WO2020182205A1

WO2020182205A1 - Duplex axial plunger motor

Info

Publication number: WO2020182205A1
Application number: PCT/CN2020/079226
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: CN110067692A

Abstract

A duplex axial plunger motor, comprising two slide plate-type non-hollow shaft plunger motors and an end base (33) sandwiched between the two slide plate-type non-hollow shaft plunger motors. Each slide plate-type non-hollow shaft plunger motor comprises a distribution slide plate sub-assembly, a main shaft (10), a cylinder body (80), and a plunger (70). The distribution slide plate sub-assembly comprises a swash plate (40) and a slide plate (50) supported on the swash plate (40). The slide plate (50) is an integral structure, and the end face of the slide plate (50) facing the swash plate (40) is provided with a static pressure bearing surface (51). A plurality of plunger ball sockets (58) are provided on the end face of the slide plate (50) facing the cylinder body (80). An oil through hole (53) communicated with the plunger ball sockets (58) and the static pressure bearing surface (51) is provided on the slide plate (50). The swash plate (40) is provided with a distribution oil groove (42) communicated with oil inlet and outlet (33a, 33b). For the duplex axial plunger motor, the structure is greatly simplified, the number of friction pairs is reduced, and the performance of the axial plunger motor is improved.

Description

Duplex axial piston motor

This application claims the priority of the Chinese patent application No. 201910189060.5 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 embodiment of the present disclosure relates to an axial plunger motor, and more particularly to a double-connected non-through shaft plunger motor.

Background technique

The axial piston motor is one of the most widely used hydraulic components in modern hydraulic transmission. Among them, the hingeless inclined axis motor and the sliding shoe swash plate axial piston motor are the two most widely used and most important types of shafts. To the plunger motor. These two motors are still in competition, and each is constantly improving and developing.

Summary of the invention

At least one embodiment of the present disclosure provides a dual axial plunger motor, including two sliding plate non-through shaft plunger motors and a terminal sandwiched between the two sliding plate non-through shaft plunger motors Each sliding plate type non-through shaft plunger motor includes a main shaft, a swash plate, a sliding plate, a plunger and a cylinder. The sliding plate is an integral structure and is supported on the swash plate to form a flow distribution sliding plate sub-assembly. The end surface of the sliding plate opposite to the swash plate is provided with a static pressure support surface, the end surface of the sliding plate opposite to the cylinder is provided with a plurality of plunger ball sockets, and the sliding plate is provided with a connecting plunger ball socket and The oil through hole of the hydrostatic bearing surface, one end of the plunger is placed in the plunger ball socket, the other end is inserted into the cylinder, one end of the plunger center hole inside the plunger is connected to the oil through hole, and the other end is connected to the The plunger hole in the cylinder communicates with the swash plate. The swash plate of the two sliding plate type non-through shaft plunger motors is supported on a common end seat. The flow distribution oil groove and the end The oil inlet and outlet ports set on the seat are connected, and the high-pressure oil flows through the distribution oil groove, the oil through hole, the plunger center hole and the plunger hole on the swash plate to drive the cylinder body and the main shaft to rotate synchronously.

For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, a plurality of oil chambers are provided on the hydrostatic bearing surface of the sliding plate, and the oil chambers are spaced apart from the axis of the sliding plate. Distributed on the static pressure support surface, an oil through hole is provided between the bottom of each oil chamber and the corresponding plunger ball socket. The oil through hole serves as the main channel for sucking and discharging oil and introduces the oil into the static pressure support Between the surface and the swash plate, the static pressure supporting surface and the end surface of the swash plate form a static pressure oil film support with clearance fit.

For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, a sealing portion for sealing oil is provided on the boss surface, and the sealing portion includes a radially inner and outer side of the oil chamber. The inner sealing part and the outer sealing part, and the interval sealing part arranged between adjacent oil chambers.

For example, in the dual axial plunger 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 is provided with The low-pressure distribution window and the high-pressure distribution window are intermittently communicated with the oil chamber. The supporting surface on the swash plate opposite to the end seat has a cylindrical supporting surface formed into a cylindrical shape. The cylindrical supporting surface is provided with a groove-shaped low-pressure port and a groove-shaped high-pressure port that are configured in a groove shape, and the groove-shaped low-pressure port and the groove-shaped high-pressure port are respectively communicated with the low-pressure distribution window and the high-pressure distribution window.

For example, in a dual axial plunger motor provided by an embodiment of the present disclosure, the oil through hole on the sliding plate and the plunger center hole on the plunger are both large-diameter main oil holes for sucking and discharging oil. structure.

For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, the axial plunger motor is configured as a centralized variable structure, and the end seat is provided with a variable mechanism including a spool valve, two The shaft pins of the two opposite swash plates are connected to a common slide valve. Under the action of the hydraulic pressure and spring force of the variable mechanism, the slide valve drives the two swash plates to rotate synchronously to realize synchronous variable.

For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, the axial plunger motor is configured as a separate variable structure, and the housing of the axial plunger motor is connected with two Variable mechanism, the variable mechanism is respectively connected with the corresponding swash plate, and realizes independent variable under the action of hydraulic pressure and spring force of the respective variable mechanism.

