CN209838612U

CN209838612U - Tandem type axial plunger pump

Info

Publication number: CN209838612U
Application number: CN201920316198.2U
Authority: CN
Inventors: 钟彪
Original assignee: Individual
Current assignee: Shanghai Qiangtian Drive Technology Co ltd
Priority date: 2019-03-13
Filing date: 2019-03-13
Publication date: 2019-12-24
Anticipated expiration: 2029-03-13

Abstract

The utility model discloses a serial-type axial plunger pump, lead to axle plunger pump and press from both sides the end socket of establishing between two sliding plate formula lead to axle plunger pumps including two sliding plate formulas, sliding plate formula lead to axle plunger pump contains the sliding plate sub-assembly that flows of joining in marriage, the sliding plate sub-assembly that flows of joining in marriage contains the sloping cam plate and supports the sliding plate on the sloping cam plate, the sliding plate is overall structure, be provided with a plurality of plunger ball sockets, a plurality of grease chambers and the intercommunication of distribution on the opposite side terminal surface of distributing on the sliding plate plunger ball socket and grease chamber on the opposite side terminal surface the large aperture of plunger ball socket and grease chamber leads to the oilhole, be provided with on the sloping cam plate with the communicating oil groove that flows in and out of hydraulic fluid port, two sloping cam plates are supported on common end socket with. The utility model discloses to join in marriage class, variable slope, supporting function integration in the sliding tray is vice, reduced the vice quantity of friction, reduced the influence that the cylinder body toppled and the fluid pollutes to make the structure simplify greatly, improved operational reliability, operating pressure and the working life of axial plunger pump.

Description

Tandem type axial plunger pump

Technical Field

The utility model belongs to the technical field of hydraulic transmission and control, a serial-type axial plunger pump is related to, in particular to contain serial-type axial plunger pump of joining in marriage class sliding tray subcomponent.

Background

The axial plunger pump is one of the most widely used hydraulic components in modern hydraulic transmission, and the hingeless inclined shaft pump and the sliding shoe inclined disc type axial plunger pump are two types of axial plunger pumps which are most widely applied and are the most main at present. Along with the emergence of various large-scale machines, to the increasing demand of high pressure big discharge capacity plunger pump, in the practical application process, in order to improve the discharge capacity, often establish ties two independent swash plate type plunger pumps, form the double pump structure, establish ties double pump structure and contain parts such as two sets of independent casings, end socket, pump shaft, swash plate, return stroke dish, plunger, piston shoes, ball pivot, cylinder body, join in marriage food tray, current double pump structure has following characteristics: firstly, the structure is complex, the number of components is large, and the cost is high; secondly, the double-pump series structure has large structural size, is not compact enough and is often limited by installation space; third, such dual pump tandem configurations often contain three pairs of critical friction pairs: the reliability of the friction pair is directly related to the reliability of the whole double-pump structure. For the friction pair of the cylinder body and the valve plate, the cylinder body is inclined due to the action of the lateral force of the plunger, a wedge-shaped gap is often formed between the cylinder body and the valve plate, and the wedge-shaped gap destroys the normal seal between the cylinder body and the valve plate, so that the volume loss of the pump is increased, the sealing surface between the cylinder body and the valve plate is locally contacted, the surface burn between the cylinder body and the valve plate is caused, namely, the plate burning phenomenon is caused, and the pump completely loses functions. For the pair of friction pairs of the sliding shoes and the swash plate, the sliding shoes can overturn relative to the surface of the swash plate under the comprehensive action of centrifugal moment and return force caused by circumferential motion and friction moment generated by rotation along with the cylinder body in the process of high-speed motion, so that a wedge-shaped oil film is formed, the sliding shoes are eccentrically worn, and the normal work of the sliding shoes is damaged.

SUMMERY OF THE UTILITY MODEL

The invention of the utility model aims to: aiming at the problems of the existing series double-pump structure, a novel series axial plunger pump is provided, and the requirements of modern large machinery on the axial plunger pump with high power, high reliability, high pressure, large flow and small structural size are met.

