CN209761644U - Sliding disc supporting type through shaft plunger pump or motor - Google Patents

Abstract

The utility model discloses a sliding disk supporting type through-shaft plunger pump or motor, which comprises a main shaft, a cylinder body and a flow distribution sliding disk pair, wherein the cylinder body is supported on the main shaft and synchronously rotates with the main shaft, the main shaft is supported on bearings at two ends in a mode of penetrating through a cylinder body and a flow distribution sliding disc pair, the flow distribution sliding disc pair comprises a swash plate and a sliding disc supported on the swash plate, the sliding disc is of an integral structure, a static pressure bearing surface is arranged on the end surface of the sliding disc opposite to the swash plate, a plurality of oil chambers are arranged on the static pressure bearing surface, a plurality of plunger ball sockets are arranged on the other end surface of the sliding disc, the sliding disc is provided with a large-aperture oil through hole for communicating the plunger ball socket and the oil chamber, the swash plate is provided with a flow distribution oil groove communicated with the oil inlet and the oil outlet, a third bearing is provided between the slide plate and the swash plate, and the slide plate is supported on the third bearing in a radially restrained state. The utility model provides performance such as high operational reliability, volume efficiency, working life of axial plunger pump or motor.

Description

Sliding disc supporting type through shaft plunger pump or motor

Technical Field

The utility model belongs to the technical field of hydraulic transmission and control, a swash plate axial plunger pump or motor is related to, in particular to sliding tray supporting formula leads to axle plunger pump or motor.

Background

The axial plunger pump and the motor are one of the most widely used hydraulic components in modern hydraulic transmission, and the hingeless inclined shaft pump and the slipper inclined disc type axial plunger pump are two types of axial plunger pumps which are most widely applied and are the most main at present. The swash pump and the slipper swash plate have characteristics respectively, and the two pumps or motors are in competition at present and are continuously improved and developed respectively. The swash plate type axial plunger pump has the characteristics of simple and compact structure, convenient variable, more variable forms, small inertia of the variable and the like, so the swash plate type axial plunger pump becomes the most important type of pump at present. According to the supporting form of the main shaft and the cylinder body, the swash plate type axial plunger pump is divided into a through shaft type and a non-through shaft type, the end part of the main shaft of the through shaft type axial plunger pump can be connected with an auxiliary oil replenishing pump or another main pump to form a serial axial plunger pump, and therefore the swash plate type axial plunger pump has obvious advantages in the aspects of improving the self-absorption capacity of oil and increasing the discharge capacity.

As shown in fig. 1, a typical structure of a conventional through-shaft axial plunger pump or motor includes a main shaft 10, a housing, a first bearing 21, a second bearing 22, a swash plate 40, a plunger 70, a slipper 120, a cylinder 80, a port plate 90, a return plate 130, and a center spring 100, wherein a main shaft axis 10C of the main shaft 10 coincides with a cylinder axis 80C of the cylinder 80, the center spring 100 presses the return plate 130 through a ball hinge 103, the slipper 120 is supported on the swash plate 40 and is in close fit with a working surface of the swash plate 40, the main shaft 10 sequentially penetrates through the swash plate 40, the return plate 60, the cylinder 80, and the port plate 90 and is supported by the first bearing 21 and the second bearing 22 at both ends, the cylinder 80 is connected with the main shaft 10 through a key and is supported on the main shaft 10, and when the axial plunger pump is used, a prime mover (not shown), such as an electric motor, an internal combustion engine, etc., rotates the main shaft 10, and the plunger 70 reciprocates in the cylinder plunger hole 81 under the supporting force of the swash plate 40 and the return force of the center spring 100, thereby performing oil suction and discharge operations of a pump or a motor.

This through-shaft axial plunger pump or motor has its following disadvantages: 1. the number of the key friction pairs is three, the number of the friction pairs is large, leakage of the axial plunger pump or the motor is increased, the volumetric efficiency of the axial plunger pump or the motor is reduced, and meanwhile, failure of any one friction pair causes failure of the whole axial plunger pump or the motor, so that the probability of working failure of the pump or the motor is increased due to the large number of the friction pairs; 2. under the action of hydraulic pressure, the swash plate generates larger lateral force to the plunger, the lateral force is transmitted to the cylinder body and the main shaft through the plunger to cause a wedge-shaped gap to be formed between the cylinder body and the port plate, so that the volume loss of the pump or the motor is increased, the sealing surface between the cylinder body and the port plate is locally contacted to cause surface burn between the cylinder body and the port plate, and the pump or the motor completely loses functions; 3. the through shaft type axial plunger pump or motor has more return mechanism parts, including a central spring 100, a thimble 102, a spherical hinge 103, a return disc 130 and other parts, and has a more complex structure and is easy to fail, particularly, the central spring is often broken due to fatigue damage, so that the sealing between a cylinder body and a valve plate is failed, and the phenomena of inclined and eccentric wear of a sliding shoe and the like are caused; 4. under the combined action of centrifugal moment, return force and friction moment generated along with the rotation of the cylinder body, the slipper is subjected to circumferential motion in the high-speed motion process, and the slipper can overturn relative to the surface of the swash plate, so that a wedge-shaped oil film is formed, the slipper is subjected to eccentric wear, and the normal work of the slipper is damaged.

