WO2020182200A1

WO2020182200A1 - Sliding plate supported through-shaft plunger pump or motor

Info

Publication number: WO2020182200A1
Application number: PCT/CN2020/079165
Authority: WO
Inventors: 钟彪; 尹学军
Original assignee: 青岛科而泰控股有限公司; 钟彪
Priority date: 2019-03-13
Filing date: 2020-03-13
Publication date: 2020-09-17
Also published as: CN110067724A

Abstract

Provided is a sliding plate supported through-shaft plunger pump or motor, comprising a main shaft (10), a cylinder (80) supported on the main shaft (10) and rotating synchronously with the main shaft (10), and a distribution sliding plate pair, wherein the main shaft (10) is supported on the bearings at both ends in the form of penetrating the cylinder (80) and the distribution sliding plate pair, the distribution sliding plate pair includes a swash plate (40) and a sliding plate (50) supported on the swash plate (40), the sliding plate (50) is an integral structure, and the end face, opposite to the swash plate (40), of the sliding plate (50) is provided with a static pressure support surface (51), a plurality of oil chambers (53a) are arranged on the static pressure support surface (51), a plurality of plunger ball sockets (58) are arranged on the other end face of the sliding plate (50), the sliding plate (50) is provided with a large-aperture oil through hole (53) communicating with the plunger ball sockets (58) and the oil chambers (53a), the swash plate (40) is provided with a distribution oil tank (42) communicating with oil inlet and outlet (33a, 33b), a third bearing (23) is arranged between the sliding plate (50) and the swash plate (40), and the sliding plate (50) is supported on the third bearing (23) in a radially constrained state. The structure can improve the performance, such as working reliability, volumetric efficiency and service life, of axial plunger pumps or motors.

Description

Sliding plate supported through shaft plunger pump or motor

This application claims the priority of the Chinese patent application No. 201910189068.1 filed on March 13, 2019, and the contents of the above-mentioned Chinese patent application are cited here in full as a part of this application.

Technical field

The embodiments of the present disclosure relate to a swash plate type axial piston pump or motor, and more particularly to a sliding plate supported through shaft piston pump or motor.

Background technique

Axial piston pumps and motors are one of the most widely used hydraulic components in modern hydraulic transmissions. Among them, the hingeless inclined axis pump and the sliding shoe swash plate axial piston pump are the two most widely used and most important. Class axial piston pump. The inclined axis pump and the sliding shoe swash plate type also have their own characteristics. These two pumps or motors are still in competition, and each is continuously improved and developed. The swash plate axial piston pump has the characteristics of simple and compact structure, convenient variables, more variable forms, and small inertia. Therefore, the swash plate axial piston pump has become the most important type now. Pump. According to the support form of the main shaft and cylinder block, the swash plate type axial piston pump is divided into through shaft type and non-through shaft type. The end of the main shaft of the through shaft type axial piston pump can be connected with an auxiliary charge pump or another main pump to form The tandem axial piston pump has obvious advantages in improving the self-priming ability of oil and increasing the displacement.

Summary of the invention

At least one embodiment of the present disclosure provides a sliding plate supported through-shaft plunger pump or motor, which includes a main shaft, a cylinder supported on the main shaft and rotating synchronously therewith, and a valve sliding plate pair. The main shaft penetrates the cylinder and The pair of flow distribution plates are supported on the bearings at both ends. The pair of flow distribution plates includes a swash plate and a sliding plate supported on the swash plate. The sliding plate is an integral structure, and the sliding plate is opposite to the swash plate. The end surface is provided with a static pressure supporting surface, the other end surface of the sliding plate is provided with a plurality of plunger ball sockets, and the sliding plate is provided with oil through holes connecting the plunger ball sockets and the static pressure supporting surface. A flow distribution oil groove is provided on the plate, and the flow distribution oil groove communicates with the oil inlet and the oil outlet provided on one end of the plunger pump or the motor housing close to the swash plate. A second oil outlet is provided between the sliding plate and the swash plate. Three bearings, the sliding plate is supported on the third bearing in a constrained state along its radial direction.

For example, in the sliding plate supported through-shaft plunger pump or motor provided by an embodiment of the present disclosure, the hydrostatic bearing surface is a boss surface on the sliding plate extending to one side of the swash plate along the axis of the sliding plate A plurality of oil chambers and a sealing part for sealing oil are provided on the boss surface, the sealing part is arranged on the inner and outer circumferences of the oil chamber in a state surrounding the oil chamber, and the sealing part includes The inner and outer seals inside and outside the oil chamber in the radial direction, and the interval seals arranged between adjacent oil chambers.

For example, in the sliding plate supported through-shaft plunger pump or motor provided by an embodiment of the present disclosure, the outer periphery of the swash plate is provided with a raised supporting stop, and the third bearing is sandwiched between the outer side of the sliding plate and Between the inner sides of the supporting block, the sliding plate is supported on the third bearing in a state of being restricted in its radial direction.

For example, in the sliding plate supported through-shaft plunger pump or motor provided by an embodiment of the present disclosure, a restraining device is provided on one side of the valve sliding plate pair, and the restraining device is included in the sliding plate close to the hydrostatic bearing surface. One side has a stop portion protruding outward and an engagement device provided on the support stop portion, and the engagement device restricts the sliding plate from moving away from the end surface of the swash plate in a manner that restricts the third bearing from moving outward .

For example, in the sliding plate supported through-shaft plunger pump or motor provided by an embodiment of the present disclosure, a plurality of oil chambers are provided on the static pressure supporting surface, and the end surface of the swash plate opposite to the sliding plate A waist-shaped low-pressure distribution window and a waist-shaped high-pressure distribution window are provided on the upper part. The high and low pressure distribution windows are intermittently communicated with the oil chamber. The supporting surface of the swash plate opposite to the end cover has a cylindrical column. The supporting surface, the cylindrical supporting surface of the swash plate is provided with a groove-shaped low-pressure port and a groove-shaped high-pressure port, the groove-shaped low-pressure port and the groove-shaped high-pressure port are respectively connected to the low-pressure distribution window and the high-pressure distribution window The window corresponds to the connection.

For example, in the sliding plate-supported through-shaft plunger pump or motor provided by an embodiment of the present disclosure, the cylindrical supporting surface of the swash plate has a communication slot connecting the groove-shaped low pressure port and the second cavity of the housing.

For example, in the sliding plate supported through-shaft plunger pump or motor provided by an embodiment of the present disclosure, the first bearing supporting the main shaft includes at least one centripetal thrust bearing or thrust bearing, and the plunger hole of the cylinder It is a structure with one end closed and one end open. During operation, the hydraulic axial force acts on the end surface of the cylinder with the closed end of the plunger hole and is transmitted to the housing of the plunger pump or motor via the first bearing.