The utility model discloses technical scheme implementation of technique: a tandem axial plunger pump, characterized by: comprises two sliding disc type through shaft plunger pumps and an end seat clamped between the two sliding disc type through shaft plunger pumps, wherein each sliding disc type through shaft plunger pump comprises a flow distribution sliding disc pair component, a main shaft and a cylinder body which is supported on the main shaft and synchronously rotates with the main shaft, the main shaft penetrates through the flow distribution sliding disc sub-assembly and is supported on the end seat, the flow distribution sliding disc sub-assembly 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 plunger ball sockets are arranged on the end surface of the sliding disc opposite to the cylinder body, the sliding disc is provided with an oil through hole for communicating the plunger ball socket and the static pressure bearing surface, the swash plate is provided with a flow distribution oil groove, the flow distribution oil groove is communicated with an oil inlet and an oil outlet arranged on the end seat, and the swash plates of the two sliding disc type through shaft plunger pumps are supported on the common end seat.

Series-type axial plunger pump, it is provided with a plurality of grease chambers on the static pressure bearing surface, be provided with low pressure distribution window and high pressure distribution window on the sloping cam plate with the terminal surface of sliding plate opposition, high, low pressure distribution window and grease chamber intermittent type intercommunication, the bearing surface with the end seat opposition has on the sloping cam plate and takes shape to be columniform cylindrical bearing surface, the configuration has the flute profile low pressure mouth and the flute profile high-pressure port for the flute profile on the cylindrical bearing surface of sloping cam plate, flute profile low pressure mouth and flute profile high-pressure port correspond the intercommunication with low pressure distribution window and high pressure distribution window respectively.

Series-type axial plunger pump, its the intercommunication notch that has the second cavity of intercommunication flute profile low pressure mouth and sliding tray formula logical axle plunger pump shell on the cylinder supporting surface of sloping cam plate.

Series-type axial plunger pump, its press from both sides between sliding tray and the sloping cam plate and be equipped with the valve plate, the sliding tray supporting just keeps sliding fit with the valve plate on the valve plate, be provided with high, low pressure valve port on the valve plate, hydraulic oil flows through the valve oil groove on the sloping cam plate, the valve port on the valve plate, the grease chamber of sliding tray, leads to oilhole and plunger centre bore under the reciprocal effect of plunger, realizes sucking, discharging of hydraulic oil.

Series-type axial plunger pump, its the one end supporting of main shaft is on first bearing, and other end tip runs through the sliding tray subassembly of joining in marriage a class and passes through the axle sleeve connection, the axle sleeve supporting is on the end seat, first bearing sets up to radial thrust bearing, main shaft and cylinder body are at rotatory during operation, and hydraulic pressure axial force passes through the cylinder body on first bearing transmits to the casing.

Series-type axial plunger pump, its cylinder body one end is provided with the check valve that only allows fluid to get into the plunger hole from the casing cavity, the check valve contains the valve body of being connected with the cylinder body, sets up at the inside case of valve body, fixes retaining ring on the valve body and sets up the spring between case and retaining ring, the check valve only allows low pressure fluid to flow to the plunger hole direction of cylinder body from the second cavity of casing.

Series-type axial plunger pump, its sloping cam plate peripheral part is provided with bellied supporting fender portion slide tray periphery and supporting fender portion are inboard between press from both sides and are equipped with the third bearing, the slide tray is in order to follow its radial confined state supporting on the third bearing.

Series-type axial plunger pump, it is in join in marriage vice one side of class sliding tray and be 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 on the bearing backstop portion, block device is in order to retrain the mode that the outside removal of third bearing restricted the sliding tray and keeps away from the sloping cam plate terminal surface.

Series-type axial plunger pump, its the main shaft end connection that two sliding tray formulas lead to an arbitrary sliding tray formula and lead to a plunger pump has oil replenishing pump or main pump in the plunger pump of two sliding tray formulas.

