 70 includes a plunger ball 71 having one end supported on the plunger ball socket 58 of the slide plate 50 and fixed to the end face of the slide plate via the 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 which is in clearance fit with the cylinder plunger hole wall and is reciprocatable therein. The plunger ball 71 is spherical and is slidably supported by the plunger ball socket 58 of the slide plate 50; the central hole 72 of the plunger is a large-aperture through hole structure and is used as an oil suction and 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 is gradually increased 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 peripheral surface of the plunger hole 81 of the cylinder body 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.

A plurality of plunger ball sockets 58 are provided at positions facing the plungers 70 in the circumferential direction of the end surface of the slide plate 50 facing the cylinder, the plunger ball sockets 58 form recesses having substantially hemispherical openings 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 along the common circumference of the slide plate axis 50C, and after the plungers 70 are attached to the plunger ball sockets 58, the plungers 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 pressure plates, 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. 5, 6 and 7, a static pressure bearing surface 51 is provided on an end surface of the swash plate 50 facing the swash plate 40, the swash plate axis 50C forms a certain angle with the main shaft axis 10C, and the static pressure bearing surface 51 is supported on the swash plate 40 and always keeps a sliding engagement with the swash plate 40. The hydrostatic bearing surface 51 is provided with a plurality of oil chambers 53a in a waist shape, preferably, the oil chambers 53a are uniformly distributed on the hydrostatic bearing surface 51 centering on a sliding plate axis 50C, and the sliding plate 50 is provided with large-aperture oil through holes 53 communicating the plunger ball sockets 58 and the oil chambers 53 a.

Further, a projecting boss surface 52 extending toward the swash plate 40 side along the swash plate axis 50C is provided on an end surface of the slide plate 50 facing the swash plate 40, the boss surface 52 is formed by a region surrounded by an inner diameter R1 and an outer diameter R2, and the boss surface 52 of the slide plate and a bearing surface of the swash plate 40 are slidably in contact with each other. A plurality of oil chambers 53a are provided in the boss surface 52 at positions corresponding to the plunger ball sockets 58, and the oil chambers 53a are preferably distributed on the boss surface 52 at regular intervals on a common circumference centering on the slide plate axis 50C.

Wherein, an effective static pressure oil film support is formed between the boss surface 52 and the bearing surface of the swash plate 40, the boss surface 52 is provided with a seal portion for sealing oil, the seal portion is provided on the inner and outer peripheries of the oil chamber 53a in a state of surrounding the oil chamber 53a, the seals comprise an inner seal 55 distributed radially inside and outside the oil chamber 53a, an outer seal 54 and a spacer seal 56 distributed between adjacent oil chambers 53a, the inner seal portion 55 is a region surrounded by the inner edge of the oil chamber 53a and the inner diameter R1 of the boss face 52, the outer seal portion 54 is a region surrounded by the outer edge of the oil chamber 53a and the outer diameter R2 of the boss face 52, the spacing sealing part 56 is a boss surface area formed by spacing between the adjacent oil chambers 53a, and a certain reasonable clearance is always kept between the sealing part of the boss surface 52 and the bearing surface of the swash plate 40, so that oil film leakage is in a reasonable level.

Fig. 8 shows an embodiment of the swash plate, the swash plate 40 has a swash plate bearing surface 41 matching with the static bearing surface of the swash plate, a distribution oil groove 42 communicating with the oil inlet 33a and the oil outlet 33b of the end cover 33 is provided on the swash plate 40, the distribution oil groove 42 includes a low pressure distribution oil groove 42a and a high pressure distribution oil groove 42b, the low pressure distribution oil groove 42a communicates with the low pressure oil inlet 33a, and the high pressure distribution oil groove 42b communicates with the high pressure oil inlet 33 b.

Wherein the opening of the oil distribution groove 42 on the end surface of the swash plate 40 opposite to the swash plate 50 is formed into a waist-shaped low-pressure distribution window 43 and a waist-shaped high-pressure distribution window 44, the low-pressure distribution window 43 and the high-pressure distribution window 44 are divided into two sides by a plane passing through the central axis of the swash plate, the low-pressure distribution window 43 and the high-pressure distribution window 44 may be arranged in a symmetrical or asymmetrical structure with respect to the central plane, for example, as shown in fig. 9, the high-pressure distribution window 44 is arranged into a plurality of windows having waist shapes; the swash plate has certain pre-boosting and pre-reducing functions, and the low-pressure flow distribution window 43 and the high-pressure flow distribution window can rotate for a certain angle along the central shaft of the swash plate; in particular, a throttling groove or hole 43a may be provided at the end of the low-pressure distribution window 43 to transition from the low-pressure distribution window 43 to the high-pressure distribution window 44 and at the end of the high-pressure distribution window 44 to transition from the high-pressure distribution window 44 to the low-pressure distribution window 43, as shown in fig. 9, to perform the functions of pre-reducing and pre-increasing the pressure from high pressure to low pressure or from low pressure to high pressure.

