Full-hydraulic supporting sliding disc pair structure

Abstract

The utility model relates to the technical field of hydraulic transmission control structures, in particular to a full-hydraulic-bearing sliding plate pair structure which comprises a swash plate, a sliding plate arranged on the swash plate, a swash plate positioning seat used for keeping the axial positions of the sliding plate and the swash plate and a pressing plate. The swash plate positioning seat comprises a shaft part connected with the swash plate, and the sliding plate is sleeved on the shaft part and rotates along the shaft part; an oil groove is formed in the matching surface of the shaft part and the sliding disc and is communicated with the positioning seat drainage channel, and oil liquid with set pressure is introduced through the positioning seat drainage channel, so that the sliding disc and the shaft part form static pressure support for counteracting lateral force. According to the utility model, by optimizing and adjusting the structure of the sliding disc pair, not only is the stability of the supporting operation of the sliding disc on the swash plate improved and the axial and lateral movement collision avoided, but also the abrasion of a friction surface is reduced by forming static pressure supporting, so that the sliding disc can be kept stable and reliable in long-term operation, and the service life is effectively prolonged.

Description

Technical Field

[0001] The utility model relates to the technical field of hydraulic transmission control structures, in particular to a fully hydraulically supported sliding disc auxiliary structure. Background Art

[0002] Axial piston pumps and motors are one of the most widely used hydraulic components in modern hydraulic transmissions, among which hingeless bevel axis pumps and slipper-type swash plate pumps are the two most widely used and main types of axial piston pumps.

[0003] Among the existing disclosed technologies, the sliding plate type piston pump combines the advantages of the existing inclined axis pump and the sliding shoe type inclined plate pump and avoids their respective shortcomings. The significant advantages are that it reduces the lateral force acting on the cylinder body by the plunger, basically eliminates the centrifugal overturning of the sliding shoe, significantly improves the operating conditions of the three major friction pairs, and can make the overall structure simpler and more compact. The sliding plate pair structure in the sliding plate type piston pump is the most critical component of the entire sliding plate pump. Among them, the two pairs of friction pairs, the sliding plate and the inclined plate, and the sliding plate and the inclined plate positioning seat, are the most critical, which directly determine the various performance indicators and service life of the sliding plate pump. During the development of the sliding plate type piston pump, it was found through multiple tests that some areas of the sliding plate and the inclined plate positioning seat often experience abnormal wear and other phenomena. In a short period of time, the problem area is mainly concentrated near the outer edge of the sliding plate on the side of the plunger. After running for a period of time, it is found that it spreads to the entire contact area. Through in-depth analysis, it is found that the main causes of abnormal wear are:

[0004] (1) The lateral force exerted by the sliding plate on the swash plate locating seat is too large, causing excessive contact wear between the sliding plate and the swash plate locating seat;

[0005] (2) The lateral force exerted by the sliding plate on the swash plate positioning seat has a certain overturning effect on the sliding plate as a whole.

[0006] Therefore, in view of the abnormal wear problem of the sliding plate and the swash plate positioning seat occurring during the test process, a more reasonable sliding plate and swash plate positioning seat support technical solution is proposed to solve the defects in the prior art. Utility Model Content

[0007] In order to overcome at least one of the defects mentioned above, the utility model proposes a fully hydraulically supported sliding plate auxiliary structure, which supplies oil to the supporting friction surface by adjusting the oil circuit structure of the sliding plate and the inclined plate to lubricate the supporting friction surface, thereby improving the lubrication effect of the entire friction pair and reducing the wear of the sliding plate auxiliary structure during operation.

[0008] In order to achieve the above technical effects, the sliding disc auxiliary structure disclosed in the utility model can adopt the following technical solutions:

[0009] A fully hydraulically supported sliding plate auxiliary structure comprises a swash plate, a sliding plate arranged on the swash plate, a swash plate positioning seat and a pressure plate for maintaining the axial position of the sliding plate and the swash plate; the characteristics are as follows: the swash plate positioning seat comprises a shaft portion connected to the swash plate, the sliding plate is sleeved on the shaft portion and rotates along the shaft portion; an oil groove is provided on the mating surface of the shaft portion and the sliding plate, and the oil groove is connected to a drainage channel of the positioning seat and introduces oil of a set pressure through the drainage channel of the positioning seat so that the sliding plate and the shaft portion form a static pressure support to offset the lateral force.