Therefore, a profitable utility model that expects aims at solving the vice more, the yawing force is great, the return stroke mechanism is comparatively complicated, the boots wear partially scheduling problem of friction that current through-shaft type axial plunger pump or motor exist to improve the reliability, the volumetric efficiency of swash plate formula axial plunger pump or motor.

SUMMERY OF THE UTILITY MODEL

The invention of the utility model aims to: aiming at the problems existing in the prior through-shaft axial plunger pump or motor, a novel axial plunger pump or motor structure is provided, aiming at reducing the number of friction pairs, reducing the influence of cylinder body overturn caused by plunger lateral force and simplifying the structure of a return stroke mechanism, thereby improving the working reliability, the volume efficiency, the service life and other performances of the through-shaft axial plunger pump or motor.

The utility model discloses technical scheme implementation of technique: a sliding disk supported through-shaft plunger pump or motor, characterized in that: the hydraulic oil distribution device comprises a main shaft, a cylinder body and a flow distribution sliding disc pair, wherein the cylinder body and the flow distribution sliding disc pair are supported on the main shaft and synchronously rotate with the main shaft, the main shaft is supported on bearings at two ends in a mode of penetrating through the cylinder body and the flow distribution sliding disc pair, the flow distribution sliding disc pair comprises a tilting disc and a sliding disc supported on the tilting disc, the sliding disc is of an integral structure, a static pressure supporting surface is arranged on the end surface, opposite to the tilting disc, of the sliding disc, a plurality of plunger ball sockets are arranged on the other end surface of the sliding disc, oil through holes for communicating the plunger ball sockets with the static pressure supporting surface are arranged on the sliding disc, a flow distribution oil groove is arranged on the tilting disc and is communicated with an oil inlet and an oil outlet which are arranged on the end part, close to one side of the tilting disc, of a shell of a plunger pump or a motor, a.

Sliding tray supporting formula lead to axle plunger pump or motor, its sloping cam plate peripheral part is provided with bellied supporting fender portion, the third bearing clamp is established between the sliding tray outside and supporting fender portion inboard, the sliding tray is in order to follow its radial confined state supporting on the third bearing.

Sliding tray supporting formula lead to axle plunger pump or motor, it is in the vice one side of join in marriage a class sliding tray is provided with restraint device, restraint device contains and has the backstop portion that sets up to the outside and in one side that the sliding tray is close to the static pressure bearing surface the block device that sets up in the supporting backstop portion, block device is in order to retrain the mode that the third bearing outwards removed restricts the sliding tray and keeps away from the sloping cam plate terminal surface.

Sliding plate supporting formula lead to axle plunger pump or motor, it is in be provided with a plurality of grease chambeies on the static pressure bearing surface, be provided with waist shape low pressure distribution window and waist shape high pressure distribution window on the terminal surface with the sliding plate opposition on the sloping cam plate, high, low pressure distribution window with grease chamber intermittent type intercommunication, have on the sloping cam plate and take shape for columniform cylindrical bearing surface with the bearing surface of end cover opposition, the flute profile low pressure mouth and the flute profile high-pressure mouth that the configuration is the flute profile on the cylindrical bearing surface of sloping cam plate, flute profile low pressure mouth and flute profile high-pressure mouth respectively with low pressure distribution window and high pressure distribution window correspond the intercommunication.

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

Sliding plate supporting formula lead to axle plunger pump or motor, its supporting the first bearing of main shaft contains one centripetal thrust bearing or thrust bearing at least, the plunger hole of cylinder body seals and one end open-ended structure for one end, the during operation, hydraulic pressure axial force is used in the plunger hole and seals the cylinder body terminal surface of one end and warp on the casing of plunger pump or motor is transmitted to the first bearing.

Sliding plate supporting formula lead to axle plunger pump or motor, its main shaft end connection has auxiliary pump or main pump, forms the double pump structure of establishing ties.

Sliding plate supporting formula lead to axle plunger pump or motor, its the blind end of cylinder body is provided with the check valve, the check valve is used for the inside cavity of the plunger hole of intercommunication cylinder body and casing, just the check valve only allows hydraulic oil to get into the plunger hole from the cavity of casing.

Sliding plate supporting formula lead to axle plunger pump or motor, its the plunger contains the connecting rod plunger of taking the toper structure or the spherical plunger's of all being provided with the bulb at both ends connecting rod plunger or taking universal hinge one kind, but the reciprocal gliding mode of plunger one end cylinder body is pulled in relatively the plunger hole of cylinder body, the other end is kept away from the limited state that just can incline with relative sliding plate terminal surface and is fixed on the plunger ball socket of sliding plate, be provided with the large aperture plunger centre bore in intercommunication plunger ball socket and plunger hole on the plunger.

sliding plate supporting formula through-shaft plunger pump or motor, its press from both sides between sliding plate and the sloping cam plate and be equipped with the valve plate, the sliding plate supporting just keeps sliding fit with the valve plate on the valve plate, be provided with high, low pressure valve port on the valve plate, hydraulic oil flows through valve port, the through oil hole on the sliding plate, plunger centre bore on valve port oil groove on the valve plate, the valve plate on the valve plate under the reciprocal effect of plunger, realizes sucking, the discharge of hydraulic oil.