Series-type axial plunger pump, its the plunger contains the connecting rod plunger of taking the toper structure or the spherical plunger's of universal hinge in the both ends all is provided with the connecting rod plunger of bulb or takes, but plunger one end cylinder body reciprocating sliding's mode relatively inserts in the plunger hole of cylinder body, the other end is kept away from the state limited and can heeling in with relative sliding plate terminal surface and is fixed in 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.

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

1. the utility model discloses establish ties two sliding tray formula through-shaft plunger pumps together, can satisfy big discharge capacity, high pressure, high-power requirement.

2. The utility model discloses a serial-type axial plunger motor, the opposition sets up the sloping cam plate to make the sloping cam plate supporting on a common end seat, set up on the sloping cam plate and inhale the oil discharge passageway and with set up the business turn over hydraulic fluid port intercommunication on the end seat, can make the structure simplify greatly, the size is littleer, the structure is compacter, the weight of pump or motor is littleer, has consequently improved its unit mass power density.

3. 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 sliding tray is vice and the plunger is vice, compares current pair axial plunger pump: firstly, a flow distribution pair is reduced, so that the leakage of oil is reduced, and the efficiency is improved; secondly, the lateral force of the plunger is greatly reduced, and the overturning phenomenon of the cylinder body is eliminated or reduced; thirdly, because the cylinder body end does not have the flow distribution pair, so there are not wearing and tearing, the leakage scheduling problem in the cylinder body end, even there is some lateral force to produce the overturning effect to the cylinder body, also can not produce the eccentric wear and lead to the inefficacy scheduling problem, so this kind of structure makes the life-span of cylinder body longer, and later stage maintenance is still less, has reduced use cost.

4. 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 twin plunger pump 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.

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

Drawings

Fig. 1 is a schematic structural view of a tandem axial plunger pump of the present invention.

Fig. 2 is a sectional view taken along a line a-a of the tandem axial plunger pump of fig. 1 according to the present invention.

Fig. 3 is a plan view of one end of the middle slide plate of the present invention.

Fig. 4 is a cross-sectional view of the sliding plate structure B-B in fig. 3 according to the present invention.

Fig. 5 is a plan view of the other end of the middle sliding plate of the present invention.

Fig. 6 is a plan view of the bearing surface of one end of the swash plate opposite the slide plate according to the present invention.

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

Fig. 8 is a plan view of the swash plate with communication notches opposite the end seats of the present invention.

Fig. 9 is a cross-sectional view of fig. 7 and 8 of the present invention.

Fig. 10 shows another embodiment of the tandem axial plunger pump of the present invention.

Fig. 11 is a cross-sectional view taken along line E-E of the tandem axial piston pump of fig. 10 according to the present invention.

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

Fig. 13 shows a tandem axial plunger pump of the present invention, which comprises a port plate and a check valve disposed at the end of the cylinder body.

FIG. 14 is a plan view of the middle port plate of the present invention

The labels in the figure are: 10 is a main shaft, 10C is a main shaft axis, 12 connecting device, 13 is a main shaft shoulder, 15 is a shaft sleeve, 21 is a first bearing, 23 is a third bearing, 32 is a shell, 33 is an end seat, 33a is an oil inlet, 33b is an oil outlet, 33d is a flow passage, 33e is a sliding arc surface, 34 is a first cavity, 35 is a second cavity, 38 is a swash plate connecting part, 39 is an oil supplementing pump, 40 is a swash plate, 41 is a swash plate supporting surface, 41a is a supporting stop part, 42 is a flow distributing oil groove, 43 is a low-pressure flow distributing window, 44 is a high-pressure flow distributing window, 45 is a cylindrical supporting surface, 46 is a groove-shaped low-pressure port, 47 is a groove-shaped high-pressure port, 48 is a communicating notch, 50 is a sliding plate, 50C is a sliding plate axis, 51 is a static pressure supporting surface, 52 is a boss 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 and, 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 center hole, 73 is a tapered rod part, 74 is a plunger part, 80 is a cylinder body, 81 is a plunger hole, 82 is a main shaft assembly hole, 80C is a cylinder body center axis, 90 is a flow distribution disc, 91 is a flow distribution support surface, 92 is a low-pressure flow distribution port, 93 is a high-pressure flow distribution port, 100 is a center spring, 101 is a spherical hinge, 102 is a stop, 110 is a check valve, 111 is a valve body, 112 is a valve core, 113 is a spring, 114 is a retainer ring, 140 is an engaging device, and 141 is a cylinder clamp spring.