For example, in a sliding plate supported through-shaft plunger pump or motor provided by an embodiment of the present disclosure, an auxiliary pump or a main pump is connected to the end of the main shaft to form a series double pump structure.

For example, in the sliding plate supported through-shaft plunger pump or motor provided by an embodiment of the present disclosure, a check valve is provided at the closed end of the cylinder, and the check valve is used to communicate with the plunger hole of the cylinder. And the inner cavity of the housing, and the one-way valve only allows hydraulic oil to enter the plunger hole from the cavity of the housing.

For example, in the sliding plate supported through-shaft plunger pump or motor provided by an embodiment of the present disclosure, the plunger includes a connecting rod plunger with a tapered structure or a connecting rod plunger with ball heads at both ends Or a kind of spherical plunger with universal hinge. One end of the plunger can be detached into the plunger hole of the cylinder in a reciprocating manner relative to the cylinder, and the other end is restricted and able to be far away from the end surface of the sliding plate. The tilted state is fixed on the plunger ball socket of the sliding plate, and the plunger is provided with a large-diameter plunger center hole connecting the plunger ball socket and the plunger hole.

For example, in the sliding plate supported through-shaft plunger pump or motor provided by an embodiment of the present disclosure, a pre-sealing device is provided between the sliding plate and the cylinder, and the pre-sealing device includes a central spring and a retaining ring. , Ball hinge, the ball hinge abuts on the sliding plate or the pressure plate, the retaining ring is arranged on the cylinder, and the pre-sealing device makes the sliding plate tightly abut on the swash plate through the action of the central spring .

For example, in the sliding plate supported through-shaft plunger pump or motor provided by an embodiment of the present disclosure, the pre-sealing between the sliding plate and the swash plate includes a combination of a pre-sealing device provided with a central spring and a restraining device.

For example, in the sliding plate supported through-shaft plunger pump or motor provided by an embodiment of the present disclosure, a valve plate is interposed between the sliding plate and the swash plate, and the sliding plate is supported on the valve plate and is connected to the valve plate. The plate maintains a sliding fit. The valve plate is provided with high and low pressure distribution ports. The hydraulic oil flows through the distribution oil groove on the swash plate, the distribution port on the distribution plate, the oil through hole on the sliding plate, and the column under the reciprocating action of the plunger. Plug the center hole to realize the suction and discharge of hydraulic oil.

Description of the drawings

Figure 1 is a schematic structural diagram of a through-shaft axial piston pump or motor;

Figure 2 is an embodiment of a sliding plate supported through-shaft plunger pump or motor in this disclosure;

Fig. 3 is an A-A sectional view of the sliding plate supported through-shaft plunger pump or motor in Fig. 2 in this disclosure;

Figure 4 is a plan view of one end of the sliding plate in this disclosure;

Fig. 5 is a B-B sectional view of the sliding plate structure in Fig. 4 in this disclosure;

Figure 6 is a plan view of the other end of the sliding plate in this disclosure;

Figure 7 is a plan view of one end of the swash plate opposite to the sliding plate in this disclosure;

Figure 8 is a plan view of one end of the swash plate opposite to the end cap in the present disclosure;

Figure 9 is a D-D sectional view of Figure 8 in this disclosure;

10 is an embodiment of a sliding plate supported through-shaft plunger pump or motor provided with thrust bearings in this disclosure;

Figure 11 is another embodiment of a sliding plate supported through-shaft plunger pump or motor in this disclosure;

Figure 12 is a plan view of the valve plate in this disclosure;

Figure 13 is an embodiment of a sliding plate supported through-shaft plunger pump or motor provided with a one-way valve in this disclosure; and

Figure 14 is an embodiment of a sliding plate supported through-shaft plunger pump or motor with a central spring.

Reference signs: 10 is the spindle, 10C is the spindle axis, 11 is the first bearing support portion, 12 is the second bearing support portion, 13 is the spindle shoulder, 21 is the first bearing, 21a is the radial ball bearing, 21b It is a radial thrust bearing or thrust bearing, 22 is the second bearing, 23 is the third bearing, 31 is the front shell, 32 is the shell body, 33 is the end cover, 33a is the oil inlet, 33b is the oil outlet, and 33d is Flow channel, 33e is the sliding arc surface, 34 is the first cavity, 35 is the second cavity, 38 is the variable connection part, 39 is the auxiliary pump, 40 is the swash plate, 41 is the swash plate support surface, 41a is the support block Part, 42 is the distribution oil groove, 43 is the low-pressure distribution window, 44 is the high-pressure distribution window, 45 is the cylindrical support surface, 46 is the groove-shaped low-pressure port, 47 is the groove-shaped high-pressure port, 48 is the connecting groove, 50 is the sliding plate, 50C is the axis of the sliding plate, 51 is the hydrostatic bearing surface, 52 is the boss surface, 53 is the oil hole, 53a is the oil chamber, 54 is the outer seal, 55 is the inner seal, 56 is the interval seal, and up to 57 Block 58 is the plunger ball socket, 59 is the sliding plate bearing support part, 60 is the pressure plate, 70 is the plunger, 71 is the plunger ball head, 72 is the plunger center hole, 73 is the tapered rod, 74 is In the plunger part, 80 is the cylinder, 81 is the plunger hole, 82 is the spindle assembly hole, 80C is the central axis of the cylinder, 90 is the valve plate, 91 is the support surface of the valve, 92 is the low pressure orifice, and 93 is the high pressure orifice. , 100 is the center spring, 101 is the stop, 102 is the thimble, 103 is the ball hinge, 110 is the one-way valve, 111 is the valve body, 112 is the valve core, 113 is the spring, 114 is the retaining ring, 120 is the slipper, 130 It is a return disk, 140 is a clamping device, and 141 is a cylinder spring.

detailed description

As shown in Figure 1, it is a typical structure of a through-shaft axial piston pump or motor, which includes a main shaft 10, a housing, a first bearing 21, a second bearing 22, a swash plate 40, a plunger 70, and a sliding shoe. 120, a cylinder 80, a valve plate 90, a return plate 130, and a central spring 100. The spindle axis 10C of the spindle 10 coincides with the cylinder axis 80C of the cylinder 80, and the central spring 100 passes through a ball hinge 103 The return plate 130 is pressed tightly, and the sliding shoe 120 is supported on the swash plate 40 and maintains a tight fit with the working surface of the swash plate 40. From the connecting end of the main shaft to the direction of the end cover, the main shaft 10 is in turn It penetrates the swash plate 40, the return plate 60, the cylinder block 80 and the valve plate 90, and is supported by the first bearing 21 and the second bearing 22 at both ends. The cylinder block 80 is connected to the main shaft 10 by a key and is supported on the On the main shaft 10, when used as an axial piston pump, a prime mover (not shown, such as an electric motor, an internal combustion engine, etc.) drives the main shaft 10 to rotate, and the supporting force of the swash plate 40 and the return force of the center spring 100 act Next, the plunger 70 reciprocates in the plunger hole 81 of the cylinder block to realize the oil suction and discharge work of the pump or motor.