The bearing surface of the swash plate 40 opposite to the end cover 33 is provided with a cylindrical bearing surface 45 which is shaped like a cylinder, the end cover 33 is provided with a sliding arc surface 33e with the same radius as the cylindrical bearing surface 45 of the swash plate, so that the cylindrical bearing surface 45 always keeps a close state when sliding on the sliding arc surface 33e of the end cover, the flow distribution oil groove 42 is opened on the cylindrical bearing surface 45 of the swash plate to form a groove-shaped low pressure port 46 and a groove-shaped high pressure port 47, and the groove-shaped low pressure port 46 and the groove-shaped high pressure port 47 on the cylindrical bearing surface 45 are respectively communicated with the low pressure flow distribution window 43 and the high pressure flow distribution window 44 on the swash plate bearing surface 41 opposite to the cylindrical bearing surface. The slotted low-pressure port 46 and the slotted high-pressure port 47 on the cylindrical support surface 45 are of symmetrical or asymmetrical configuration, for example, the slotted low-pressure port 46 and the slotted high-pressure port 47 are of equal or unequal configuration in opening width and/or length. The slotted low pressure port 46 and the slotted high pressure port 47 on the cylindrical bearing surface 45 may be asymmetrically configured for use as a pump. The peripheries of the groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical bearing surface 45 are provided with sealing belts for sealing the groove openings, so that the cylindrical bearing surface 45 seals oil when sliding on the sliding arc surface of the end cover. In one embodiment, a communication slot 48 is provided on the cylindrical bearing surface 45 of the swash plate to communicate the slotted low pressure port 46 with the second cavity 35 of the housing, so that the oil inlet communicates with the second cavity 35 of the housing.

When the pump is used as a pump, the oil flow is as follows: when the oil absorption, there are two way oil feed passageways, wherein the passageway of one kind is: the low-pressure oil enters the flow passage from the oil inlet 33a of the end cover 33 and sequentially passes through the groove-shaped low-pressure port 46 of the swash plate, the low-pressure flow distribution window 43, the oil chamber 53a of the sliding plate, the large-aperture oil through hole 53, the plunger ball socket 58 and the large-aperture plunger center hole 72 to reach the plunger hole 81 of the cylinder body; the other path is as follows: low pressure oil enters the cylinder plunger bore 81 directly from the housing second cavity 35 through the check valve 110 at the end of the cylinder 80; during oil discharge, high-pressure oil passes through the large-aperture plunger center hole 72, the plunger ball socket 58, the large-aperture oil passing hole 53, the oil chamber 53a of the sliding disc, the high-pressure flow distribution window 44 and the groove-shaped high-pressure port 46 in sequence from the plunger hole 81 of the cylinder body, and is finally discharged from the end cover oil outlet 33 b.

There are two way oil feed access's benefit to lie in when inhaling the oil: firstly, heat generated by each part of the pump can be taken away in time through the one-way valve 110, and the condition that the temperature of oil in the pump is increased to cause failure is avoided; secondly, an oil suction channel can be added, and the self-priming capacity of the pump is improved; and thirdly, an oil return pipeline and a cooling device of the pump can be eliminated, and the manufacturing and using cost of the pump is reduced.

Example 2:

specifically, the main difference from the other embodiments is that a port plate 90 is interposed between the slide plate 50 and the swash plate 40 in the slide plate pair, as shown in fig. 15, the slide plate 50 is supported on the port plate 90 and is in sliding fit with the port plate 90, the port plate is fixed on the swash plate by means of pins or the like, a high-pressure port 93 and a low-pressure port 92 are provided on the port plate 90, as shown in fig. 16, the high-pressure port 93 and the low-pressure port 92 are respectively communicated with the low-pressure port 43 and the high-pressure port 44 on the swash plate, and the low-pressure port 92 and the high-pressure port 93 may be arranged in a symmetrical or asymmetrical structure with respect to the central plane, for example, the high-pressure port 93 is arranged in a plurality of windows (not shown) having a kidney shape; in order to enable the valve plate to have certain pre-boosting and pre-reducing functions, the low-pressure valve port 92 and the high-pressure valve port 93 can rotate for a certain angle along the central axis of the valve plate; specifically, a throttling groove or a hole which is arranged on the end part of the low-pressure distribution port 92 and transits from the low-pressure distribution port 92 to the high-pressure distribution port 93 and is arranged on the end part of the high-pressure distribution port 93 and transits from the high-pressure distribution port 93 to the low-pressure distribution port 92 can be arranged, so that the functions of pre-reducing pressure and pre-increasing pressure from high pressure to low pressure or from low pressure to high pressure can be achieved.