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 a swash plate type plunger pump is held horizontally, with the coupling end side of the main shaft to the left and the end seat 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, but for convenience of description and simplicity of description, and not to indicate or imply that the device or element referred to must have a particular orientation, and that the device or element referred to must be constructed and operated in a particular orientation, it is to be understood that the invention can be manufactured, stored, transported, used, and sold in an orientation other than the position described.

Example 1:

as shown in fig. 1 to 9, in the preferred embodiment of the tandem axial plunger pump of the present invention, the tandem axial plunger pump includes two sliding-disk through-shaft plunger pumps and an end seat 33 interposed between the two sliding-disk through-shaft plunger pumps, each sliding-disk through-shaft plunger pump includes a flow-distributing sliding-disk subassembly, a main shaft 10, a cylinder 80 supported on the main shaft 10 and rotating synchronously with the main shaft 10, and a plunger 70, the main shaft 10 penetrates the flow-distributing sliding-disk subassembly and is supported on the end seat 33, the flow-distributing sliding-disk subassembly includes a swash plate 40 and a sliding disk 50 supported on the swash plate 40, the sliding disk 50 is an integral structure, the end surface of the sliding disk 50 opposite to the swash plate 40 is provided with a static pressure bearing surface 51, the sliding disk 50 is provided with a plurality of plungers 58 distributed on one side end surface, a plurality of oil chambers 53a distributed on the other side end surface, and a large-diameter oil through-ball socket 58 and 53a communicating the plunger ball socket 58 and 53a One end of the plunger 70 is arranged in the plunger ball socket 58, the other end of the plunger 70 is inserted into the cylinder block 80, one end of a plunger center hole 72 in the plunger 70 is communicated with the oil through hole 53, the other end of the plunger 70 is communicated with a plunger hole 81 in the cylinder block 80, a flow distribution oil groove 42 is arranged on the swash plate 40, the swash plates 40 of the two sliding plate type through shaft plunger pumps are supported on a common end seat 33, the flow distribution oil groove 42 is communicated with an oil inlet 33a and an oil outlet 33b which are arranged on the end seat 33, and the two swash plates 40 are supported on the common end seat 33.

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 the embodiment of the tandem axial plunger pump, as shown in fig. 1 and 2, the end seat 33 is disposed at the middle, and the left and right sides are respectively provided with a sliding disc type through shaft axial plunger pump, and particularly, the sliding disc type through shaft axial plunger pumps at the left and right sides are of a symmetrical structure. The sliding disc type through shaft axial plunger pumps on the left side and the right side share one end seat 33, the end seat 33 is used for sealing one end opening of pump housings on the two sides, and the sliding disc type through shaft axial plunger pumps on the left side and the right side are fixedly connected with the end seat 33 through bolts. For the sake of convenience of explanation, the sliding-disk through-shaft axial plunger pump on one side is taken as an example for the sake of explanation because the sliding-disk through-shaft axial plunger pumps on both sides of the end seat 33 are similar in structure.