The through-shaft axial piston pump or motor may have the following disadvantages: 1. There are three key friction pairs, and the number of friction pairs is large, which causes the leakage of the axial piston pump or motor to increase and reduces its volumetric efficiency. The failure of any friction pair will result in the failure of the entire axial piston pump or motor. Therefore, a larger number of friction pairs will also increase the failure probability of the pump or motor; 2. Under the action of hydraulic pressure, the swash plate will oppose the column. The plug generates a large lateral force, which is transmitted to the cylinder and main shaft via the plunger, causing a wedge-shaped gap between the cylinder and the valve plate, increasing the volume loss of the pump or motor, and making the cylinder and the valve flow The sealing surface between the discs produces partial contact, causing burns on the surface between the cylinder block and the valve plate, which in turn makes the pump or motor completely out of function; 3. The return mechanism of the through-shaft axial plunger pump or motor has more components. Many, including the center spring 100, thimble 102, ball hinge 103, return plate 130 and other components, its structure is more complex, easy to fail, especially the center spring is often broken due to fatigue damage, resulting in the seal between the cylinder and the valve plate Failure, slippery shoe tilting and eccentric wear, etc.; 4. During the high-speed movement of the shoe, the centrifugal torque, return force caused by the circumferential movement and the friction torque generated by the rotation of the cylinder will cause the shoe to be relatively inclined. The surface of the disc is overturned, thereby forming a wedge-shaped oil film, and causing partial wear of the sliding shoe, thereby destroying the normal operation of the sliding shoe.

Therefore, it is hoped to propose a beneficial disclosure, which aims to solve the problems of the through-shaft axial piston pump or motor with more friction pairs, greater lateral force, more complex return mechanism, eccentric wear of sliding shoes, etc., thereby improving The reliability and volumetric efficiency of the swash plate axial piston pump or motor.

The purpose of the present disclosure is to provide a new type of axial piston pump or motor structure in view of the possible problems of the through-shaft axial piston pump or motor, which aims to reduce the number of friction pairs and reduce the lateral direction of the plunger. The impact of the overturning of the cylinder caused by the force, simplifying the structure of the return mechanism, thereby improving the working reliability, volumetric efficiency, and working life of the through-shaft axial piston pump or motor.

The following describes the embodiments of the present disclosure in detail with reference to the accompanying drawings.

Although the present disclosure allows embodiments in different forms, this specification and drawings only disclose some specific forms as examples of the present disclosure. However, the present disclosure is not intended to be limited to the described embodiments. The scope of the present disclosure is given in the appended claims.

For ease of description, the embodiments of the present disclosure are shown in a typical orientation, the orientation is such that when the central axis of the shaft of the axial plunger pump or motor is horizontally standing, the side of the coupling end of the main shaft is left, and the end cover For the right, "vertical", "horizontal", "upper", "lower", "front", "rear", "left", "right", "horizontal", "bottom", "inner" and " Terms such as "outside" are used with reference to this position, only for the convenience of describing the present disclosure and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, and a specific orientation configuration and operation. It is understood that the present disclosure can be manufactured, stored, transported, used, and sold in orientations other than those described.

For ease of description, the focus is on the description of the axial piston pump. The structure of the axial piston motor can refer to the structure of the axial piston pump and make necessary changes. However, it should be pointed out that all the axial piston pumps using the principles of the present disclosure Both plunger pumps or motors can be considered to be included.

Example 1:

As shown in Figures 2-9, this is an embodiment of the sliding plate supported through shaft plunger pump of the present disclosure. In the preferred embodiment shown, the sliding plate supported through shaft plunger pump includes a main shaft 10, a housing Body, the first bearing 21, the second bearing 22, the valve sliding plate pair, the plunger 70 and the cylinder 80, the main shaft axis 10C of the main shaft 10 coincides with the cylinder center axis 80C of the cylinder block 80, so One end of the main shaft 10 extends out of the housing and is supported on the first bearing 21, and the other end penetrates the valve slide pair to the end seat and is supported on the second bearing 22. The main shaft 10 and the cylinder 80 are connected by a key to realize synchronous rotation. , The cylinder 80 is supported in the central area of the main shaft 10, from the coupling end of the main shaft 10 to the end cover direction, the main shaft 10 passes through the cylinder 80, the pressure plate 60, the sliding plate 50 and the swash plate 40 in turn; the flow distribution sliding plate The auxiliary includes a swash plate 40 and a sliding plate 50 supported on the swash plate 40. The sliding plate 50 is an integral structure. The sliding plate 50 is provided with a static pressure support surface 51 supported on the swash plate. 40 and maintain a close fit with the working surface of the swash plate 40, one end of the sliding plate 50 is provided with a plurality of waist-shaped oil chambers 53a, and 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 that communicates the plunger ball socket 58 and the oil chamber 53a, and the swash plate 40 is provided with a distribution oil groove 42 communicating with the oil inlet 33a and the oil outlet 33b When working, under the reciprocating action of the plunger, the hydraulic oil flows through the distribution oil groove 42 on the swash plate 40, the oil chamber 53a, the large-diameter oil through hole 53, the large-diameter plunger center hole 72, and the cylinder plunger hole 81 to achieve hydraulic pressure. The suction and discharge of oil; a third bearing 23 is arranged between the sliding plate 50 and the swash plate 40, and the sliding plate 50 is supported on the third bearing 23 in a state of being restrained in the radial direction.

Among them, it should be noted that the large pore diameters in the large-diameter oil through hole 53 and the large-diameter plunger center hole 72 are relative to the pore diameter of the corresponding part in another structure, and the pore diameter in this structure is slender. Hole diameter, only a small part of the high-pressure oil in the plunger hole passes through this hole, and the oil pressure is reduced under the action of the slender pore diameter. Therefore, the pore diameter in the structure with the slender pore diameter is mainly used for throttling and For decompression, the large-aperture oil through hole 53 and the large-aperture plunger center hole 72 in the present disclosure are used as the main oil hole structure. Both suction and discharge of hydraulic oil flow through this main oil hole structure, and the oil passes through the large-aperture oil hole. There is no significant pressure drop between the hole 53 and the central hole 72 of the large-aperture plunger, so their structures are essentially different. Specifically, in the disclosed embodiment, the hole diameter of the oil through hole 53 is increased to be similar to or consistent with the width direction dimension of the waist-shaped oil chamber 53a compared with the hole diameter of the corresponding part in the above-mentioned structure adopting the elongated hole diameter.