In this embodiment, the benefit of interposing port plate 90 between the slider plate 50 and the swashplate 40 is that it is easier and less expensive to later replace the port plate than to replace the swashplate.

Example 3:

as shown in fig. 13, 14 and 17, the main difference from the other embodiments is the structure of the swash plate 40 and the port plate 90.

As shown in fig. 13 and 14, an embodiment of a swash plate having a swash plate bearing surface 41 matching with the static pressure bearing surface of the swash plate is shown, and only a high-pressure distribution oil groove 42b communicating with the end cover oil outlet 33b is provided on the swash plate, and the opening of the high-pressure distribution oil groove 42b on the end surface of the swash plate 40 opposite to the swash plate is shaped as a kidney-shaped high-pressure distribution window 44. Specifically, a throttling groove or hole 43a may be provided on one or both ends of the high-pressure distribution window 44 to perform pre-pressure reduction and pre-pressure increase from high pressure to low pressure or from low pressure to high pressure.

The bearing surface of the swash plate 40 opposite the end cover 33 is provided with a cylindrical bearing surface 45 shaped like a cylinder. The end cover 33 is provided with a sliding arc surface 33e with the same radius as the cylindrical bearing surface 45, so that the cylindrical bearing surface 45 is always kept in a close contact state when sliding on the sliding arc surface 33e of the end cover, the high-pressure flow distribution oil groove 42b is opened on the cylindrical bearing surface 45 of the swash plate to form a groove-shaped high-pressure port 47, the groove-shaped high-pressure port 47 on the cylindrical bearing surface 45 is correspondingly communicated with the high-pressure flow distribution window 44 on the swash plate bearing surface 41 on the opposite side of the cylindrical bearing surface, and the periphery of the groove-shaped high-pressure port 47 on the cylindrical bearing surface 45 is provided with a sealing belt for sealing the groove opening, so that the cylindrical bearing surface 45 seals oil when sliding on the sliding arc surface 33e of the end cover.

Similarly, as shown in fig. 17, the port plate 90 is provided with only the high-pressure port 93, the high-pressure port 93 communicates with the high-pressure port groove 42b of the swash plate, and the slide plate 50 is supported by the port plate 90 to realize the static pressure support.

In a structure matched with the pump, oil inlet and outlet ports 33a and 33b of the pump are separately provided, an oil inlet port 33a is provided on the housing 32, and an oil outlet port 33b is provided on the end cover 33, so that when the pump is used, the oil flow path is as follows: when oil is absorbed, low-pressure oil directly enters the cylinder plunger hole 81 from the second cavity 35 of the shell through the check valve 110 at the end part of the cylinder 80; during oil discharge, high-pressure oil passes through the plunger hole 81 of the cylinder body, the large-aperture plunger center hole 72, the plunger ball socket 58, the large-aperture sliding disc oil through hole 53 and the high-pressure oil distribution groove 42b in sequence, and is finally discharged from the end cover oil outlet 33 b.

The above description is further detailed in connection with specific preferred embodiments of the invention and should not be taken as limiting the invention to the specific embodiments described. To those skilled in the art to which the invention pertains, without departing from the spirit of the invention, several simple deductions or replacements can be made, and all the technical solutions and modifications thereof that do not depart from the spirit and scope of the invention should be covered by the scope of the claims of the invention.

Claims

1. An axial plunger pump or motor, characterized in that: the oil distribution type hydraulic pump comprises a swash plate (40), a sliding disc (50) supported on the swash plate (40), a cylinder body (80) and a plunger (70), wherein the sliding disc (50) is of an integral structure, a static pressure bearing surface (51) is arranged on the end surface of the sliding disc (50) opposite to the swash plate (40), a plurality of plunger ball sockets (58) are arranged on the other end surface of the sliding disc (50), oil through holes (53) for communicating the plunger ball sockets (58) with the static pressure bearing surface (51) are formed in the sliding disc (50), a flow distribution oil groove (42) is formed in the swash plate (40), the flow distribution oil groove (42) is communicated with oil inlet and outlet holes (33a and 33b) formed in the shell of the plunger pump or motor and close to the end part of one side of the swash plate (40), one end of the plunger (70) is arranged in the plunger ball sockets (58), the other end of the plunger center hole (72) in the plunger (70) is inserted into the opening end of the, the other end of the hydraulic cylinder is communicated with a plunger hole (81) in the cylinder body (80), one end of the cylinder body (80) is provided with a one-way valve (110), the one-way valve (110) is used for communicating the plunger hole (81) of the cylinder body (80) with an inner cavity of the shell, and the one-way valve (110) only allows hydraulic oil to enter the plunger hole (81) from the cavity of the shell.