The end seat 33 is used for closing an opening at one end of the housing body 32, and the end seat 33 is provided with an oil inlet 33a and an oil outlet 33b of the pump, a flow passage 33d communicated with the swash plate oil distribution groove 42 and a sliding arc surface 33e for supporting the swash plate; when the tandem axial piston pump is a variable displacement pump, a variable displacement mechanism (not shown) for variable displacement oscillation is connected to the housing 32, and the variable displacement mechanism is connected to a variable displacement connecting portion 38 provided on a swash plate 40, and the swash plate 40 and a slide plate 50 rotate in the second cavity 35 under the action of the variable displacement mechanism.

The tandem type axial plunger pump comprises two main shafts 10, a first bearing 21 is arranged between the main shafts 10 and a shell body 32 in a clamping mode, one end of each main shaft 10 is supported on the shell body 32 through the first bearing 21, the other end of each main shaft 10 penetrates through a flow distribution sliding disc pair to an end seat 33 and is connected through a shaft sleeve 15, the shaft sleeves 15 are supported on the end seats 33, the main shafts 10 can freely rotate around the axes of the main shafts 10 relative to the shell body 32, a key connection structure used for connecting a cylinder body 80 is arranged on the circumferential surface of the middle portion of each main shaft 10, and the main shafts 10 drive the cylinder body 80 to synchronously rotate through the key connection structure.

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 80 abuts against the main shaft shoulder 13 and is transmitted to the first bearing 21 through the main shaft shoulder 13 and further transmitted to the shell 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, and it is alternatively possible, for example, for the first bearing 21 to be provided as a combined bearing system of radial ball bearing plus thrust bearing, the cylinder 80 directly abutting on the radial thrust bearing and transmitting the axial force to the housing 32, the radial force being borne by the radial ball bearing and the sleeve 15 supported at both ends of the spindle 10.

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 assembling hole 82 for accommodating a main shaft at the center, and the plunger holes 81 of the cylinder body 80 have a structure with one closed end and one open end. Preferably, the number of the plunger holes 81 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 closed 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 balls 58 are provided at positions facing the plunger 70 in the circumferential direction of the end surface of the slide plate 50 facing the cylinder, the plunger balls 58 form recesses having substantially hemispherical openings in the end surface of the slide plate 50, the plunger balls 58 support 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 balls 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. 3, 4 and 5, a static pressure bearing surface 51 is provided on an end surface of the swash plate 50 facing the swash plate, the swash plate axis 50C forms a certain angle with the main shaft axis 10C, and the static pressure bearing surface 51 is supported on the swash plate 40 and always keeps a sliding fit with the swash plate 40. The hydrostatic bearing surface 51 is provided with a plurality of oil chambers 53a in a kidney shape, preferably, the oil chambers 53a are uniformly distributed on the hydrostatic bearing surface 51 centering on a sliding plate axis 50C, and the sliding plate 50 is provided with large-aperture oil through holes 53 communicating the plunger ball sockets 58 with the oil chambers 53 a.

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

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 and an outer sealing part 54 which are distributed inside and outside the oil chamber 53a in the radial direction, and a spacing sealing part 56 which is 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. 6, the swash plate 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, and 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 a kidney shape. For the purpose of making the swash plate have a certain pre-pressure-increasing and pre-pressure-decreasing, the low pressure distribution window 43 and the high pressure distribution window may be rotated at a certain angle along the central axis of the swash plate, or specifically, a throttling groove or hole (not shown) may be provided on the end of the low pressure distribution window 43 to transition from the low pressure distribution window 43 to the high pressure distribution window 44 and on the end of the high pressure distribution window 44 to transition from the high pressure distribution window 44 to the low pressure distribution window 43, so as to play the role of pre-pressure-decreasing and pre-pressure-increasing from high pressure to low pressure or from low pressure to high pressure.

As shown in fig. 7 to 9, the bearing surface of the swash plate 40 facing the end seat 33 is provided with a cylindrical bearing surface 45 formed in a cylindrical shape, and the end seat 33 is provided with a sliding arc surface 33e having the same radius as the cylindrical bearing surface 45 of the swash plate, so that the cylindrical bearing surface 45 of the swash plate is always kept in a close contact state when sliding on the sliding arc surface of the end seat. 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 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. 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 swash plate cylindrical bearing surface 45 seals oil when sliding on the sliding arc surface 33e of the end seat. 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 seat 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 disc, the 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 sliding disc 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 seat oil outlet 33 b.