In the embodiment of the present disclosure, the housing may be configured as a double-piece structure or a three-piece structure. When the housing is configured as a double-piece structure, the housing includes a hollow-shaped housing 32 and an end connected to the housing. Cover 33. The shell body 32 has a first cavity 34 for accommodating the first bearing 21 and a second cavity 35 for accommodating the cylinder and for accommodating the valve sliding plate pair. The end cover 33 is used to close the opening at one end of the shell 32. The end cover 33 is provided with the oil inlet 33a and the oil outlet 33b of the pump, the flow channel 33d communicating with the swash plate distribution oil groove 42 and the sliding arc surface supporting the swash plate 33e; When the axial piston pump is a variable pump, a variable mechanism for variable swing is provided on the housing 32, and the variable mechanism is connected to the variable connecting portion 38 provided on the swash plate, under the action of the variable mechanism , The swash plate 40 and the sliding plate 50 rotate in the second cavity 35; when the housing is configured as a three-piece structure, the front shell can be configured as a structure composed of a front shell or a front shell 31 and a shell body 32, The front shell or front shell 31 is provided with a first cavity 34 for accommodating the first bearing 21, and the shell body 32 is provided with a second cavity 35 for accommodating the cylinder block and the sliding plate pair.

Wherein, the main shaft 10 passes through the shell body 32 to the end cover 33 in a cylindrical shape, and is provided with a first bearing support portion 11 and a second bearing support portion 12, and the first bearing support portion 11 and the shell body 32 are sandwiched therebetween. A first bearing 21 is provided. A second bearing 22 is interposed between the second bearing support portion 12 and the end cover 33. One end of the main shaft 10 extends out of the housing 32 for external prime movers (or loads) and passes through the first The bearing 21 is supported on the shell 32, and the other end penetrates to the end cover 33 and is supported on the end cover 33 via the second bearing 22. The main shaft 10 can rotate relative to the shell 32 through the first bearing 21 and the second bearing 22. The shaft is freely rotatable. The circumferential surface of the central area of the main shaft 10 is provided with a key connection structure for connecting the cylinder 80, and the main shaft 10 drives the cylinder 80 to realize synchronous rotation via the key connection structure.

The first bearing 21 includes at least one centripetal thrust bearing, and the centripetal thrust bearing includes, but is not limited to, a centripetal thrust ball bearing, a planar thrust bearing or a tapered roller bearing, which is located near the end of the cylinder 80 A spindle shoulder 13 is provided on the spindle 10. When the pump is working, the main shaft 10 drives the cylinder 80 to rotate synchronously. In the axial hydraulic pressure, the end of the cylinder abuts on the main shaft shoulder 13 and is transmitted to the first bearing 21 through the main shaft shoulder 13 and then Transfer to the shell 32. It should be noted that the transmission of axial load by the cylinder 80 through the main shaft shoulder 13 is not a condition for its application. Alternatively, as shown in FIG. 10, the first bearing 21 is provided with a supporting system including a thrust bearing 21b. The cylinder 80 directly abuts on the thrust bearing 21b and transmits the hydraulic axial force to the housing 32. The radial force is borne by the radial bearings 21a and the second bearings 22 supported on both ends of the main shaft.

The cylinder 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 32. The cylinder 80 has an evenly distributed circumferential direction about the central axis 80C of the cylinder. A plurality of plunger holes 81 and a spindle assembly hole 82 at the center for accommodating the spindle, the plunger hole 81 of the cylinder 80 is a blind hole structure with one end closed and one end open. Preferably, the number of the plunger holes is generally set to 7 or 9. The main shaft 10 passes through the main shaft assembly hole 82 of the cylinder block 80 and is connected to the cylinder block 80 with a connecting key provided on the outer peripheral surface of the shaft body. The cylinder block 80 is supported on the main shaft 10 in a manner that it moves synchronously with the main shaft 10 .

It should be pointed out that the end of the cylinder body 80 is not provided with a valve plate abutting it, thus reducing a friction pair and improving its volumetric efficiency; because the valve plate is not abutting, the end of the cylinder body 80 does not require precision machining, which reduces The manufacturing and use costs are reduced; there is no valve plate at the end of the cylinder body 80, even if there is some lateral force, it will not cause problems such as partial wear and failure.

The plunger 70 includes a plunger ball 71 with one end supported on the plunger ball socket 58 of the sliding plate 50 and fixed on the end surface of the sliding plate via a pressure plate 60, and a post for communicating the plunger hole 81 and the plunger ball socket 58 The central hole 72 of the plug, the conical rod portion 73 with a conical outer peripheral surface, and the plunger portion 74 that is clearance fit with the cylinder plunger hole wall and can reciprocate therebetween. The plunger ball head 71 is spherical and slidably supported on the plunger ball socket 58 of the sliding plate 50; the plunger center hole 72 is a large-diameter through hole structure, which serves as a suction and discharge channel for oil; The plug portion 74 is in clearance fit with the cylinder plunger hole 81. Preferably, at least one sealing ring is often provided on the plunger portion 74 to seal the liquid. The tapered rod portion 73 is approximately from the ball end of the plunger toward the plunger. The tapered shape of the portion 74 gradually increases. When the plunger 70 moves to a certain position, the tapered rod portion 74 is in contact with the inner circumferential surface of the plunger hole 81 of the cylinder to transmit force. However, it should be noted that the plunger 70 is not limited to the conical plunger type, and may also include a connecting rod-plunger with ball heads at both ends or a spherical plunger with a universal hinge.

A plurality of plunger ball sockets 58 are provided on the end surface of the sliding plate 50 facing the cylinder block opposite to the plunger 70. The plunger ball sockets 58 form recesses with a substantially hemispherical opening on the end surface of the sliding plate 50. The plunger ball socket 58 supports the plunger ball head 71 in a state evenly distributed on the common circumference of the sliding disc axis 50C. After the plunger 70 is installed in the plunger ball socket 58, the pressure plate 60 fixes it on the slide The end surface of the disk 50 restricts the movement of the plunger 70 relative to the end surface of the sliding disk 50. In particular, the method for fixing the plunger 70 on the end surface of the sliding plate 50 is not limited to the way of using a pressing plate. For example, a form-locking pressing device (not shown) may also be provided on the sliding plate 50, The pressing device can fix the plunger ball head 71 through a covering greater than 180 degrees.