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

1. The utility model discloses to join in marriage class, variable slope, static pressure supporting function integration in joining in marriage class sliding tray is vice, and main friction is vice for joining in marriage class sliding tray is vice and the plunger is vice, compares current slipper formula sloping cam plate axial plunger pump or motor, has following advantage: firstly, as the end part of the cylinder body is not provided with the valve plate, one valve pair is reduced, thereby reducing the leakage of oil and improving the volume efficiency; secondly, the end part of the cylinder body does not need to be abutted against the valve plate, so that the end part of the cylinder body does not need to be precisely machined, the manufacturing difficulty is greatly reduced, meanwhile, the service life of the cylinder body is longer, the later maintenance is less, and the use cost is reduced; thirdly, as the sliding disc is supported on the tilting disc by a bearing, and the plunger adopts a connecting rod plunger with a hingeless conical structure or a connecting rod plunger with a ball head arranged at both ends or a spherical plunger with a universal hinge, the lateral force of the plunger is greatly reduced, and the overturning phenomenon of the cylinder body is eliminated or reduced; fourthly, because the end part of the cylinder body is not provided with the port plate, even if partial lateral force exists, the problems of failure and the like caused by eccentric wear can not be generated.

2. The utility model discloses a sliding tray supporting formula leads to axle plunger pump or motor, its return stroke mechanism sets up the restraint device on the valve plate is vice, and this restraint device compares with current logical shaft type axial plunger pump or motor, and its structure is very simplified, does not need additionally to set up spare parts such as central spring, thimble, ball hinge, return stroke dish, does not have central spring because of fatigue damage fracture and lead to phenomena such as the sealed inefficacy between cylinder body and the valve plate and the inclined partial mill of sliding shoe.

3. The utility model discloses a sliding tray supporting formula leads to axle plunger pump or motor, its restraint device is compared with fixed clearance forced return mechanism, the utility model discloses a restraint device is static contact such as jump ring and third bearing, does not have wearing and tearing scheduling problem. The existing fixed-gap forced return mechanism uses a screw to fix a pressure plate on a swash plate, the pressure plate is in dynamic contact with the return plate, namely, the pressure plate and the return plate are always in friction loss, mechanical noise is caused, and a constant gap cannot be kept for a long time, so that the pump fails early. Meanwhile, the clamp spring is simple to mount and guaranteed in precision according to mounting requirements, the existing fixed-gap forced return requires processing and mounting precision, the gap cannot meet the requirements if the gap is too large or too small, and the gap is dynamically changed.

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

5. The utility model provides a sliding tray structure is overall structure, has replaced a plurality of independent piston shoes among the prior art and has utilized the structure of return stroke dish return stroke, the utility model provides a plunger is connected more reliably with sliding tray, sliding tray and pressure disk, has avoided piston shoe neck and shoulder wearing and tearing among the prior art, has sheared destruction and return stroke dish drilling position to take place phenomenons such as fracture to the operational reliability of swash plate type plunger pump or motor has been improved. Meanwhile, the centrifugal force and the friction force of each part of the sliding plate are mutually offset, the overturning of a single sliding shoe under the comprehensive action of the centrifugal moment caused by circumferential motion and the friction moment generated along with the rotation of the cylinder body in the high-speed motion process is avoided, the integral sliding plate structure is uniform in abrasion, and the eccentric wear phenomenon of the original sliding shoe pair is eliminated or reduced.

Drawings

Fig. 1 is a schematic structural diagram of a through-shaft type axial plunger pump or motor in the prior art.

Fig. 2 shows an embodiment of the present invention, which is a sliding-disk-supported through-shaft plunger pump or motor.

3 fig. 33 3 is 3a 3 cross 3- 3 sectional 3 view 3 taken 3 along 3 the 3 line 3a 3- 3a 3 of 3 the 3 sliding 3- 3 disk 3- 3 supported 3 through 3- 3 shaft 3 plunger 3 pump 3 or 3 motor 3 of 3 fig. 32 3 according 3 to 3 the 3 present 3 invention 3. 3

Fig. 4 is a plan view of one end of the middle slide plate of the present invention.

Fig. 5 is a cross-sectional view of the sliding plate structure B-B in fig. 4 according to the present invention.

Fig. 6 is a plan view of the other end of the middle sliding plate of the present invention.

Fig. 7 is a plan view of an end of the swash plate opposite the slide plate according to the present invention.

Fig. 8 is a plan view of an end of the swash plate opposite the end cap according to the present invention.

Fig. 9 is a cross-sectional view taken along line D-D of fig. 8 according to the present invention.

Fig. 10 shows an embodiment of a sliding-disk-supported through-shaft plunger pump or motor with thrust bearings according to the present invention.

fig. 11 shows another embodiment of the present invention, a sliding plate supported through-shaft plunger pump or motor.

FIG. 12 is a plan view of the middle port plate of the present invention

Fig. 13 shows an embodiment of a sliding-disk-supported through-shaft plunger pump or motor of the present invention in which a check valve is provided.