For example, in a dual axial plunger motor provided by an embodiment of the present disclosure, the sliding plate type non-through shaft plunger motors distributed on both sides of the end seat are combined in a variable manner of swash plate, and the specific combination method is two sides Slip-disk type non-thru-shaft plunger motors are of variable type structure; or both sides-slip-disk type non-thru-shaft plunger motors are of quantitative structure; or slide-plate type non-thru-shaft plunger motors on both sides are of quantitative structure , The other is a variable structure.

For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, one end of the main shaft of the two sliding disc type non-through shaft plunger motors extends out of the housing and is supported on the first bearing, and the other One end cantilever supports the cylinder body and rotates synchronously with the cylinder body. The plunger hole of the cylinder body is a structure with one end closed and one end open. The closed end of the cylinder body is not provided with a distribution pair. The main shaft and When the cylinder is rotating, the hydraulic axial force is transmitted to the housing through the cylinder through the first bearing.

For example, in the dual axial plunger 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 hydraulic axial force acts on the plunger during operation. The hole closes the end surface of the cylinder at one end and is transmitted to the casing of the plunger pump or the motor through the first bearing.

For example, in a dual axial piston motor provided by an embodiment of the present disclosure, a third bearing is interposed between the swash plate and the sliding plate, and the sliding plate is in a state of being restricted in its radial direction. Supported on the third bearing.

For example, in the dual axial piston motor provided by an embodiment of the present disclosure, the middle part of the swash plate has a supporting shaft or a supporting shaft pin extending outward, the sliding plate is provided with a central through hole, and the first The three bearings are sandwiched between the inner wall of the central through hole of the sliding plate and the supporting shaft or the supporting shaft pin, and the sliding plate is supported on the third bearing in a state of being restrained in the radial direction.

For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, the outer periphery of the swash plate is provided with a raised support stop, and the third bearing is sandwiched between the outer side of the swash plate and the support stop. Between the inner sides, the sliding plate is supported on the third bearing in a state of being restrained in its radial direction.

For example, in the dual axial plunger 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 a ball head or a belt on both ends. A type of spherical plunger with a hinge, one end of the plunger can be inserted into the plunger hole of the cylinder in a reciprocating manner relative to the cylinder, and the other end is fixed on the sliding plate in a state where the distance from the end surface of the sliding plate is restricted and can be tilted. In the plunger ball socket of the disc, the plunger is provided with a large-aperture plunger center hole communicating the plunger ball socket and the plunger hole.

For example, in the dual axial plunger motor provided by an embodiment of the present disclosure, a valve plate is sandwiched between the sliding plate and the swash plate, and the sliding plate is supported on the valve plate and kept sliding with the valve plate In cooperation, the valve plate is provided with high and low pressure valve ports, and the high pressure oil flows through the valve oil groove on the swash plate, the valve port of the valve plate, the oil chamber of the sliding plate, the oil through hole, the center hole of the plunger and the cylinder block. The plunger hole drives the cylinder body and the spindle to rotate synchronously.

Description of the drawings

Figure 1 is a schematic diagram of a swash plate type non-through shaft plunger motor;

Fig. 2 is an embodiment of the double-joint concentrated variable axial piston motor in the present disclosure;

Figure 3 is a cross-sectional view of the axial plunger motor A-A of Figure 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 in Fig. 4 in this disclosure;

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

7 is a plan view of the supporting surface of one end of the swash plate opposite to the sliding plate in the present disclosure;

Figure 8 is another plan view of the supporting surface of one end of the swash plate opposite to the sliding plate in the present disclosure;

Figure 9 is a plan view of the swash plate opposite to the end seat in this disclosure;

Figure 10 is a D-D cross-sectional view of the swash plate of Figure 9 in this disclosure;

FIG. 11 is an embodiment of a double-connected concentrated variable axial piston motor adopting a sliding disk internal support method in this disclosure;

Fig. 12 is an E-E sectional view of the axial piston motor in Fig. 11 in this disclosure;

FIG. 13 is an embodiment of a dual concentrated variable axial plunger motor adopting a sliding disk external support method in this disclosure;

Fig. 14 is an embodiment of the double-coupled split variable axial piston motor in this disclosure;

15 is a cross-sectional view of a sliding plate type non-through shaft plunger motor including a valve plate in this disclosure; and

FIG. 16 is a schematic diagram of the structure of the quantitative sliding disc type axial piston motor in this disclosure.