As shown in Figures 4, 5 and 6, the end face of the sliding plate 50 opposite to the swash plate 40 is provided with a static pressure support surface 51, the sliding plate axis 50C and the spindle axis 10C are at a certain angle, the static pressure The supporting surface 51 is supported on the swash plate 40 and is always in sliding fit with the swash plate 40. The static pressure supporting surface 51 is provided with a plurality of lumbar-shaped oil chambers 53a. Preferably, the oil chambers 53a are The sliding disc axis 50C is evenly distributed on the hydrostatic support surface 51 as the center, and the sliding disc 50 is provided with a large-diameter oil through hole 53 that communicates the plunger ball socket 58 and the oil chamber 53a.

Further, the opposite end surface of the sliding plate 50 and the swash plate 40 is provided with a raised boss surface 52 extending along the axis 50C of the sliding plate to the side of the swash plate 40, and the boss surface 52 is formed by the inner diameter R1 and the outer diameter R1. The area enclosed by the diameter R2 is formed, the boss surface 52 of the sliding plate and the supporting surface of the swash plate 40 abut each other in a slidable manner, and a plurality of oils are provided on the boss surface 52 corresponding to the position of the plunger ball socket 58 The chamber 53a, preferably, the oil chamber 53a is uniformly spaced on the boss surface 52 in a common circumference centered on the sliding disc axis 50C.

Wherein, an effective hydrostatic oil film support is formed between the boss surface 52 and the support surface of the swash plate 40, and the boss surface 52 is provided with a sealing portion for sealing oil, and the sealing portion surrounds the oil chamber The state of 53a is arranged on the inner and outer circumferences of the oil chamber 53a, and the sealing part includes an inner sealing part 55 distributed in the radial direction of the oil chamber 53a, an outer sealing part 54 and an interval sealing part 56 distributed between adjacent oil chambers 53a. . The inner seal portion 55 is an area enclosed by the inner edge of the oil chamber 53a and the inner diameter R1 of the boss surface 52, and the outer seal portion 54 is enclosed by the outer edge of the oil chamber 53a and the outer diameter R2 of the boss surface 52. Area, the interval sealing portion 56 is a boss surface area formed by the interval between adjacent oil chambers 53a. A reasonable gap is always maintained between the sealing portion of the boss surface 52 and the supporting surface of the swash plate 40 so that the oil film leakage is at a reasonable level.

As shown in FIG. 7, the swash plate 40 has a swash plate support surface 41 that matches the static pressure support surface of the swash plate. The swash plate support surface 41 is provided with 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 the CC plane passing through the central axis of the swash plate. The low-pressure distribution window 43 and the high-pressure distribution window 44 can be arranged in a symmetrical or asymmetrical structure relative to the central plane CC. For example, the high-pressure distribution window 44 is set as a plurality of waist-shaped windows; in order to make the swash plate have a certain pre-boosting and pre-decreasing function, the low-pressure distribution window 43 and the high-pressure distribution window can be arranged along the center of the swash plate. The shaft rotates at a certain angle; in particular, it is also possible to set the transition from the low pressure distribution window 43 to the high pressure distribution window 44 on the end of the low pressure distribution window 43 and the high pressure distribution window 44 to transition from the high pressure distribution window 44 to the low pressure distribution on the end of the high pressure distribution window 44 The throttle groove or hole (not shown) in the direction of the window 43 plays a role of pre-decompression and pre-boosting from high pressure to low pressure or low pressure to high pressure.

As shown in FIG. 8, the supporting surface of the swash plate 40 and the end cover 33 opposite to each other is configured to have a cylindrical support surface 45 formed into a cylindrical shape, and the end cover 33 has a sliding arc with the same radius as the cylindrical support surface 45. The surface 33e makes the cylindrical supporting surface 45 always maintain a close contact state when sliding on the sliding arc surface 33e of the end cap. The cylindrical support surface 45 of the swash plate has a groove-shaped low-pressure port 46 and a groove-shaped high-pressure port 47 that are configured in a groove shape. The groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical support surface 45 are respectively connected to The low pressure distribution window 43 and the high pressure distribution window 44 on the swash plate supporting surface 41 on the opposite side of the cylindrical supporting surface of the swash plate communicate with each other. The groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical support surface 45 have a symmetrical or asymmetric structure. For example, the opening width and/or length of the groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 are equal or different. Equal configuration. Generally speaking, when used as a motor, the opening width and opening length of the groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical support surface 45 are of equal symmetrical configuration; when used as a pump, the cylindrical support The groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the surface 45 may have an asymmetric configuration. The groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical support surface 45 are provided with sealing bands to seal the grooves, so that the cylindrical support surface 45 seals oil when sliding on the sliding arc surface 33e of the end cover . In particular, on the cylindrical support surface 45 of the swash plate, a communication slot 48 having a groove-shaped low-pressure port 46 and a second cavity 35 of the housing, as shown in FIG. 8, makes the oil inlet and the first cavity of the housing The two cavities 35 are connected.

When used as a pump, its oil flow is as follows: When sucking oil, low pressure oil enters the flow passage 33d from the oil inlet 33a of the end cover 33, and then passes through the groove-shaped low pressure port 46 of the swash plate, the low pressure distribution window 43, and the sliding plate oil. The chamber 53a, the large-aperture oil hole 53, the plunger ball socket 58, and the large-aperture plunger center hole 72 reach the plunger hole 81 of the cylinder block; when the oil is discharged, the high-pressure oil passes through the plunger hole 81 of the cylinder block in turn The large diameter plunger center hole 72, the plunger ball socket 58, the large diameter oil through hole 53, the oil chamber 53a, the high pressure distribution window 44, the groove-shaped high pressure port 46, and finally discharge from the end cover oil outlet 33b.

The outer periphery of the swash plate 40 is provided with a supporting stop 41a, a third bearing 23 is interposed between the outer side of the sliding plate and the inner side of the supporting stop 41a, and the sliding plate 50 is supported in a restrained state along its radial direction. The third bearing 23. The third bearing 23 can be set to include, but is not limited to, a radial thrust ball bearing, a needle roller bearing, a cylindrical roller bearing, a tapered roller bearing, and a radial ball bearing. The main shaft 10 and the cylinder 80 are When rotating, the plunger 70 reciprocates in the plunger cavity of the cylinder 80 to realize the oil suction and discharge operation of the pump or motor.