[0010] The above disclosed sliding plate subassembly delivers oil with a relatively high pressure between the shaft and the sliding plate through the drainage channel of the positioning seat for lubrication support, thereby avoiding wear caused by continuous friction between the sliding plate and the shaft.

[0011] Furthermore, the drainage channel of the positioning seat can be constructed in a variety of forms, which are not limited to the only one. Here, an optimization is made and one of the feasible options is proposed: the drainage channel of the positioning seat includes an axial drainage hole extending into the shaft portion, and the axial drainage hole is connected to the oil groove through the first radial drainage hole and is connected to the swash plate drainage channel through the second radial drainage hole. When such a solution is adopted, the axial drainage hole can be opened from one end of the shaft portion and extended axially, and the opening of the axial drainage hole can be closed during use.

[0012] Furthermore, when the sliding plate is installed on the swash plate positioning seat, the axial position of the sliding plate needs to be maintained so that the sliding plate and the swash plate fit more tightly and stably. There are many solutions for maintaining the axial position, which are not limited to the only one. Here, an optimization is made and one of the feasible options is proposed: a boss structure is formed on the sliding plate, and the swash plate positioning seat also includes a limit plate formed at the end of the shaft. When the sliding plate is sleeved and fitted to the swash plate positioning seat, the limit plate presses against the boss structure and prevents the sliding plate from moving toward the end of the shaft. When such a solution is adopted, the boss structure is integrally formed with the sliding plate, and the limit plate structure can also be integrally formed with the swash plate positioning seat.

[0013] Furthermore, the boss structure can be constructed in a variety of forms, and its structure is not limited to a single one. Here, an optimization is made and one of the feasible options is proposed: the boss structure is continuously arranged along the circumference to form a cylindrical structure, and the top of the boss structure is formed with an oil discharge groove connecting the inner and outer sides of the boss structure, or the edge of the limit plate is formed with an oil discharge groove. When such a scheme is adopted, the boss structure and the limit plate structure are tightly fitted, and the oil discharge groove is used to discharge the high-pressure oil formed by the shaft and the sliding plate, thereby reducing the influence of excessive oil pressure on the force balance under the premise of ensuring that the oil forms a static pressure support.

[0014] Furthermore, after the sliding disc is matched to the shaft, the oil on the sliding disc can also be used as a static pressure support. The specific method is not limited to the only one. Here, an optimization is made and one of the feasible options is proposed: the sliding disc is provided with a sliding disc center hole corresponding to the shaft, and the sliding disc is also provided with a plurality of plunger ball sockets for matching the plunger rod at circumferential intervals, and a plurality of sliding disc drainage holes are extended from the plunger ball socket to the sliding disc center hole, and the sliding disc drainage holes are used to guide the oil in the plunger ball socket to the oil tank. When such a scheme is adopted, part of the oil at the sliding disc ball socket can reach the oil tank through the sliding disc drainage holes to lubricate the matching structure of the sliding disc and the shaft.

[0015] Furthermore, the friction surface where the swash plate and the sliding plate are in contact is also lubricated and a hydrostatic support is formed. This effect is achieved by guiding the oil to the friction surface. The specific form is not limited to a single one. Here, an optimization is made and one of the feasible options is proposed: a waist-shaped hole is formed on the friction surface of the swash plate facing the sliding plate. The waist-shaped hole is connected to the swash plate drainage channel and introduces oil of a set pressure through the swash plate drainage channel to form a hydrostatic support between the sliding plate and the friction surface of the swash plate. When such a scheme is adopted, the waist-shaped hole is bent according to the circumference, and the central angle corresponding to the waist-shaped hole is greater than the central angle corresponding to the sealing belt between the sliding plate oil chambers on the sliding plate, so that continuous replenishment of oil can be achieved to maintain the stable effect of the hydrostatic support.