Reference signs: 10 is the spindle, 10C is the spindle axis, 12 is the spindle shoulder, 21 is the first bearing, 21a is the radial ball bearing, 21b is the 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 seat, 33a is the oil inlet, 33b is the oil outlet, 33c is the spool valve, 33d is the flow channel, 33e is the sliding surface, 34 is The first cavity, 35 is the second cavity, 38 is the variable connection part, 40 is the swash plate, 41 is the support surface of the swash plate, 41a is the support block, 42 is the distribution oil groove, 43 is the low pressure distribution window, 44 is the high pressure 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 connecting slot, 49 is a supporting shaft pin, 50 is a sliding plate, 50C is a sliding plate axis, and 51 is a hydrostatic support Surface, 52 is the boss surface, 53 is the oil through hole, 53a is the oil chamber, 54 is the outer sealing part, 55 is the inner sealing part, 56 is the interval sealing part, 58 is the plunger ball socket, 60 is the pressure plate, 70 is the column Plug, 71 is the plunger ball head, 72 is the plunger center hole, 73 is the tapered rod, 74 is the plunger, 80 is the cylinder, 81 is the plunger hole, 82 is the spindle assembly hole, and 84 is the cylinder liner , 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 valve, 93 is the high pressure valve, 100 is the central spring, 101 is the steel ball, 102 is the sleeve, and 103 is the outer jacket. 120 is a sliding shoe, 130 is a return disk, 140 is a clamping device, and 141 is a cylinder circlip.

detailed description

As shown in Figure 1, it is a typical structure of a non-through shaft swash plate type axial piston motor, which includes a swash plate 40, a sliding shoe 120, a plunger 70, a cylinder 80, a valve plate 90, a main shaft 10, and a center Spring 100, return plate 130 and other components. One end of the main shaft 10 is supported on a bearing at one end, and the other end penetrates the valve plate 90 and is connected to the cylinder block 80 by a key. The central spring 100 connects the sliding shoe 120 through the sleeve 102 and the steel ball 101. After pressing, the central spring 100 compresses the cylinder block and the valve plate through the outer sleeve 103, a cylinder liner 84 is provided on the outer peripheral surface of the cylinder block 80, and a second bearing 22 is interposed between the cylinder liner 84 and the motor housing 32.

The disadvantages of this kind of non-through shaft swash plate axial plunger motor are: First, under the action of hydraulic pressure, the swash plate of the axial plunger motor produces a large lateral force on the plunger, and the lateral component force It is transmitted to the cylinder block and the main shaft via the plunger, causing a wedge-shaped gap between the cylinder block and the valve plate, which increases the power loss of the motor, and makes the sealing surface between the cylinder block and the valve plate come into partial contact, causing the cylinder block and the valve plate. The surface between the disks is burned, which makes the motor completely lose its function; second, it is difficult to form a series motor, especially the high-power, high-pressure and large-flow series variable axial piston motor is difficult to achieve; third, the external structure is large, The noise is high.

With the increasing demand of large-scale machinery for high-pressure and large-displacement axial piston motors, this traditional single non-through shaft swash plate axial piston motor, whether in terms of displacement, power, or structural reliability Neither can meet its requirements.

The purpose of the present disclosure is to provide a dual axial piston motor in view of the problems of non-thru-shaft axial piston motors that cannot be connected in series, are low in reliability, and are too large in size. Demand for hydraulic motors with high power, high pressure and large flow, compact structure and high reliability.

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 the convenience 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 spindle of the axial plunger motor stands horizontally, “longitudinal”, “lateral”, “up”, and “up” are used in the description. The terms "down", "front", "rear", "left", "right", "horizontal", "bottom", "inner", "outer" and other terms are all used with reference to this position, just for ease of description The present disclosure and simplified description do not indicate or imply that the device or element referred to must have a specific orientation, and a specific orientation structure and operation. It should be understood that the present disclosure can be manufactured and stored in an orientation different from the stated position. , Delivery, use and sale.

Example 1:

As shown in Figures 2-10, this is an embodiment of the double-connected centralized variable sliding plate type axial piston motor of the present disclosure. In the preferred embodiment shown, the double-connected axial piston motor includes two sliding plates. A disc type non-through shaft plunger motor and an end seat 33 sandwiched between two sliding disc type non-through shaft plunger motors, each sliding disc type non-through shaft plunger motor includes a flow distribution sliding plate sub-assembly and a main shaft 10 , A cylinder 80 and a plunger 70 cantilever supported on one end of the main shaft 10 and rotating synchronously with the main shaft 10, the flow distribution sliding plate sub-assembly 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 of the sliding plate 50 and the swash plate 40 is provided with a static pressure support surface 51, and the sliding plate 50 is provided with a plurality of plunger ball sockets 58 distributed on one end surface. A plurality of oil chambers 53a on the other end surface and a large-diameter oil through hole 53 connecting the plunger ball socket 58 and the oil chamber 53a. One end of the plunger 70 is placed in the plunger ball socket 58, and the other end Inserted into the cylinder 80, one end of the plunger center hole 72 inside the plunger 70 communicates with the oil through hole 53, and the other end communicates with the plunger hole 81 in the cylinder 80. The swash plate 40 is provided with Portion oil groove 42. The swashplates 40 of the two sliding plate type non-through shaft plunger motors are supported on a common end seat 33. The port flow groove 42 and the oil inlet 33a and the oil outlet provided on the end seat 33 33b is connected, the high-pressure oil flows through the distribution oil groove 42 on the swash plate 40, the oil chamber 53a of the sliding plate 50 and the oil through hole 53, the large-diameter plunger center hole 72, and the cylinder plunger hole 81 to drive the cylinder 80 and The main shaft 10 rotates.

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 embodiment of the present disclosure, the pore diameter of the oil through hole 53 is increased to be similar to or consistent with the widthwise dimension of the waist-shaped oil chamber 53a compared with the pore diameter of the corresponding part in the above-mentioned slender pore structure.