2. The axial piston pump or motor as claimed in claim 1, wherein: the check valve (110) comprises a valve body (111) connected with the cylinder body (80), a valve core (112) arranged inside the valve body (111), a retaining ring (114) fixed on the valve body (111) and a spring (113) arranged between the valve core (112) and the retaining ring (114), and the check valve (110) only allows hydraulic oil to flow from the second cavity (35) of the shell to the plunger hole (81) of the cylinder body (80).

3. The axial piston pump or motor as claimed in claim 1, wherein: the oil distribution groove (42) arranged on the swash plate (40) comprises a low-pressure oil distribution groove (42a) and a high-pressure oil distribution groove (42b) which are respectively communicated with the oil inlet and the oil outlet (33a and 33b), when oil is absorbed, low-pressure oil enters the plunger hole (81) of the cylinder body (80) from the low-pressure oil distribution groove (42a) and the check valve (110) at the end part of the cylinder body (80), and when oil is discharged, high-pressure oil is only discharged to the oil outlet (33b) from the high-pressure oil distribution groove (42 b).

4. The axial piston pump or motor as claimed in claim 3, wherein: the hydrostatic bearing surface (51) is provided with a plurality of oil chambers (53a), openings of the flow distribution oil grooves (42) on the end surface of the swash plate (40) opposite to the sliding plate (50) are formed into waist-shaped low-pressure flow distribution windows (43) and waist-shaped high-pressure flow distribution windows (44), the high-pressure flow distribution windows (44) and the low-pressure flow distribution windows (43) are intermittently communicated with the oil chambers (53a), the bearing surface of the swash plate (40) opposite to the end cover (33) of the plunger pump or the motor shell is provided with a cylindrical bearing surface (45) formed into a cylinder, the cylindrical bearing surface (45) of the swash plate (40) is provided with groove-shaped low-pressure ports (46) and groove-shaped high-pressure ports (47), and the groove-shaped low-pressure ports (46) and the groove-shaped high-pressure ports (47) are respectively communicated with the oil inlet (33a) and the oil outlet (33 b.

5. The axial piston pump or motor as claimed in claim 4, wherein: the cylindrical bearing surface (45) of the swash plate (40) is provided with a communication notch (48) for communicating the groove-shaped low-pressure port (46) with the second cavity (35) of the shell.

6. The axial piston pump or motor as claimed in claim 1, wherein: the oil through hole (53) in the sliding disc (50) and the plunger center hole (72) in the plunger (70) are both large-aperture main oil hole structures.

7. The axial piston pump or motor as claimed in claim 1, wherein: the oil distribution groove (42) arranged on the swash plate (40) is only provided with a high-pressure oil distribution groove (42b) communicated with the oil outlet (33b), when oil is absorbed, low-pressure oil enters the plunger hole (81) of the cylinder body (80) from the check valve (110) at the end part of the cylinder body (80), and when oil is discharged, high-pressure oil is discharged to the oil outlet (33b) from the high-pressure oil distribution groove (42 b).

8. The axial piston pump or motor as claimed in claim 7, wherein: an opening of the flow distribution oil groove (42) on the end face of the swash plate (40) opposite to the sliding disc is formed into a waist-shaped high-pressure flow distribution window (44), the high-pressure flow distribution window (44) is intermittently communicated with an oil chamber (53a) on the static pressure bearing surface (51), an opening of the flow distribution oil groove (42) on a cylindrical bearing surface (45) opposite to the end cover (33) is formed into a groove-shaped high-pressure port (47), and the groove-shaped high-pressure port (47) is correspondingly communicated with an oil outlet (33 b).

9. The axial piston pump or motor as claimed in claim 1, wherein: the plunger (70) comprises a connecting rod plunger with a conical structure or a connecting rod plunger with ball heads at two ends or a spherical plunger with a universal hinge, one end of the plunger (70) can be inserted into a plunger hole (81) of a cylinder body (80) in a reciprocating sliding mode relative to the cylinder body (80), the other end of the plunger (70) is fixed on a plunger ball socket (58) of a sliding disc (50) in a state of being limited in distance relative to the end surface of the sliding disc (50) and capable of tilting, and a large-aperture plunger center hole (72) communicating the plunger ball socket (58) with the plunger hole (81) is formed in the plunger (70).

10. The axial piston pump or motor as claimed in any one of claims 1 to 9, wherein: a flow distribution disc (90) is clamped between the sliding disc (50) and the swash plate (40), the sliding disc (50) is supported on the flow distribution disc (90) and keeps sliding fit with the flow distribution disc (90), high-pressure and low-pressure flow distribution ports (93 and 92) or the high-pressure flow distribution ports (93) are formed in the flow distribution disc (90), and the flow distribution ports of the flow distribution disc (90) are communicated with a flow distribution oil groove (42) of the swash plate (40) and an oil chamber (53a) of the sliding disc (50).