[0016] Furthermore, the purpose of setting the swash plate drainage channel is to introduce external oil and guide it to the waist-shaped hole on the friction surface of the swash plate and the oil groove on the shaft. The swash plate drainage channel can be constructed in various forms, which are not limited to the only one. Here, optimization is made and one feasible option is proposed: the swash plate drainage channel includes a swash plate first drainage hole extending from the bottom of the waist-shaped hole to the inside of the swash plate, and a swash plate second drainage hole connected to the swash plate first drainage hole and extending from the outside of the swash plate to the center hole of the swash plate. When such a solution is adopted, the swash plate first drainage hole and the swash plate second drainage hole are opened from the friction surface and the side surface of the swash plate respectively and then extended and connected.

[0017] Furthermore, when oil is passed between the swash plate and the sliding plate to form a hydrostatic support, it is necessary to keep the swash plate stable to avoid the balance of the influence of the accumulation of oil in the partial area between the swash plate and the sliding plate. Therefore, it is necessary to discharge the excess oil to the outside. This can be achieved in a variety of ways, which are not limited to the only one. Here, an optimization is made and one of the feasible options is proposed: an oil unloading channel is provided on the friction surface of the swash plate and the sliding plate, and the oil unloading channel includes a first oil unloading hole of the swash plate extending from the friction surface to the inside of the swash plate, and a second oil unloading hole of the swash plate connected to the first oil unloading hole of the swash plate and extending to the outside of the swash plate. When such a scheme is adopted, the first oil unloading hole of the swash plate and the second oil unloading hole of the swash plate extend inward and connect from the friction surface of the swash plate and the opening on the side surface of the swash plate, respectively.

[0018] Furthermore, after the swash plate positioning seat is connected to the swash plate, it is used to apply pressure to the pressure plate and the sliding plate from the axial direction to keep the axial position of the pressure plate and the sliding plate stable. Therefore, the connection between the swash plate positioning seat and the swash plate needs to be kept fixed to avoid self-movement during operation that affects stability. Specifically, axial fixation can be achieved in a variety of ways. Here, optimization is performed and one of the feasible options is proposed: the center hole of the swash plate forms a blocking structure that prevents the axial displacement of the shaft, the front end of the shaft passes through the center hole of the swash plate and is connected to the backstop assembly, and the shaft is also provided with a shoulder that abuts against the blocking structure. When such a solution is adopted, the blocking structure includes a variable diameter step hole, and the shoulder of the shaft is blocked by the variable diameter structure; the backstop assembly includes a backstop cover plate.

[0019] Furthermore, after the swash plate positioning seat is fixed with the swash plate, it is necessary to prevent the swash plate positioning seat from circumferential movement, which can be achieved in a variety of ways. Here, an optimization is made and one of the feasible options is proposed: the swash plate center hole and the shaft portion are kept circumferentially fixed by a circumferential limiting structure. When such a solution is adopted, the circumferential limiting structure can be achieved by providing a limiting pin between the shaft portion and the swash plate center hole, that is, the swash plate center hole and the shaft portion are provided with grooves corresponding to form a limiting hole, and the limiting pin is inserted into the limiting hole so that the swash plate positioning seat can be kept fixed on the circumference.

[0020] Furthermore, after the shaft and the sliding plate cooperate to form a hydrostatic support, in order to avoid excessive oil pressure affecting the stable and reliable rotation of the sliding plate, an optimization is performed here and one of the feasible options is proposed: the swash plate positioning seat is provided with an axial oil unloading groove and a radial oil unloading groove, and the axial oil unloading groove is connected with the radial oil unloading groove and is used to guide and remove the excess oil between the swash plate positioning seat and the center hole of the sliding plate. When such a scheme is adopted, the axial oil unloading groove is staggered with the oil groove of the shaft, and the axial oil unloading groove extends axially and its length is greater than the width of the matching surface between the sliding plate and the shaft. The radial oil unloading groove is located at the limit plate. It extends radially to the edge of the limit plate.