As shown in Figure 2, in the embodiment of the dual axial plunger motor, the end seat 33 is arranged in the middle, and each of the left and right sides has a sliding plate type non-through shaft plunger motor. In particular, the sliding plate on the left and right sides The non-through shaft plunger motor is a symmetrical structure. The sliding disc type non-through shaft plunger motors on the left and right sides share one end seat 33, which is used to close one end opening of the motor housing on both sides, and the sliding disc type non-through shaft plunger motors on the left and right sides and the end seat 33 is connected by bolts. Since the sliding plate type non-through shaft plunger motors on both sides of the end seat are similar in structure, for simple description, the sliding plate type non-through shaft plunger motor on one side is taken as an example.

The shells of the sliding disc type non-thru-shaft plunger motors on the left and right sides can be set in a double-piece structure or an integral structure. When the shell is set in a double-piece structure, the shell includes a front shell 31 and a shell body 32. The front shell 31 has a first cavity 34 for accommodating the first bearing 21, and the housing body 32 has a second cavity 35 for accommodating the cylinder and the valve sliding plate pair. In particular, the housing of the axial piston motor can also be configured as an integral structure, that is, the motor front shell 31 and the shell body 32 can be made into an integral structure, as shown in FIGS. 11 to 14.

Wherein, the end seat 33 is used to close the opening at one end of the shell body 32. The end seat 33 is provided with the oil inlet 33a and the oil outlet 33b of the motor, the flow passage 33d communicating with the swash plate distribution oil groove 42 and the supporting swash plate 40 sliding arc surface 33e; when the axial piston motor is set as a centralized variable type axial piston motor, a variable mechanism for variable swing is provided on the end seat 33, and the variable mechanism includes a slide valve 33c, the Axle pin holes are respectively provided on both sides of the spool valve 33c, and the axle pins 49 on the two opposed swash plates 40 are connected to the same spool valve 33c, and the axle pins 49 can rotate in the axle pin holes. Under the action of the variable mechanism, the slide valve 33c moves and drives the swash plate 40 together with the slide plate 50 to rotate in the second cavity 35 to realize the synchronous variable of the motors at both ends of the end seat. The advantage of this structure is that only one variable mechanism can be set to realize the same variable of the two serial motors, so the structure is simple and the variables are convenient, especially for the situation that requires the simultaneous movement of the two shaft ends of the dual axial piston motor. Advantage.

The main shaft 10 is cylindrical and penetrates the first cavity 34 of the motor front housing 31. A first bearing 21 is interposed between the main shaft and the motor front housing 31. One end of the main shaft 10 extends out of the front housing 31 for external load. , And supported on the motor front housing 31 via a first bearing 21. The main shaft axis 10C of the main shaft 10 coincides with the cylinder center axis 80C of the cylinder block 80. One end of the main shaft 10 is supported on the first bearing 21, The other end is connected with the cylinder 80 by a key. The main shaft 10 cantilever supports the cylinder 80 and rotates synchronously with the cylinder 80. The main shaft 10 can rotate freely around its own axis via a first bearing 21. The first bearing 21 includes at least A centripetal thrust bearing or thrust bearing 21b is provided with a spindle shoulder 12 on the spindle close to the end of the cylinder 80. The spindle shoulder 12 is used to stop the cylinder and act on the axial hydraulic pressure on the cylinder. The force is transmitted to the centripetal thrust bearing or thrust bearing 21b.

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 of the motor. The cylinder 80 has a uniform circumferential direction about the central axis 80C of the cylinder. A plurality of distributed 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 spindle 10 passes through the spindle assembly hole 82 of the cylinder body 80 and is connected to the cylinder body 80 by a key connection on the outer circumference of the shaft body, so The cylinder 80 is supported on the main shaft 10 in a manner that it moves synchronously with the main shaft 10.

When the motor is working, the end of the cylinder 80 abuts on the main shaft shoulder 12 and rotates synchronously with the main shaft. The axial hydraulic pressure and central spring force are transmitted to the radial thrust ball bearing or tapered roller bearing through the main shaft shoulder 12 Or the thrust bearing 21b, and then to the motor housing.

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 has a large-diameter through-hole structure, which serves as a channel for sucking and discharging oil. The plunger portion 74 is often provided with at least one sealing ring for sealing the liquid. The tapered rod portion 73 has a tapered shape that gradually increases from the ball end of the plunger to the plunger portion 74. When the plunger 70 moves to a certain position At this time, the tapered rod portion 74 is in contact with the inner circumferential surface of the cylinder plunger hole 81 and plays a role of force transmission. 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.

As shown in Figures 4, 5 and 6, the end face of the sliding plate 50 opposite to the swash plate is provided with a static pressure support surface 51, the sliding plate axis 50C and the spindle axis 10C are at a certain angle, and the static pressure support The surface 51 is supported on the swash plate 40 and always maintains a sliding fit with the swash plate 40. The static pressure support surface 51 is provided with a plurality of lumbar-shaped oil chambers 53a. Preferably, the oil chambers 53a are smooth The disc axis 50C is uniformly 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 configured so that the boss surface 52 of the sliding plate and the supporting surface of the swash plate 40 abut against each other in a slidable manner. A plurality of oil chambers 53a are provided on the boss surface 52 corresponding to the position of the plunger ball socket 58. Preferably, the oil chambers 53a are distributed evenly on a common circumference centered on the sliding disc axis 50C. The boss surface 52 is on.