The labels in the figure are: 10 is a main shaft, 10C is a main shaft axis, 11 is a first bearing support part, 12 is a second bearing support part, 13 is a main shaft shoulder, 21 is a first bearing, 21a is a radial ball bearing, 21b is a radial thrust bearing or a thrust bearing, 22 is a second bearing, 23 is a third bearing, 31 is a front shell, 32 is a shell body, 33 is an end cover, 33a is an oil inlet, 33b is an oil outlet, 33d is a flow passage, 33e is a slip arc surface, 34 is a first cavity, 35 is a second cavity, 38 is a variable connecting part, 39 is an auxiliary pump, 40 is a swash plate, 41 is a swash plate support surface, 41a is a support baffle, 42 is a flow distribution oil groove, 43 is a low-pressure flow distribution window, 44 is a high-pressure flow distribution window, 45 is a cylindrical support surface, 46 is a groove-shaped low-pressure port, 47 is a groove-shaped high-pressure port, 48 is a communication groove opening, 50 is a sliding plate, 50C is a sliding plate axis, 51 is a static pressure support surface, 53 is an oil through hole, 53a is an oil chamber, 54 is an outer sealing part, 55 is an inner sealing part, 56 is a spacing sealing part, 57 is a stop part, 58 is a plunger ball socket, 59 is a sliding disc bearing support part, 60 is a pressure plate, 70 is a plunger, 71 is a plunger ball head, 72 is a plunger central hole, 73 is a tapered rod part, 74 is a plunger part, 80 is a cylinder body, 81 is a plunger hole, 82 is a main shaft assembly hole, 80C is a cylinder body central axis, 90 is a distributing disc, 91 a distributing bearing surface, 92 is a low-pressure distributing port, 93 is a high-pressure distributing port, 100 is a central spring, 101 is a stop, 102 is an ejector pin, 103 is a ball hinge, 110 is a check valve, 111 is a valve body, 112 is a valve core, 113 is a spring, 114 is a retainer ring, 120 is a sliding shoe, 130 is a return disc, 140 is an engaging device, and 141 is a cylinder body snap.

Detailed Description

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

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

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

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

Example 1:

As shown in fig. 2-9, in the embodiment of the sliding-disk-supported through-shaft plunger pump of the present invention, in the illustrated preferred embodiment, the sliding-disk-supported through-shaft plunger pump includes a main shaft 10, a housing, a first bearing 21, a second bearing 22, a flow-distribution sliding-disk pair, a plunger 70 and a cylinder 80, the main shaft axis 10C of the main shaft 10 coincides with the cylinder center axis 80C of the cylinder 80, one end of the main shaft 10 extends out of the housing and is supported on the first bearing 21, the other end of the main shaft passes through the flow-distribution sliding-disk pair to an end seat and is supported on the second bearing 22, the main shaft 10 and the cylinder 80 are connected through a key to realize synchronous rotation, the cylinder 80 is supported in the middle area of the main shaft 10, and the main shaft 10 sequentially penetrates through the cylinder 80, the pressure plate 60, the sliding disk 50 and the swash plate 40 from the end; the flow distribution sliding disc pair comprises a swash plate 40 and a sliding disc 50 supported on the swash plate 40, wherein the sliding disc 50 is of an integral structure, the sliding disc 50 is provided with a static pressure bearing surface 51, the static pressure bearing surface 51 is supported on the swash plate 40 and is tightly matched with the working surface of the swash plate 40, one end of the sliding disc 50 is provided with a plurality of kidney-shaped oil chambers 53a, the other end surface of the sliding disc 50 is provided with a plurality of plunger ball sockets 58, the sliding disc 50 is provided with large-aperture oil through holes 53 for communicating the plunger ball sockets 58 with the oil chambers 53a, the swash plate 40 is provided with a flow distribution oil groove 42 communicated with the oil inlet 33a and the oil outlet 33b, and when the sliding disc works, hydraulic oil flows through the flow distribution oil groove 42, the oil chambers 53a, the large-aperture oil through holes 53, the large-aperture plunger central holes 72 and the cylinder plunger holes 81 on the swash plate 40 under the reciprocating action; a third bearing 23 is provided between the slide plate 50 and the swash plate 40, and the slide plate 50 is supported in a radially restrained state on the third bearing 23.

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

In this embodiment, the housing may be configured as a two-body structure or a three-body structure, when the housing is configured as a two-body structure, the housing includes a hollow housing body 32 and an end cover 33 connected to the housing body, the housing body 32 has a first cavity 34 for accommodating the first bearing 21 and a second cavity 35 for accommodating the cylinder block and for accommodating the flow distribution sliding plate pair, the end cover 33 is used for closing one end opening of the housing body 32, the end cover 33 is provided with an oil inlet 33a and an oil outlet 33b of the pump, a flow passage 33d communicating with the swash plate flow distribution oil groove 42, and a sliding arc surface 33e for supporting the swash plate; when the axial plunger pump is a variable displacement pump, a variable displacement mechanism for variable displacement swing is arranged on the shell body 32, the variable displacement mechanism is connected with a variable displacement connecting part 38 arranged on a swash plate, and under the action of the variable displacement mechanism, the swash plate 40 and the sliding plate 50 rotate in the second cavity 35; when the housing is provided as a three-piece structure, the front housing may be provided as a structure composed of a front housing or front housing 31 and a housing body 32, the front housing or front housing 31 being provided with a first cavity 34 for accommodating the first bearing 21, the housing body 32 being provided with a second cavity 35 for accommodating the cylinder and the sliding disk pair.