[0021] Compared with the prior art, some beneficial effects of the technical solution disclosed in the utility model include:

[0022] The utility model optimizes and adjusts the sliding plate auxiliary structure, which not only improves the stability of the sliding plate's supporting operation on the inclined plate and avoids axial and lateral movement collisions, but also reduces the wear of the friction surface by forming a static pressure support, so that the sliding plate can remain stable and reliable in long-term operation and effectively extend its service life. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] In order to more clearly illustrate the technical solutions of the embodiments of the utility model, the drawings required for use in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the utility model and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other related drawings can be obtained based on these drawings without paying creative work.

[0024] Figure 1 It is an embodiment of the sliding plate auxiliary structure of the full hydraulic floating support in the utility model.

[0025] Figure 2 for Figure 1 A schematic structural diagram of another cross section of the embodiment.

[0026] Figure 3 This is a schematic diagram of the structure of the swash plate positioning seat.

[0027] Figure 4 This is a cross-sectional view of the sliding disc.

[0028] Figure 5 It is a schematic diagram of the structure on one side of the sliding disc support surface.

[0029] Figure 6 Schematic diagram of the inclined plate structure.

[0030] Figure 7 This is a schematic diagram of the inclined disk's orthographic projection.

[0031] Figure 8 It is another embodiment of the sliding plate auxiliary structure of the full hydraulic floating support in the utility model.

[0032] Fig. 9 for Figure 8 Schematic diagram of the sliding disk structure in the embodiment.

[0033] In the above drawings, the meanings of the various reference numerals are as follows:

[0034] 1. Plunger; 2. Pressure plate; 3. Sliding plate; 4. Slanting plate; 5. Slanting plate positioning seat; 31. Sliding plate oil chamber; 32. Sliding plate ball socket; 33. Oil through hole; 34. Sliding plate center hole; 35. Boss structure; 36. Sliding plate ball socket center; 37. Ball socket center plane; 38. Oil drain groove; 39. Sliding plate drainage hole; 40. Slanting plate support surface; 41. Slanting plate center positioning hole; 42. Slanting plate first drainage hole; 43. Slanting plate second drainage hole; 44. Slanting plate first oil discharge hole; 4 5. The second oil unloading hole of the swash plate; 46. The limit pin hole; 47. The waist-shaped groove of the swash plate; 51. The limit plate; 51a. The radial oil unloading groove; 52. The rotary matching part; 52a. The axial oil unloading groove; 53. The positioning part; 54. The connecting part; 55. The axial drainage hole; 56. The first radial drainage hole; 57. The oil groove; 58a. The outer sealing belt; 58b. The inner sealing belt; 58c. The intermediate auxiliary support; 59. The second radial drainage hole; 59a. The damping hole; 60. The limit pin. DETAILED DESCRIPTION

[0035] The present invention will be further explained below in conjunction with the accompanying drawings and specific embodiments.

[0036] In view of the fact that the sliding disc pair in the prior art suffers from significant operating wear, the following embodiments are optimized and overcome the defects in the prior art.

[0037] Example

[0038] like Figures 1 to 7 As shown, an embodiment of the fully hydraulic floating support sliding plate subassembly structure of the utility model is provided. In the embodiment shown, it includes a sliding plate 3; a swash plate 4; a swash plate positioning seat 5. The sliding plate 3 is an integral disc-shaped structure. One end face of the sliding plate 3 is provided with a plurality of sliding plate oil chambers 31 and supported on the swash plate 4 to form a static pressure support. The other end face of the sliding plate 3 is provided with a plurality of sliding plate ball sockets 32 and is used to connect the plunger ball head of the plunger rod 1. A sliding plate center hole 34 is provided in the middle of the sliding plate. On the swash plate positioning seat 5, at least one oil groove 57 is provided along the outer periphery of the swash plate 4 downward. The oil groove 57 introduces high-pressure oil from the positioning seat drainage channel in the sliding plate subassembly, so that a static pressure support is formed between the sliding plate and the swash plate positioning seat to offset most or all of the lateral component force of the sliding plate 3 acting on the swash plate positioning seat 5.