During the operation of the axial piston pump, the plunger 70 in the high-pressure zone is acted on by the high-pressure oil pressure of the cylinder plunger hole 81, and a nearly horizontal hydraulic pressure is exerted on the sliding plate 50 through the plunger ball 71. The force pushes the sliding plate 50 toward the swash plate 40 and makes close contact with the end surface of the swash plate 40. The end of the swash plate 40 exerts a reaction force on the sliding plate 50. Since the end face of the swash plate 50 and the end face of the swash plate 40 are in inclined contact, the reaction force of the swash plate 40 can be decomposed into a horizontal component force along the spindle axis 10C and The lateral component force along the direction perpendicular to the spindle axis 10C has a tendency to move the sliding plate sideways. After the third bearing 23 is interposed between the swash plate 40 and the sliding plate 50, the sliding plate receives the reaction force of the third bearing 23, and the reaction force acting on the sliding plate can also be decomposed into a direction along the spindle axis 10C The horizontal component and the lateral component along the direction perpendicular to the spindle axis 10C. In addition, the sliding plate is also subjected to return restraint force, inertial force (to cancel each other), and friction (not shown), etc. The above-mentioned forces constitute the force balance of the sliding plate. It should be noted that the horizontal component force of each force along the axis of the main shaft is balanced with the hydraulic pressure of the plunger 70 acting on the sliding plate 50. The lateral component force acting on the sliding plate 50 in the direction perpendicular to the spindle axis 10C can be offset in the sliding plate 50 without being further transmitted to the cylinder 80 via the plunger 70.

This structure adopting the bearing to support the sliding plate has the following characteristics: the third bearing 23 restricts the movement or movement trend of the sliding plate 50 in the radial direction, and balances the lateral component of the sliding plate 50, so that the sliding plate 50 passes through The lateral force of the plunger 70 on the cylinder 80 is eliminated or greatly reduced, which improves the working reliability, working pressure and working life of the axial piston pump or motor.

At the same time, it is particularly obvious that the return stroke of the axial piston pump or motor is greatly simplified. The return structure includes a restraining device provided on the side of the valve sliding plate pair, and the restraining device restricts the slide plate 50 in the return stroke. Keep away from the end face of the swash plate 40 under the action of force.

Further, the restraining device includes a stop portion 57 protruding to the outside on the side of the sliding plate 50 close to the hydrostatic support surface 51 and an engagement device 140 provided on the support stop portion 41a. The portion 57 is used to restrict the movement of the third bearing 23, and the engaging device includes an engaging peripheral groove provided on the supporting stop 41a and adjacent to the third bearing 23 and an engaging inner peripheral groove provided on the engaging inner peripheral groove. A retaining spring (not shown) restricts the sliding plate from moving away from the end surface of the swash plate 40 in a manner that restricts the third bearing 23 from moving outward.

Predictably, an elastic washer (not shown) can also be appropriately provided between the stop portion 57 and the third bearing 23 or between the circlip and the third bearing 23, so that the restraint assembly can not only restrict the sliding plate from moving away from the swash plate, Outside the end face, there is also a certain initial preload to maintain the preload state of the sliding plate and the swash plate.

In the same way, the restraining method of the restraining device 140 can also be realized by the interference fit between the third bearing 23 and the swash plate supporting block 41a, which is provided on the swash plate supporting block 41a and adjacent to the third bearing 23 The engaging peripheral groove and the circlips matched with the engaging peripheral groove play a further restraining effect.

It should be noted that since there is no valve plate at the end of the cylinder body 80 and there is no friction pair supported by a static pressure oil film, it is not necessary to apply a pre-tightening force to the end of the cylinder body 80 to achieve the purpose of sealing. The restraint device 140 is provided on the disc pair to meet the return requirements of the plunger. There is no need to add additional pre-tensioning or return components such as the central spring, so that the restraint device greatly simplifies the structure and avoids the fatigue damage of the central spring And the phenomenon of fracture. Of course, in order to prevent the axial piston pump from being placed in a non-horizontal position (such as storing, transporting, turning it upside down during use, etc.), the cylinder 80 moves along the main shaft 10 in the direction of the sliding plate, on the main shaft 10, adjacent to the end surface of the cylinder. A cylinder circlip 141 is provided to restrict the string movement of the cylinder 80.

Example 2:

As shown in Figures 11 and 12, the main difference from the first embodiment is that a valve plate 90 is sandwiched between the sliding plate 50 and the swash plate 40 in the valve plate pair. The static pressure support surface 51 is supported on the valve plate 90. And maintain a sliding fit with the valve plate 90. The valve plate is fixed on the swash plate by means of pins or the like. The valve plate 90 is provided with a high pressure valve port 93 and a low pressure valve port 92, as shown in FIG. The high pressure distribution port 93 and the low pressure distribution port 92 are respectively communicated with the low pressure distribution window 43 and the high pressure distribution window 44 on the swash plate. The low-pressure distribution port 92 and the high-pressure distribution port 93 can be arranged in a symmetrical or asymmetrical structure with respect to the central plane. For example, the high-pressure distribution port 93 is provided with a plurality of waist-shaped windows (not shown); in order to make the distribution plate have A certain pre-boost and pre-pressure function can rotate the low-pressure distribution port 92 and the high-pressure distribution port 93 to a certain angle along the central axis of the distribution plate; in particular, the low-pressure distribution port 92 can also be provided at the end of the low-pressure distribution port 92 Port 92 transitions to the direction of the high-pressure port 93 and at the end of the high-pressure port 93 is provided with a throttle groove or hole that transitions from the high-pressure port 93 to the low-pressure port 92 to change from high pressure to low pressure or low pressure to high pressure. The role of pre-buck and pre-boost.

In the embodiment of the present disclosure, the advantage of sandwiching the valve plate 90 between the sliding plate 50 and the swash plate 40 is that it is easier and cheaper to replace the valve plate later than replacing the swash plate.

Example 3:

As shown in Figure 11, the main difference from other embodiments is that the axial piston pump is an axial piston pump with an auxiliary pump. In the embodiment shown, an auxiliary pump 39 is connected to the end of the main shaft 10. The auxiliary pump 39 is used to supply oil or provide hydraulic operating force for the hydraulic system; the auxiliary pump 39 is connected with the end cover 33 by bolts, and the external auxiliary pump 39 may be a gear pump or a vane pump. Predictably, the main shaft can be set to extend out of the housing and connect with another main pump to form a series double pump structure.

Example 4:

As shown in Figure 13, the main difference from other embodiments is that one end of the cylinder 80 abutting the spindle shoulder 13 is provided with a one-way valve 110 that only allows oil to enter the plunger hole 81 from the housing cavity. The one-way valve 110 is fixedly connected to the cylinder body 80. The one-way valve 110 includes a valve body 111 fixedly connected to the cylinder body, a valve core 112 arranged inside the valve body, a retaining ring 114 fixed on the valve body 111, and In the spring 113 between the valve core 112 and the retaining ring 114, the one-way valve 110 only allows low-pressure oil to flow from the second cavity 35 of the housing into the plunger hole 81, that is, when the cylinder 80 is in the oil-absorbing state, The spool 112 of the one-way valve 110 is opened, and low-pressure oil enters the plunger hole 81 from the second cavity 35 of the housing. When the cylinder 80 is in the draining state, the spool 112 of the one-way valve 110 is closed.