The main shaft 10 penetrates through the housing 32 to the end cover 33 in a cylindrical shape, a first bearing support part 11 and a second bearing support part 12 are arranged on the main shaft, a first bearing 21 is arranged between the first bearing support part 11 and the housing 32, a second bearing 22 is arranged between the second bearing support part 12 and the end cover 33, one end of the main shaft 10 extends out of the housing 32 and is used for an external prime mover (or load) and supported on the housing 32 through the first bearing 21, the other end of the main shaft penetrates through the end cover 33 and is supported on the end cover 33 through the second bearing 22, the main shaft 10 can freely rotate around the axis of the main shaft 10 relative to the housing 32 through the first bearing 21 and the second bearing 22, a key connection structure used for connecting a cylinder body 80 is arranged on the circumferential surface of the middle area of the main shaft 10, and the main shaft 10 drives the cylinder body.

The first bearing 21 includes at least one radial thrust bearing, including but not limited to a radial thrust ball bearing or a tapered roller bearing, and a main shaft shoulder 13 is provided on the main shaft 10 near the end of the cylinder 80. When the pump works, the main shaft 10 drives the cylinder 80 to rotate synchronously, and under the action of axial hydraulic pressure, the end part of the cylinder abuts against the main shaft retaining shoulder 13 and is transmitted to the first bearing 21 through the main shaft retaining shoulder 13 and further transmitted to the shell body 32. It should be noted that the transmission of the axial load by the cylinder 80 through the spindle shoulder 13 is not a condition limiting the application thereof, but instead, for example, as shown in fig. 10, the first bearing 21 is provided with a support system comprising a thrust bearing 21b, the cylinder 80 directly abuts on the radial thrust bearing 21b and transmits the hydraulic axial force to the casing 32, the radial force being taken by the radial bearing 21a and the second bearing 22 supported at both ends of the spindle.

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

It should be noted that the end of the cylinder 80 is not provided with a port plate abutting against it, thus reducing a friction pair and improving its volumetric efficiency; because the end part of the cylinder body 80 is not abutted against the valve plate, the end part of the cylinder body does not need to be precisely machined, and the manufacturing and using cost is reduced; the end of the cylinder body 80 has no port plate, and even if partial lateral force exists, the problems of failure and the like caused by eccentric wear can be avoided.

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

A plurality of plunger ball sockets 58 are provided at positions facing the plunger 70 on the end surface of the slide plate 50 facing the cylinder, the plunger ball sockets 58 form recesses having substantially hemispherical openings on the end surface of the slide plate 50, the plunger ball sockets 58 support the plunger balls 71 in a state where the plunger balls 71 are uniformly distributed at intervals on the common circumference of the slide plate axis 50C, and after the plunger 70 is attached to the plunger ball sockets 58, the plunger balls are fixed to the end surface of the slide plate 50 by a pressing plate 60, so that the movement of the plunger 70 away from the end surface of the slide plate 50 is restricted. In particular, the means for fastening the plunger 70 to the front face of the slide plate 50 are also not limited to the use of a pressure plate, but, for example, a form-locking holding device (not shown) can also be provided on the slide plate 50, which can fasten the plunger ball 71 by a covering of more than 180 degrees.

As shown in fig. 4, 5 and 6, a static pressure bearing surface 51 is provided on an end surface of the slide plate 50 facing the swash plate 40, the slide plate axis 50C forms a certain angle with the main shaft axis 10C, the static pressure bearing surface 51 is supported on the swash plate 40 and always slidably engages with the swash plate 40, a plurality of oil chambers 53a shaped like a kidney are provided on the static pressure bearing surface 51, preferably, the oil chambers 53a are uniformly distributed on the static pressure bearing surface 51 centering on the slide plate axis 50C, and a large-diameter oil passage hole 53 communicating the plunger ball socket 58 and the oil chamber 53a is provided on the slide plate 50.

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

The land 52 and the bearing surface of the swash plate 40 form effective static pressure oil film bearing, the land 52 is provided with a sealing part for sealing oil, the sealing part is arranged on the inner periphery of the oil chamber 53a in a state of surrounding the oil chamber 53a, and the sealing part comprises an inner sealing part 55 distributed inside and outside the oil chamber 53a in the radial direction, an outer sealing part 54 and a spacing sealing part 56 distributed between the adjacent oil chambers 53 a. The inner seal 55 is a region defined by the inner edge of the oil chamber 53a and the inner diameter R1 of the boss surface 52, the outer seal 54 is a region defined by the outer edge of the oil chamber 53a and the outer diameter R2 of the boss surface 52, and the partition seal 56 is a partition boss surface region between adjacent oil chambers 53 a. A certain reasonable clearance is always kept between the sealing part of the boss surface 52 and the bearing surface of the swash plate 40, so that oil film leakage is at a reasonable level.