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 set on the inner and outer circumferences of the oil chamber 53a, and the sealing portion includes an inner sealing portion 55 and an outer sealing portion 54 distributed radially inward and outward of the oil chamber 53a, and an interval sealing portion distributed between adjacent oil chambers 53a 56. 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 Figures 5 and 6, 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, and the plunger ball sockets 58 form openings on the end surface of the sliding plate 50. A substantially hemispherical recess, the plunger ball sockets 58 support the plunger ball 71 in a state evenly distributed on the common circumference of the spool axis 50C. After the plunger 70 is mounted on the plunger ball socket 58, It is fixed on the end surface of the sliding plate 50 by the pressing plate 60, so that the movement of the plunger 70 relative to the end surface of the sliding plate 50 is restricted. 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.

Figures 7-10 show an embodiment of the swash plate. The swash plate has a swash plate support surface 41 that matches the static pressure support surface of the swash plate. A waist-shaped low pressure distribution window is provided on the swash plate support surface 41. 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 CC plane passing through the central axis of the swash plate. The low-pressure distribution window 43 and the high-pressure distribution window 44 are arranged relative to the central plane CC For a symmetrical structure, the flow distribution window can be configured as a single or multiple windows having a waist shape.

In particular, in order to make the swash plate have a certain pre-boosting and pre-decreasing effect, the low-pressure distribution window 43 and the high-pressure distribution window 44 can be rotated to a certain angle along the central axis of the swash plate; alternatively, the low-pressure distribution window can also be used. The end of the window 43 is provided with a throttle groove or hole that transitions 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 is provided a throttle groove or hole that transitions from the high-pressure distribution window 44 to the low-pressure distribution window 43. High pressure to low pressure or low pressure to high pressure play the role of pre-pressure reduction and pre-boost.

The supporting surface of the swash plate 40 opposite to the end seat 33 is configured to have a cylindrical supporting surface 45 shaped as a cylinder, and the end seat 33 has a sliding arc surface 33e with the same radius as the cylindrical supporting surface 45 of the swash plate, so that The cylindrical support surface 45 of the swash plate always maintains a close contact state when sliding on the sliding arc surface 33e of the end seat. 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 supporting surface 41 on the opposite side of the cylindrical surface of the swash plate are correspondingly communicated. The groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical support surface 45 are arranged in a symmetrical structure; the groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical support surface 45 have a seal The sealing band of the notch makes the cylindrical support surface 45 of the swash plate seal oil when sliding on the sliding arc surface 33e of the end seat.

The end seat 33 is provided with an oil inlet 33a and an oil outlet 33b of the axial piston motor. The oil outlet 33b is in communication with the groove-shaped low pressure port 46 on the cylindrical support surface 45. The oil inlet 33a Connected with the groove-shaped high-pressure port 47 on the cylindrical support surface 45, the number of the oil inlet 33a and the oil outlet 33b provided on the end seat 33 can be one or two. In particular, the end seat 33 has only One oil inlet 33a and one oil outlet 33b are provided, so that the motors on the left and right sides share one oil inlet and one oil outlet.

Example 2:

As shown in FIG. 15, the main difference from other embodiments is that a valve plate 90 is sandwiched between the sliding plate 50 and the swash plate 40 in the valve plate sub-assembly, and 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, the high pressure valve port 93 and the low pressure valve plate The ports 92 respectively communicate with the low pressure distribution window 43 and the high pressure distribution window 44 on the swash plate. The low-pressure distribution port and the high-pressure distribution port can be arranged in a symmetrical structure relative to the central plane; further, in order to make the distribution plate have a certain pre-boosting and pre-decreasing effect, the low-pressure distribution port and the high-pressure distribution port can be arranged along the distribution plate The central axis rotates at a certain angle; alternatively, the direction of transition from the low-pressure port to the high-pressure port and the direction of the transition from the high-pressure port to the low-pressure port can be set on the end of the high-pressure port. The throttling groove or hole plays the role of pre-pressure reduction and pre-boosting from high pressure to low pressure or low pressure to high pressure.

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 Figures 11-14, the main difference from other embodiments is that a third bearing 23 is sandwiched between the sliding plate 50 and the swash plate 40 in the flow distribution sliding plate sub-assembly, so that the sliding plate 50 follows its diameter. It is supported on the third bearing 23 in a constrained state, and the valve sliding plate pair of the third bearing 23 is arranged, and its structure is more favorable for stress.