In operation, hydraulic pressure acts on the plunger 70 and is further transmitted to the disc 50, and in general, the axial force of the plunger 70 acting on the disc 50 is greater than the sum of the supporting force of the swash plate 40 acting on the disc 50 through oil film reaction and the return force of the plunger 70, so that the disc 50 always slides against the swash plate 40 through a layer of oil film. However, since the initial seal is still required between the slide plate 50 and the swash plate 40 at the time of starting the plunger pump or the motor to quickly build up the oil pressure, an initial seal device must be provided on the side of the distribution slide plate pair in order to maintain the slide plate 50 and the swash plate 40 in a pre-tightened state immediately after starting the operation.

The initial sealing device comprises a central spring 100, a spherical hinge 101 and a stop 102, wherein the central spring 100 has a certain pretightening force after being installed, and the pretightening force acts on the pressure plate 60 through the spherical hinge 101 and is further transmitted to the sliding plate 50, so that the sliding plate 50 is always abutted against the swash plate 40, and a certain sealing capacity is kept.

Example 2:

as shown in fig. 10 to 13, the main difference from embodiment 1 is that a third bearing 23 is provided on the outer peripheral portion of a slide plate 50 for supporting, a support stopper portion 41a is provided on the outer peripheral portion of the swash plate 40, a third bearing 23 is interposed between the outer side of the slide plate 50 and the inner side of the support stopper portion 41a, and the slide plate 50 is supported by the third bearing 23 in a radially constrained 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 tandem axial plunger pump, the high-pressure area 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 disc 50, and the hydraulic force pushes the sliding disc 50 to the swash plate 40 and is tightly contacted with the end surface 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 plate 50, and balances the lateral component of the acting force of the sliding plate 50, so that the lateral force of the sliding plate 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 plunger pump are improved.

At the same time, it is particularly evident that the return stroke of the axial piston pump of the slide-disk-mounted type is greatly simplified, and the return stroke structure comprises a restraint device arranged on the secondary side of the slide disk, which restrains the slide disk 50 from moving away from the end face of the swash plate 40 under the action of the return force.

As shown in fig. 12, the restricting means includes a stopper 57 having an outward protrusion on the side of the slide plate 50 closer to the static pressure bearing surface 51, and an engaging means 140 provided on the bearing stopper 41 a. The stopping portion 57 is used for limiting the movement of the third bearing 23, and the engaging means includes an engaging peripheral groove provided on the support stopping portion 41a and adjacent to the third bearing 23, and a snap spring (not shown) provided on the engaging peripheral groove and limiting the sliding plate from moving away from the end surface of the swash plate 40 in a manner of limiting the outward movement of the third bearing 23.

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 a port plate, and there is no friction pair supported by a static pressure oil film, and it is not necessary to apply a pre-tightening force to the end of the cylinder 80 to achieve the sealing purpose, only the sliding plate pair is required to be provided with the restraint device 140, so that the return stroke requirement of the plunger can be met, and no additional pre-tightening or return stroke components such as a central spring are required to be added, so that compared with the existing plunger pump, the restraint device greatly simplifies the structure, and avoids the phenomena such as breakage of the central spring due to fatigue damage. 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 3:

as shown in fig. 13, the main difference from the other embodiments 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, a high-pressure port 93 and a low-pressure port 92 are provided in the port plate 90, and as shown in fig. 14, 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 in 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; or in particular, 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 4:

the main difference from the other embodiments is that the tandem axial plunger pump is a tandem plunger pump with an oil replenishing pump, in the illustrated embodiment, an oil replenishing pump 39 is connected to the end of one of the main shafts 10 through the connecting device 12, and the oil replenishing pump 39 is used for supplying oil to the hydraulic system or providing hydraulic operating force; the oil supplementing pump is connected with the shell through bolts, and the external oil supplementing pump 39 can be a gear pump or a vane pump and the like.