As shown in fig. 7, the swash plate 40 has a swash plate bearing surface 41 matching with the static pressure bearing surface of the swash plate, a kidney-shaped low-pressure distribution window 43 and a kidney-shaped high-pressure distribution window 44 are provided on the swash plate bearing surface 41, 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 center axis of the swash plate, the low-pressure distribution window 43 and the high-pressure distribution window 44 may be provided in a symmetrical or asymmetrical structure with respect to the center plane CC, for example, the high-pressure distribution window 44 is provided in a plurality of windows having kidney shapes; in order to enable the swash plate to have certain pre-boosting and pre-reducing functions, the low-pressure flow distribution window 43 and the high-pressure flow distribution window can rotate for a certain angle along the central shaft of the swash plate; in particular, a throttling groove or a hole (not shown) which is arranged on the end of the low-pressure distribution window 43 and transits from the low-pressure distribution window 43 to the high-pressure distribution window 44 and is arranged on the end of the high-pressure distribution window 44 and transits from the high-pressure distribution window 44 to the low-pressure distribution window 43 can be arranged to play the roles of pre-reducing the pressure and pre-increasing the pressure from high pressure to low pressure or from low pressure to high pressure.

As shown in fig. 8, the bearing surface of the swash plate 40 facing the end cover 33 is provided with a cylindrical bearing surface 45 formed in a cylindrical shape, and the end cover 33 has a smooth arc surface 33e having the same radius as the cylindrical bearing surface 45, so that the cylindrical bearing surface 45 is always kept in a close contact state when sliding on the smooth arc surface 33e of the end cover. The cylindrical bearing surface 45 of the swash plate is provided with a groove-shaped low-pressure port 46 and a groove-shaped high-pressure port 47, and the groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical bearing surface 45 are respectively communicated with the low-pressure flow distribution window 43 and the high-pressure flow distribution window 44 on the swash plate bearing surface 41 on the opposite side of the cylindrical bearing surface of the swash plate. The slotted low-pressure port 46 and the slotted high-pressure port 47 on the cylindrical support surface 45 are of symmetrical or asymmetrical configuration, for example, the slotted low-pressure port 46 and the slotted high-pressure port 47 are of equal or unequal configuration in opening width and/or length. Generally, when the motor is used, the opening widths and the opening lengths of the groove-shaped low-pressure opening 46 and the groove-shaped high-pressure opening 47 on the cylindrical supporting surface 45 are in the same symmetrical configuration; the slotted low pressure port 46 and the slotted high pressure port 47 on the cylindrical bearing surface 45 may be asymmetrically configured for use as a pump. The peripheries of the groove-shaped low-pressure port 46 and the groove-shaped high-pressure port 47 on the cylindrical bearing surface 45 are provided with sealing belts for sealing the notches, so that the cylindrical bearing surface 45 seals oil when sliding on the sliding arc surface 33e of the end cover. Specifically, a communication groove opening 48 communicating the groove-shaped low-pressure port 46 with the housing second cavity 35 is provided on the cylindrical bearing surface 45 of the swash plate, as shown in fig. 8, so that the oil inlet communicates with the housing second cavity 35.

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

A support stopper 41a is provided on the outer periphery of the swash plate 40, a third bearing 23 is interposed between the outer side of the swash plate and the inner side of the support stopper 41a, and the swash plate 50 is supported by the third bearing 23 in a radially restrained state. The third bearing 23 may be configured to include but not limited to one of a radial ball bearing, a needle bearing, a cylindrical roller bearing, a tapered roller bearing, and a radial ball bearing, and when the main shaft 10 and the cylinder 80 rotate, the plunger 70 reciprocates in a plunger cavity of the cylinder 80, so as to perform oil suction and discharge operations of a pump or a motor.

During the operation of the axial plunger pump, the high-pressure plunger 70 is acted by the high-pressure oil hydraulic force of the cylinder plunger hole 81, and the plunger ball 71 exerts a nearly horizontal hydraulic force on the sliding plate 50, and the hydraulic force pushes the sliding plate 50 to the swash plate 40 and is tightly contacted with the end face of the swash plate 40. Since the end surface of the swash plate 40 applies a reaction force to the swash plate 50, and the end surface of the swash plate 50 is in contact with the end surface of the swash plate 40 in the form of an inclined surface, the reaction force of the swash plate 40 can be decomposed into a horizontal component force in the direction of the spindle axis 10C and a lateral component force in the direction perpendicular to the spindle axis 10C, which has a tendency to move the swash plate laterally. After the third bearing 23 is interposed between the swash plate 40 and the slide plate 50, the slide plate receives the reaction force of the third bearing 23, and the reaction force acting on the slide plate can be decomposed into a horizontal component force in the direction of the main shaft axis 10C and a lateral component force in the direction perpendicular to the main shaft axis 10C. In addition to this, the slide plate is subjected to a return restraining force, an inertial force (which counteracts each other), a frictional force (not shown), etc., which constitute a balance of the forces of the slide plate. The horizontal component of each force in the axial direction of the main shaft is balanced with the hydraulic force acting on the slide plate 50 by the plunger 70. The lateral force component acting on the slide plate 50 in the direction perpendicular to the main shaft axis 10C can be canceled in the slide plate 50 without being further transmitted to the cylinder 80 via the plunger 70.

The structure adopting the bearing to support the sliding disc has the following characteristics: the third bearing 23 restrains the radial movement or movement tendency of the sliding disk 50, and balances the lateral component of the acting force of the sliding disk 50, so that the lateral force of the sliding disk 50 acting on the cylinder 80 via the plunger 70 is eliminated or greatly reduced, and the working reliability, the working pressure and the working life of the axial plunger pump or motor are improved.