As shown in Figures 11 and 12, there is shown an embodiment of a series variable axial piston motor supported in the sliding disk. In the preferred embodiment shown, two opposed flow distributions supported on the end seat 33 In the sliding plate assembly, a supporting shaft or supporting shaft pin 49 extending outward is provided in the middle of the swash plate 40, and a third bearing 23 is interposed between the swash plate supporting shaft or supporting shaft pin 49 and the inner side of the sliding plate 50, The sliding plate 50 is supported on the third bearing 23 in a state of being constrained in its radial direction. The third bearing 23 may be configured to include, but is not limited to, a radial thrust ball bearing, a needle roller bearing, and a cylindrical roller. One of bearings, tapered roller bearings, and radial ball bearings. When the spindle 10 and the cylinder 80 are rotating, the plunger 70 reciprocates in the plunger cavity of the cylinder 80 to realize the suction and discharge of the motor. Oil work.

As shown in Figures 13 and 14, there is shown an embodiment of a sliding disc externally supported series variable shaft axial piston motor. In the preferred embodiment shown, in the two opposed flow distribution sliding plate assemblies supported on the end seat 33, a third bearing 23 is interposed between the outer circumference of the sliding plate 50 and the inner side of the supporting block 41a, so The sliding plate 50 is supported by the third bearing 23 in a state of being restrained in its radial direction. When the main shaft 10 and the cylinder 80 are rotating, under the action of the supporting force of the swash plate 40 and the return force of the return mechanism, the plunger 70 reciprocates in the plunger cavity of the cylinder 80 to achieve The motor sucks and discharges oil.

During the operation of the axial piston motor, the plunger 70 in the high-pressure zone is acted on by the high-pressure oil pressure from the plunger hole 81 of the cylinder block, 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 the return force at the central axis, the inertial force (to cancel each other), and the frictional force (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.

Taking a sliding plate internally supported tandem variable shaft axial piston motor as an example, as shown in Figures 11 and 12, the restraining device includes a stop protruding inward on the side of the sliding plate 50 close to the hydrostatic support surface 51 The portion 57 and the engagement device 140 provided outside the swash plate support shaft or the support shaft pin 49. The stop portion 57 is used to stop the movement of the third bearing 23, and the engagement device 140 includes an engagement circumferential groove provided on the outer side of the swash plate support shaft or the support shaft pin 49 and an engagement circumferential groove A circlip (not shown) is provided, and the circlip restricts the sliding plate from moving away from the end surface of the swash plate 40 in a manner of restraining the third bearing 23 from moving outward along the supporting shaft 41. In particular, the restraining device 140 can also be configured as a combination of a stop portion and a pre-tightening nut (not shown), that is, a thread is provided on the outside of the supporting shaft or the supporting shaft pin 49, and the nut is tightened to restrain the third bearing and sliding The disk is away from the end face of the swash plate.

Taking the sliding plate externally supported tandem variable shaft axial piston motor as an example, as shown in Figures 13 and 14, the restraining device includes a stop protruding outward on the side of the sliding plate 50 close to the hydrostatic bearing surface 51 Portion 57 and an engagement device 140 provided on the supporting stop portion 41a. The stop portion 57 is used to restrict the movement of the third bearing 23, and the engagement device includes an engagement circumferential groove provided on the support stop portion 41a and adjacent to the third bearing 23 and in the engagement A retaining spring (not shown) is provided on the circumferential groove, and the retaining spring restricts the sliding plate from moving away from the end surface of the swash plate 40 in a manner of restricting the third bearing 23 to move 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 of the third bearing 23, and the engaging circumferential groove is provided adjacent to the third bearing 23 and the circlip that cooperates with the engaging circumferential groove is further restrained. 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 constraining device 140 is provided on the auxiliary to meet the requirements of the plunger's return stroke. There is no need to add additional pre-tensioning or return components such as a central spring, so that the constraining device greatly simplifies the structure and avoids fatigue damage to the central spring. Phenomena such as 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 4:

As shown in FIG. 14, the main difference from Embodiment 1 is that the variable mode of the dual axial piston motor adopts a separate variable. The double variable axial plunger motor is provided with two independent variable mechanisms, the variable mechanisms are respectively connected to the housing 32 on both sides of the end seat, the end of the swash plate is provided with a variable connecting portion 38, so The variable connection portions 38 of the swash plate on both sides are respectively connected to the variable mechanism. The variable mechanism respectively controls the respective swash plate movement to realize synchronous or asynchronous variable.

Example 5:

According to the different variable modes, the motors distributed on the left and right sides of the end seat 33 in the dual axial piston motor can have different combinations, including one of the following combinations: 1) The motors on the left and right sides of the end seat 33 are both It is a variable type axial piston motor, as shown in Figures 2 and 3, both ends of the end seat are provided with cylindrical sliding arc surfaces 33e and tightly abutted with the cylindrical support surface 45 of the variable swash plate; 2) the left and right sides of the end seat 33 The motors on the side are all quantitative axial piston motors. As shown in Fig. 16, the swash plates 40 on the left and right sides have a fixed inclination angle and are supported on a common end seat 33; 3) the left and right sides of the end seat 33 One of the motors is a quantitative axial piston motor, and the other is a variable axial piston motor. One end of the end seat is provided with a cylindrical sliding arc surface 33e and is in close contact with the cylindrical support surface 45 of the variable swash plate, and the other end is provided The plane supporting surface is connected with the swash plate 40 with a fixed angle.