When used as a pump, its oil flow is as follows: when sucking oil, there are two oil inlet passages, one of which is: low pressure oil enters the flow passage from the oil inlet 33a of the end cover 33, and passes through the groove-shaped low pressure port of the swash plate in turn 46. The low-pressure distribution window 43, the oil chamber 53a of the sliding plate, the large-diameter oil through hole 53, the plunger ball socket 58, and the large-aperture plunger center hole 72 reach the plunger hole 81 of the cylinder block; the other path is: through With the one-way valve 110 provided at the end of the cylinder 80, the low-pressure oil directly enters the plunger hole 81 of the cylinder from the second cavity 35 of the housing; when the oil is drained, the high-pressure oil passes through the plunger hole 81 of the cylinder in turn. The large diameter plunger center hole 72, the plunger ball socket 58, the large diameter oil through hole 53, the oil chamber 53a, the high pressure distribution window 44, the groove-shaped high pressure port 46, and finally discharge from the end cover oil outlet 33b.

The advantages of having two oil inlet passages when sucking oil are: one is that the heat generated by the various parts of the pump can be taken away through the one-way valve 110 in time to prevent the temperature of the oil in the pump from rising and causing its failure; the other is that it can be increased The oil suction channel improves the self-priming capacity of the pump; third, the oil return pipeline and cooling device of the pump can be eliminated, which reduces the manufacturing and use costs of the pump.

Example 5:

As shown in Figure 14, in order to have a better sealing effect, a pre-sealing device is provided between the sliding plate and the cylinder. The pre-sealing device includes a central spring 100, a retaining ring 101, a spherical hinge 103, and the spherical hinge 103 When abutting on the sliding plate or pressure plate, the retaining ring is arranged on the cylinder 80. During installation, the central spring 100 has a certain amount of pre-compression, so that the sliding plate 50 tightly abuts on the swash plate 40. Therefore, it can be predicted that the pre-sealing of the sliding plate and the swash plate includes setting a central spring, setting a restraining device, or a combination of the two.

Based on the above technical solutions, the beneficial effects of the embodiments provided in the present disclosure at least include:

1. At least one embodiment of the present disclosure integrates the functions of flow distribution, variable tilt, and hydrostatic support into the valve slide pair. The main friction pairs are the valve slide pair and the plunger pair, which have the following advantages: First, because of the cylinder block There is no valve plate at the end, which reduces one valve pair, thereby reducing oil leakage and improving its volumetric efficiency; second, because the end of the cylinder does not need to abut on the valve plate, the end of the cylinder There is no need for precision machining, which greatly reduces the difficulty of manufacturing. At the same time, the life of the cylinder body is longer, the later maintenance is less, and the use cost is reduced; third, because the sliding plate is supported on the swash plate with bearings and the plunger uses a hingeless cone The connecting rod plunger of the circular structure or the connecting rod plunger with ball head or the spherical plunger with universal hinge on both ends, so the lateral force of the plunger is greatly reduced, and the cylinder overturning phenomenon is eliminated or reduced; Fourth, because there is no valve plate at the end of the cylinder, even if there is some lateral force, problems such as failure due to partial wear will not occur.

2. In the sliding plate supported through-shaft plunger pump or motor provided by at least one embodiment of the present disclosure, the return mechanism is a restraining device arranged on the valve sliding plate pair. The restraining device has a very simplified structure and does not require additional The center spring, thimble, ball hinge, return disk and other parts are installed, and there is no phenomenon such as the failure of the center spring due to fatigue damage and the failure of the seal between the cylinder and the valve plate and the tilt and eccentric wear of the sliding shoe.

3. In the sliding disc-supported through-shaft plunger pump or motor provided by at least one embodiment of the present disclosure, the restraining device is compared with a fixed clearance forced return mechanism. The restraining device of the present disclosure, such as a circlip and a third bearing, are static Contact, there are no problems such as wear. Another type of fixed clearance forced return mechanism is to use screws to fix the pressure plate on the swash plate. The pressure plate and the return plate are in dynamic contact, that is, there is always abrasion between the two, which causes mechanical noise and cannot maintain a constant gap for a long time. Early failure. At the same time, from the perspective of installation requirements, the circlip in the embodiment provided by the present disclosure is simple to install and has a guaranteed accuracy, while another type of fixed clearance forced return requires machining and installation accuracy. The clearance is too large or too small to meet the requirements, and This gap is dynamically changing.

4. In at least one embodiment of the present disclosure, the oil through holes on the sliding plate and the central hole of the plunger are both large in diameter. Therefore, the clogging of oil can be prevented and the sensitivity to oil can be reduced. At the same time, the central hole of the large diameter plunger reduces The mass of the plunger helps to reduce the centrifugal force of the plunger.

5. The sliding plate structure of at least one embodiment of the present disclosure is an integral structure, instead of a structure that uses multiple independent sliding shoes and uses a return plate to return. The plunger and the sliding plate and the sliding plate in the present disclosure The connection with the pressure plate is more reliable, avoiding the wear of the neck and shoulder of the shoe, shear damage and cracking of the drilling part of the return plate, thereby improving the working reliability of the swash plate plunger pump or motor. At the same time, the centrifugal force and frictional force of each part of the sliding plate cancel each other out, avoiding the overturning of a single shoe under the combined action of the centrifugal torque caused by the circumferential motion and the frictional torque generated by the rotation of the cylinder during high-speed movement. The sliding plate structure wears evenly, eliminating or reducing the partial wear of the original sliding shoe pair.

The above content is a further detailed description of the present disclosure in combination with specific preferred technical solutions, and it cannot be considered that the specific implementation of the present disclosure is limited to these descriptions. For those of ordinary skill in the technical field of the present disclosure, without departing from the concept of the present disclosure, several simple deductions or substitutions can be made, and all technical solutions and improvements thereof that do not depart from the spirit and scope of the present disclosure All of them shall be covered in the scope of the claims of the present disclosure.