At the same time, it is particularly evident that the return stroke of the axial piston pump or motor, which comprises a restraint device arranged on the secondary side of the distributor slide, limits the distance of the slide 50 from the end face of the swash plate 40 under the action of the return force, is greatly simplified.

further, the restraining means includes a stopper 57 protruding outward on the side of the slide plate 50 close to the static pressure bearing surface 51, and an engaging means 140 provided on the bearing stopper 41a, the stopper 57 being used to limit the movement of the third bearing 23, the engaging means includes an engaging peripheral groove provided on the bearing stopper 41a adjacent to the third bearing 23, and a snap spring (not shown) provided on the engaging peripheral groove, the snap spring limiting the outward movement of the third bearing 23 away from the end surface of the swash plate 40.

It is contemplated that an elastic washer (not shown) may be disposed between the stop 57 and the third bearing 23 or between the circlip and the third bearing 23, so that the restraining assembly has an initial preload to maintain the preload state of the swash plate and the swash plate, in addition to limiting the movement of the swash plate away from the end of the swash plate.

Similarly, the constraint mode of the constraint device 140 can also be realized by interference fit of the third bearing 23 and the swash plate support stop portion 41a, and the circumferential engaging groove and the snap spring engaged with the circumferential engaging groove are arranged on the swash plate support stop portion 41a and adjacent to the third bearing 23 to perform further constraint action.

It should be noted that, because the end of the cylinder 80 is not provided with the port plate, there is no friction pair supported by the static pressure oil film, and it is not necessary to apply pre-tightening force to the end of the cylinder 80 to achieve the sealing purpose, so that only the restriction device 140 is needed to be arranged on the port plate pair, which can meet the return requirement of the plunger, and there is no need to additionally arrange pre-tightening or return components such as the central spring, so that the restriction device has a greatly simplified structure compared with the existing swash plate type axial plunger pump or motor, and the phenomenon of the central spring being broken due to fatigue damage is avoided. Of course, in order to prevent the axial plunger pump from moving along the main shaft 10 toward the sliding plate when the axial plunger pump is not horizontally placed (e.g., stored, transported, turned upside down during use, etc.), a cylinder clamp spring 141 is disposed on the main shaft 10 adjacent to the end surface of the cylinder to restrain the movement of the cylinder 80.

Example 2:

As shown in fig. 11 and 12, the main difference from embodiment 1 is that a port plate 90 is interposed between a slide plate 50 and a swash plate 40 in the port plate pair, the static pressure bearing surface 51 is supported on the port plate 90 and is in sliding engagement with the port plate 90, the port plate is fixed to the swash plate by means of pins or the like, and the port plate 90 is provided with a high-pressure port 93 and a low-pressure port 92, as shown in fig. 11, the high-pressure port 93 and the low-pressure port 92 are respectively communicated with a low-pressure port 43 and a high-pressure port 44 on the swash plate. The low pressure distribution ports 92 and the high pressure distribution ports 93 may be arranged in a symmetrical or asymmetrical configuration with respect to the center plane, for example, the high pressure distribution ports 93 may be arranged as a plurality of windows (not shown) having a kidney shape; in order to enable the valve plate to have certain pre-boosting and pre-reducing functions, the low-pressure valve port 92 and the high-pressure valve port 93 can rotate for a certain angle along the central axis of the valve plate; specifically, a throttling groove or a hole which is arranged on the end part of the low-pressure distribution port 92 and transits from the low-pressure distribution port 92 to the high-pressure distribution port 93 and is arranged on the end part of the high-pressure distribution port 93 and transits from the high-pressure distribution port 93 to the low-pressure distribution port 92 can be arranged, so that the functions of pre-reducing pressure and pre-increasing pressure from high pressure to low pressure or from low pressure to high pressure can be achieved.

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

Example 3:

As shown in fig. 11, the main difference from the other embodiments is that the axial plunger pump is an axial plunger pump with an auxiliary pump, in the illustrated embodiment, an auxiliary pump 39 is connected to the end of the main shaft 10, and the auxiliary pump 39 is used for supplying oil to the hydraulic system or providing hydraulic operating force; the auxiliary pump 39 is connected with the end cover 33 through bolts, and the external auxiliary pump 39 can be a gear pump or a vane pump. It is contemplated that the main shaft may be disposed to extend out of the housing and be connected to another main pump to form a tandem dual pump configuration.

Example 4:

As shown in fig. 13, the main difference from the other embodiments is that one end of the cylinder 80 abutting against the main shaft shoulder 13 is provided with a check valve 110 only allowing oil to enter the plunger hole 81 from the housing cavity, the check valve 110 is fixedly connected with the cylinder 80, the check valve 110 comprises a valve body 111 fixedly connected with the cylinder, a valve core 112 arranged inside the valve body, a retaining ring 114 fixed on the valve body 111, and a spring 113 arranged between the valve core 112 and the retaining ring 114, the check valve 110 only allows low-pressure oil to flow into the plunger hole 81 from the housing second cavity 35, that is, when the cylinder 80 is in an oil suction state, the valve core 112 of the check valve 110 is opened, low-pressure oil enters the plunger hole 81 from the housing second cavity 35, and when the cylinder 80 is in an oil discharge state, the valve core 112 of the check valve 110 is closed.