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

1. At least one embodiment of the present disclosure connects two sliding plate type non-through shaft plunger motors in series, and the motor power is increased by two times, which can meet the requirements of large displacement, high pressure and high power, and solves the problem of non-through shaft plunger. Motors cannot be connected in series or difficult to connect in series.

2. In the dual axial plunger motor provided by at least one embodiment of the present disclosure, the swash plate is arranged oppositely, and the swash plate is supported on a common end seat, and the swash plate is provided with an oil suction and discharge channel and is connected with The connection between the inlet and outlet ports provided on the end seat can greatly simplify the structure, make the size smaller, the structure more compact, and the weight of the motor is smaller, thus increasing its power density per unit mass. At the same time, the dual axial piston motor As the optimized structure of the cylinder is closer to the bearing, the bending moment acting on the cantilever main shaft is reduced, which is more beneficial to the main shaft, the bearing life is longer, and the mechanical noise during operation is smaller.

3. At least one embodiment of the present disclosure integrates the functions of flow distribution, variable tilt, and hydrostatic support into the sliding plate pair. The main friction pairs are the sliding plate pair and the plunger pair. One is that one valve pair is reduced, thereby reducing The leakage of oil improves its efficiency; secondly, the lateral force of the plunger is greatly reduced, which eliminates or reduces the overturning phenomenon of the cylinder. Since there is no valve pair at the end of the cylinder, there are no problems such as wear and leakage at the end of the cylinder. Even if there is a side force that overturns the cylinder, it will not cause problems such as partial wear and failure. At the same time, this structure Makes the life of the cylinder longer, less maintenance later, and reduces the cost of use.

4. The variable mode of the dual axial plunger motor provided by at least one embodiment of the present disclosure can be set to a centralized and separate variable mode, which can be adapted to different working conditions and each has its own characteristics, of which the centralized variable mode , Two opposite swash plates can be connected to a common slide valve. When the slide valve moves, it can drive the two swash plates to move synchronously. This structure only has one variable mechanism, so the structure is simple and the variables are convenient , It is especially advantageous for the situation that requires the simultaneous movement of the two shaft ends of the dual axial piston motor.

5. At least one embodiment of the present disclosure integrates the functions of flow distribution, variable tilt, and hydrostatic support in the sliding plate pair. Since the sliding plate ball socket and the plunger ball head can be relatively tilted during the working process, they can be moved automatically It adapts to various situations due to the tilting of the swash plate and the tilting of the cylinder body, so that the sliding plate can always be close to the swash plate to complete the flow distribution, variable, support and other functions; at the same time, it is easier and more convenient to replace the sliding plate or the valve plate than replacing the cylinder. economic.