Claims

A sliding plate supported through-shaft plunger pump or motor, comprising a main shaft (10), a cylinder block (80) supported on the main shaft (10) and rotating synchronously therewith, and a valve sliding plate pair. The main shaft (10) is It is supported on the bearings at both ends in the form of penetrating the cylinder block (80) and the valve sliding plate pair. The valve sliding plate pair includes a swash plate (40) and a sliding plate (50) supported on the swash plate (40). The sliding plate (50) is an integral structure. The opposite end surface of the sliding plate (50) and the swash plate (40) is provided with a static pressure support surface (51), and the other end surface of the sliding plate (50) is provided with a plurality of The plunger ball socket (58) is provided with an oil through hole (53) connecting the plunger ball socket (58) and the static pressure bearing surface (51) on the sliding plate (50), the swash plate (40) A distribution oil groove (42) is provided on the upper part, and the distribution oil groove (42) communicates with the oil inlet and outlet ports (33a, 33b) provided on the end of the plunger pump or the motor housing near the swash plate (40), A third bearing (23) is arranged between the sliding plate (50) and the swash plate (40), and the sliding plate (50) is supported on the third bearing (23) in a constrained state along its radial direction.
The sliding plate supported through-shaft plunger pump or motor according to claim 1, wherein a plurality of oil chambers (53a) are provided on the hydrostatic bearing surface (51) of the sliding plate (50), and the oil The chambers (53a) are distributed on the static pressure support surface (51) with the sliding disc axis (50C) as the center, and are arranged between the bottom of each oil chamber (53a) and the corresponding plunger ball socket (58) There is an oil through hole (53), the oil through hole (53) as the main channel for sucking and discharging oil and introduces the oil between the hydrostatic bearing surface (51) and the swash plate (40) to make the hydrostatic support The surface (51) and the end surface of the swash plate (40) form a static pressure oil film support with clearance fit.
The sliding plate supported through-shaft plunger pump or motor according to claim 1, wherein the hydrostatic bearing surface (51) is on the sliding plate (50) and is located along the axis of the sliding plate to the side of the swash plate. The extended boss surface (52) is provided with a plurality of oil chambers (53a) and a sealing part for sealing oil, the sealing part surrounds the oil chamber (53a) The state is set on the inner and outer circumferences of the oil chamber (53a), and the sealing portion includes an inner seal portion (55) and an outer seal portion (54) provided radially inward and outward of the oil chamber (53a), and an adjacent oil chamber ( 53a) The gap seal part (56) between.
The sliding plate supported through-shaft plunger pump or motor according to claim 1, wherein the outer periphery of the swash plate (40) is provided with a raised support stop (41a), and the third bearing (23) It is sandwiched between the outer side of the sliding plate (50) and the inner side of the supporting block (41a), and the sliding plate (50) is supported on the third bearing (23) in a state of being restrained in the radial direction.
The sliding plate supported through-shaft plunger pump or motor according to claim 4, wherein a restraining device is provided on one side of the flow distribution sliding plate pair, and the restraining device is included in the sliding plate (50) near the hydrostatic support One side of the surface (51) has a stop part (57) protruding outward and an engaging device (140) provided on the supporting stop part (41a), and the engaging device (140) is used to restrain the The outward movement of the third bearing (23) restricts the sliding plate (50) away from the end surface of the swash plate (40).
The sliding plate supported through-shaft plunger pump or motor according to claim 1, wherein a plurality of oil chambers (53a) are provided on the static pressure bearing surface (51), and the swash plate (40) A waist-shaped low-pressure distribution window (43) and a waist-shaped high-pressure distribution window (44) are provided on the end face opposite to the sliding plate (50), and the high and low-pressure distribution windows (44, 43) are connected to the oil chamber (53a). ) Intermittently communicated, the supporting surface of the swash plate (40) opposite to the end cover (33) has a cylindrical supporting surface (45) shaped into a cylindrical shape, and the cylindrical supporting surface (45) of the swash plate (40) There are groove-shaped low-pressure ports (46) and groove-shaped high-pressure ports (47) in the shape of grooves. The groove-shaped low-pressure ports (46) and the groove-shaped high-pressure ports (47) are respectively connected to the low-pressure distribution window (43). ) And the high-pressure distribution window (44) correspondingly communicate.
The sliding plate supported through-shaft plunger pump or motor according to claim 6, wherein the cylindrical support surface (45) of the swash plate (40) is provided with a groove-shaped low-pressure port (46) and a second housing The communicating slot (48) of the cavity (35).
The sliding plate supported through-shaft plunger pump or motor according to claim 1, wherein the first bearing (21) supporting the main shaft (10) comprises at least one centripetal thrust bearing or thrust bearing, and the cylinder block The plunger hole (81) of (80) is a structure with one end closed and one end open. During operation, hydraulic axial force acts on the end surface of the cylinder with the closed end of the plunger hole (81) and passes through the first bearing (21) Transfer to the housing of the plunger pump or motor.
The sliding plate supported through-shaft plunger pump or motor according to claim 1, wherein an auxiliary pump (39) or a main pump is connected to the end of the main shaft (10) to form a series double pump structure.
The sliding plate supported through-shaft plunger pump or motor according to claim 1, wherein one end of the cylinder (80) is provided with a one-way valve (110), and the one-way valve (110) is used for communication The plunger hole (81) of the cylinder (80) and the internal cavity of the housing, and the one-way valve (110) only allows hydraulic oil to enter the plunger hole (81) from the cavity of the housing.
The sliding plate supported through-shaft plunger pump or motor according to claim 1, wherein the plunger (70) comprises a connecting rod plunger with a tapered structure or a connecting rod column with ball heads at both ends A plug or a spherical plunger with a universal hinge. One end of the plunger (70) can be detached into the plunger hole (81) of the cylinder (80) in a reciprocating manner relative to the cylinder (80) , The other end is fixed on the plunger ball socket (58) of the sliding plate (50) in a restricted and tiltable state with respect to the end surface of the sliding plate (50), and a connecting plunger ball is provided on the plunger (70) The socket and the plunger hole are the large bore plunger center hole.
The sliding plate supported through-shaft plunger pump or motor according to claim 1, wherein a pre-sealing device is provided between the sliding plate (50) and the cylinder (80), and the pre-sealing device includes a center A spring (100), a retaining ring (101), a ball hinge (103), the ball hinge (103) abuts on the sliding plate (50) or the pressure plate (40), and the retaining ring (101) is arranged On the cylinder (80), the pre-sealing device makes the sliding plate (50) tightly abut on the swash plate (40) through the action of the central spring (100).
The sliding plate supported through-shaft plunger pump or motor according to claim 5 or 12, wherein the pre-sealing between the sliding plate and the swash plate comprises a combination of a pre-sealing device provided with a central spring and a restraining device.
The sliding plate supported through-shaft plunger pump or motor according to any one of claims 1 to 13, wherein a valve plate (90) is sandwiched between the sliding plate (50) and the swash plate (40) , The sliding plate (50) is supported on the valve plate (90) and maintains a sliding fit with the valve plate (90), and the valve plate (90) is provided with high and low pressure valve ports (93, 92), hydraulic oil Under the reciprocating action of the plunger, it flows through the valve oil groove (42) on the swash plate (40), the valve port on the valve plate, the oil through hole (53) on the sliding plate, and the plunger center hole (72) to realize the hydraulic oil Inhale and discharge.