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

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

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

Claims (10)

1. A sliding disk supported through-shaft plunger pump or motor, characterized in that: the hydraulic oil distribution device comprises a main shaft (10), a cylinder body (80) and a flow distribution sliding disc pair, wherein the cylinder body (80) and the flow distribution sliding disc pair are supported on the main shaft (10) and synchronously rotate with the main shaft, the main shaft (10) is supported on bearings at two ends in a mode of penetrating through the cylinder body (80) and the flow distribution sliding disc pair, the flow distribution sliding disc pair comprises a swash plate (40) and a sliding disc (50) supported on the swash plate (40), the sliding disc (50) is of an integral structure, a static pressure bearing surface (51) is arranged on the end surface, opposite to the swash plate (40), of the sliding disc (50), a plurality of plunger ball sockets (58) are arranged on the other end surface of the sliding disc (50), oil through holes (53) for communicating the plunger ball sockets (58) with the static pressure bearing surface (51) are arranged on the sliding disc (50), a flow distribution oil groove (42) is arranged on the swash plate (40), and the flow distribution oil groove (42) and the, The oil outlets (33 a, 33 b) are communicated, a third bearing (23) is provided between the slide plate (50) and the swash plate (40), and the slide plate (50) is supported on the third bearing (23) in a radially restrained state thereof.

2. A sliding-disc-supported through-shaft plunger pump or motor according to claim 1, wherein: the outer periphery of the swash plate (40) is provided with a convex supporting stop part (41 a), the third bearing (23) is arranged between the outer side of the sliding plate (50) and the inner side of the supporting stop part (41 a), and the sliding plate (50) is supported on the third bearing (23) in a radial constrained state.

3. A sliding-disc-supported through-shaft plunger pump or motor according to claim 2, wherein: and a restraining device is arranged on one side of the flow distribution sliding disc pair, the restraining device comprises a stopping part (57) which protrudes outwards and is arranged on one side, close to the static pressure bearing surface (51), of the sliding disc (50) and an engaging device (140) arranged on the bearing stopping part (41 a), and the engaging device (140) limits the sliding disc (50) from being far away from the end surface of the swash plate (40) in a mode of restraining the third bearing (23) from moving outwards.

4. A sliding-disc-supported through-shaft plunger pump or motor according to claim 1, wherein: the static pressure bearing surface (51) is provided with a plurality of oil chambers (53 a), the end surface of the swash plate (40) opposite to the slide plate (50) is provided with a waist-shaped low-pressure flow distribution window (43) and a waist-shaped high-pressure flow distribution window (44), the high-pressure flow distribution windows (44) and the low-pressure flow distribution windows (43) are intermittently communicated with the oil chambers (53 a), the bearing surface of the swash plate (40) opposite to the end cover (33) is provided with a cylindrical bearing surface (45) which is formed into a cylindrical shape, the cylindrical bearing surface (45) of the swash plate (40) is provided with a groove-shaped low-pressure port (46) and a groove-shaped high-pressure port (47) which are formed into a groove shape, and the groove-shaped low-pressure port (46) and the groove-shaped high-pressure port (47) are respectively and correspondingly communicated with the low-pressure.

5. A slide-plate-supported through-shaft plunger pump or motor according to claim 4, wherein: the cylindrical bearing surface (45) of the swash plate (40) is provided with a communication notch (48) for communicating the groove-shaped low-pressure port (46) with the second cavity (35) of the shell.

6. A sliding-disc-supported through-shaft plunger pump or motor according to claim 1, wherein: the first bearing (21) supporting the main shaft (10) at least comprises a centripetal thrust bearing or a thrust bearing, the plunger hole (81) of the cylinder body (80) is of a structure with one closed end and one open end, and when the hydraulic axial force hydraulic pump or the hydraulic axial force hydraulic pump works, the hydraulic axial force acts on the end face of the cylinder body with the closed end of the plunger hole (81) and is transmitted to a shell of a plunger pump or a motor through the first bearing (21).

7. A sliding-disc-supported through-shaft plunger pump or motor according to claim 1, wherein: the end part of the main shaft (10) is connected with an auxiliary pump (39) or a main pump to form a series double-pump structure.

8. A sliding-disc-supported through-shaft plunger pump or motor according to claim 1, wherein: one end of the cylinder body (80) is provided with a one-way valve (110), the one-way valve (110) is used for communicating a plunger hole (81) of the cylinder body (80) with an inner cavity of the shell, and the one-way valve (110) only allows hydraulic oil to enter the plunger hole (81) from the cavity of the shell.

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

10. A slide plate supported through-shaft plunger pump or motor according to any one of claims 1 to 9, wherein: a flow distribution disc (90) is clamped between the sliding disc (50) and the swash plate (40), the sliding disc (50) is supported on the flow distribution disc (90) and keeps sliding fit with the flow distribution disc (90), high-pressure and low-pressure flow distribution ports (93 and 92) are formed in the flow distribution disc (90), and hydraulic oil flows through a flow distribution oil groove (42) in the swash plate (40), the flow distribution ports in the flow distribution disc, oil through holes (53) in the sliding disc and a plunger center hole (72) under the reciprocating action of a plunger, so that the suction and the discharge of the hydraulic oil are realized.