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 double-connected axial plunger motor, comprising two sliding plate type non-through shaft plunger motors and an end seat (33) sandwiched between the two sliding plate type non-through shaft plunger motors, each sliding plate The disc type non-through shaft plunger motor includes a main shaft (10), a swash plate (40), a sliding plate (50), a plunger (70) and a cylinder (80). The sliding plate (50) is an integral structure and supports The swash plate (40) constitutes a flow distribution sliding plate sub-assembly. The end surface of the sliding plate (50) and the swash plate (40) is provided with a static pressure support surface (51). The sliding plate (50) and the cylinder The opposite end surface of the body (80) is provided with a plurality of plunger ball sockets (58), and the sliding plate (50) is provided with an oil passage connecting the plunger ball sockets (58) and the hydrostatic bearing surface (51) Hole (53), one end of the plunger (70) is placed in the plunger ball socket (58), and the other end is inserted into the cylinder (80). The plunger center hole (72) inside the plunger (70) ) One end is connected to the oil through hole (53), and the other end is connected to the plunger hole (81) in the cylinder (80). The swash plate (40) is provided with a distribution oil groove (42), the two The swash plate (40) of the sliding plate type non-through shaft plunger motor is supported on a common end seat (33). The distribution oil groove (42) and the oil inlet and outlet ports (33a, 33a, 33a, 33b) Connected, high-pressure oil flows through the distribution oil groove (42), the oil through hole (53), the plunger center hole (72) and the plunger hole (81) on the swash plate (40) to drive the cylinder block (80) It rotates synchronously with the main shaft (10).
The dual axial piston 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 chambers (53a) ) Is distributed on the static pressure support surface (51) with the sliding disc axis (50C) as the center, and an oil passage is provided between the bottom of each oil chamber (53a) and the corresponding plunger ball socket (58) Hole (53), the oil through hole (53) serves as the main channel for sucking and discharging oil and introduces the oil between the static pressure bearing surface (51) and the swash plate (40), so that the static pressure bearing surface (51) ) A static pressure oil film support with clearance fit is formed with the end surface of the swash plate (40).
The dual axial piston motor according to claim 1, wherein a sealing portion for sealing oil is provided on the boss surface (52), and the sealing portion includes a diameter provided in the oil chamber (53a). An inner sealing part (55) and an outer sealing part (54) facing inward and outward, and an interval sealing part (56) provided between adjacent oil chambers (52).
The dual axial piston 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) is connected to the sliding plate (50) A low-pressure distribution window (43) and a high-pressure distribution window (44) are provided on the opposite end surfaces, and the high and low-pressure distribution windows (44, 43) are intermittently communicated with the oil chamber (53a), and the swash plate (40) The supporting surface opposite to the end seat (33) has a cylindrical supporting surface (45) shaped as a cylinder, and the cylindrical supporting surface (45) of the swash plate (40) has a groove-shaped cylindrical supporting surface (45). The groove-shaped low-pressure port (46) and the groove-shaped high-pressure port (47), the groove-shaped low-pressure port (46) and the groove-shaped high-pressure port (47) respectively communicate with the low-pressure distribution window (43) and the high-pressure distribution window (44) .
The dual axial piston motor according to claim 1, wherein the oil through hole (53) on the sliding plate (50) and the plunger center hole (72) on the plunger (70) are both Large diameter and used as the main oil hole structure for oil suction and discharge.
The dual axial plunger motor according to claim 1, wherein the axial plunger motor is arranged in a centralized variable structure, and the end seat (33) is provided with a spool valve (33c) Variable mechanism, the shaft pins (49) of two opposed swash plates (40) are connected to a common slide valve (33c). Under the action of the hydraulic pressure and spring force of the variable mechanism, the slide valve (33c) drives the two A swash plate (40) rotates synchronously to realize synchronous variable.
The dual axial piston motor according to claim 1, wherein the axial piston motor is configured as a separate variable structure, and two variable mechanisms are connected to the housing of the axial piston motor The variable mechanism is respectively connected with the corresponding swash plate (40), and the independent variable is realized under the action of the hydraulic pressure and spring force of the respective variable mechanism.
The dual axial piston motor according to claim 1, wherein the sliding plate non-through shaft piston motors distributed on both sides of the end seat (33) are combined in a variable swash plate, and the specific combination is two Side-slip disc type non-thru-shaft plunger motors are of variable type structure; or both sides-slip disc type non-thru-shaft plunger motors are all quantitative structure; or both sides are sliding disc type non-thru-shaft piston motors, one is quantitative type The structure, the other is a variable structure.
The dual axial piston motor according to claim 1, wherein one end of the main shaft (10) of the two sliding disc type non-through shaft piston motors extends out of the housing and is supported by the first bearing (21) The other end cantilever supports the cylinder (80) and rotates synchronously with the cylinder (80). The plunger hole (81) of the cylinder (80) is a structure with one end closed and one end open. The closed end of the cylinder (80) is not provided with a flow distribution pair. When the main shaft (10) and the cylinder (80) are rotating, the hydraulic axial force is transmitted through the cylinder (80) through the first bearing (21) To the shell.
The dual axial piston motor according to claim 9, wherein the first bearing (21) supporting the main shaft (10) includes at least one centripetal thrust bearing or thrust bearing, and the hydraulic axial force The cylinder end surface acting on the closed end of the plunger hole (81) is transmitted to the housing of the plunger pump or the motor through the first bearing (21).
The dual axial piston motor according to claim 1, wherein a third bearing (23) is interposed between the swash plate (40) and the sliding plate (50), and the sliding plate (50) ) Is supported on the third bearing (23) in a state of being restrained in its radial direction.
The dual axial piston motor according to claim 11, wherein the middle part of the swash plate (40) has a supporting shaft or a supporting shaft pin (49) extending outward, and the sliding plate (50) is provided with The third bearing (23) is sandwiched between the inner wall of the central through hole of the sliding plate (50) and the supporting shaft or the supporting shaft pin (49), and the sliding plate (50) is to receive radially The restrained state is supported on the third bearing (23).
The dual axial plunger motor according to claim 11, wherein the outer periphery of the swash plate (40) is provided with a raised support stop (41a), and the third bearing (23) is sandwiched between Between the outer side of the sliding plate (50) and the inner side of the supporting block (41a), the sliding plate (50) is supported on the third bearing (23) in a state of being restrained in its radial direction.
The dual axial plunger motor according to claim 1, wherein the plunger (70) comprises a connecting rod plunger with a tapered structure or a connecting rod plunger with a ball head at both ends or a belt A type of universal hinged spherical plunger. One end of the plunger (70) is inserted into the plunger hole (81) of the cylinder (80) in a reciprocating manner relative to the cylinder (80), and the other end is relatively sliding The disc (50) is fixed in the plunger ball socket (58) of the sliding disc (50) in a state where the end surface of the disc (50) is restricted away from and can be tilted. The plunger (70) is provided with a connecting plunger ball socket (58) and a post The central hole (72) of the large-diameter plunger of the plug hole (81).
The dual axial piston motor according to any one of claims 1 to 14, wherein a valve plate (90) is interposed between the sliding plate (50) and the swash plate (40), and the The sliding plate (50) is supported on the valve plate (90) and maintains a sliding fit with the valve plate (90). The valve plate (90) is provided with high and low pressure orifices (93, 92) through which high-pressure oil flows The valve oil groove (42) on the swash plate (40), the valve port of the valve plate, the oil chamber (53a) of the sliding plate (50), the oil through hole (53), the plunger center hole (72) and the cylinder plunger The hole (81) drives the cylinder (80) and the main shaft (10) to rotate synchronously.