Example 5:

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

When the pump works, 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 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; the other path is as follows: low pressure oil enters the cylinder plunger bore 81 directly from the housing second cavity 35 through the check valve 110 at the end of the cylinder 80; during oil discharge, high-pressure oil passes through the large-aperture plunger center hole 72, the plunger ball socket 58, the large-aperture oil through hole 53, the sliding disc 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

1. A tandem axial plunger pump, characterized by: the plunger pump comprises two sliding disc type through-shaft plunger pumps and an end seat (33) clamped between the two sliding disc type through-shaft plunger pumps, wherein each sliding disc type through-shaft plunger pump comprises a flow distribution sliding disc subassembly, a main shaft (10) and a cylinder body (80) supported on the main shaft (10) and synchronously rotating with the main shaft (10), the main shaft (10) penetrates through the flow distribution sliding disc subassembly and is supported on the end seat (33), the flow distribution sliding disc subassembly 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 of the sliding disc (50) opposite to the swash plate (40), a plurality of plunger ball sockets (58) are arranged on the end surface of the sliding disc (50) opposite to the cylinder body (80), and a through ball socket (53) for communicating the plunger ball sockets (58) and the static pressure oil hole bearing surface (51) is arranged on the sliding disc (50), the swash plates (40) are provided with a flow distribution oil groove (42), the flow distribution oil groove (42) is communicated with oil inlet and outlet ports (33a, 33b) arranged on the end seat (33), and the swash plates (40) of the two swash plate type through-shaft plunger pumps are supported on the common end seat (33).

2. The in-line axial plunger pump of claim 1, wherein: the static pressure bearing surface (51) is provided with a plurality of oil chambers (53a), the end surface of the swash plate (40) opposite to the slide plate (50) is provided with a low-pressure flow distribution window (43) and a 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 (53a), the bearing surface of the swash plate (40) opposite to the end seat (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 correspondingly communicated with the low-pressure flow distribution window.

3. The in-line axial plunger pump of claim 2, 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 sliding-plate type through-shaft plunger pump shell.

4. The in-line axial plunger pump of claim 1, 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 (90), an oil chamber (53a) in the sliding disc (50), an oil through hole (53) 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.

5. The in-line axial plunger pump of claim 1, wherein: one end of the main shaft (10) is supported on a first bearing (21), the end part of the other end of the main shaft penetrates through the flow distribution sliding disc pair assembly and is connected through a shaft sleeve (15), the shaft sleeve (15) is supported on an end seat (33), the first bearing (21) is arranged as a centripetal thrust bearing, and when the main shaft (10) and the cylinder body (80) rotate to work, hydraulic axial force is transmitted to the shell through the first bearing (21) through the cylinder body.

6. The in-line axial plunger pump of claim 1, wherein: one end of the cylinder body (80) is provided with a one-way valve (110) only allowing oil to enter the plunger hole (81) from the cavity of the shell, the one-way valve (110) comprises a valve body (111) connected with the cylinder body (80), a valve core (112) arranged in 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), and the one-way valve (110) only allows low-pressure oil to flow from the second cavity (35) of the shell to the plunger hole (81) of the cylinder body.

7. The in-line axial plunger pump of claim 1, wherein: a convex supporting stop part (41a) is arranged on the outer periphery of the swash plate (40), a third bearing (23) is arranged between the outer periphery of the sliding plate (50) and the inner side of the supporting stop part (41a), and the sliding plate (50) is supported on the third bearing (23) in a radial constrained state.

8. The in-line axial plunger pump of claim 7, 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 (41a), 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.

9. The in-line axial plunger pump of claim 1, wherein: the end of a main shaft (10) of any one of the two sliding disc type through shaft plunger pumps is connected with an oil replenishing pump (39) or a main pump.

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