[0039] like Figure 1 As shown in the figure, through the force analysis of the plunger 1 and the sliding plate 3, it is known that the hydraulic plunger force F acting on the sliding plate by a single plunger 1 is 1 According to the lateral force F in the direction parallel to the swash plate 3 and the vertical force F perpendicular to the swash plate direction 2 Decomposed into: F 3 =F 1 sinα, F 2 =F 1cosα, so the total lateral force and total vertical force when multiple plungers act are ∑F 3 =nF 1 sinα and ∑F 2 =nF 1 cosα, under the action of high-pressure oil, the total lateral force and total vertical force are very large, and traditional bearing supports cannot meet the requirements. Therefore, the method of dealing with lateral force and vertical force becomes the key technology of plunger pumps, involving a series of technical problems such as material limits, precision machining, and bearing life.

[0040] The traditional single-shoe structure only designs a method to balance the force in the direction of the vertical swash plate, but cannot effectively balance the lateral force inside the plunger and the shoe. Therefore, it can only be transmitted to the cylinder body, the main shaft, and the bearing through the plunger, which indirectly causes a series of related problems such as wedge contact between the distribution plate and the sliding plate, deflection of the main shaft, excessive wear of the plunger and the plunger hole of the cylinder body, and excessive bearing support force, which become the most critical factors restricting the traditional plunger pump. It should be noted that this embodiment introduces high-pressure oil to offset most of the lateral force and vertical force respectively, so that the support between the sliding plate 3 and the swash plate positioning seat 5; the support between the sliding plate 3 and the swash plate 4 becomes a fully hydraulic floating support structure, which can overcome various problems of traditional plunger pumps caused by excessive lateral force.

[0041] The swash plate positioning seat 5 is provided with a limit plate 51, a rotary fitting portion 52, a positioning portion 53 and a connecting portion 54. The limit plate portion 51 has a certain gap with the sliding plate 3 and limits the sliding plate 3 from being away from the swash plate 4. The sliding plate 3 is supported on the rotary fitting portion 52 through a hydraulic floating support structure and slidingly cooperates with it. The positioning portion 53 is inserted into the central positioning hole 41 of the swash plate to play a central positioning and supporting role. The connecting portion 54 is fixedly connected to the swash plate 4 through threads or nuts.

[0042] The rotary mating portion 52 is provided with at least one oil groove 57, which is arranged in the downward direction along the swash plate, opposite to the lateral force direction of the sliding plate 3 acting on the swash plate positioning seat 5. The two sides of the oil groove 57 are respectively provided with an outer sealing belt 58a and an inner sealing belt 58b. In a special case, an intermediate auxiliary support 58c can be provided in the oil groove 57 area. The outer sealing belt 58a and the inner sealing belt 58b are used to seal the high-pressure oil to prevent leakage, and the intermediate auxiliary support 58c has an enhanced support function.

[0043] One preferred embodiment of the drainage structure is as follows: Figures 1 to 3 As shown, the drainage holes for introducing high-pressure oil from the sliding plate subassembly include at least one first radial drainage hole 56 arranged on the swash plate positioning seat 5; an axial drainage hole 55; and a second radial drainage hole 59. The axial drainage hole 55 is connected to the first radial drainage hole 56 and the second radial drainage hole 59 respectively, and the first radial drainage hole 56 is connected to the oil groove 57.

[0044] The swash plate 4 is provided with a first swash plate drainage hole 42 and a second swash plate drainage hole 43 connected to the sliding plate oil chamber 31. The first swash plate drainage hole 42 and the second swash plate drainage hole 43 are connected to each other, and the second swash plate drainage hole 43 is connected to the second radial drainage hole 59 on the swash plate positioning seat 5. The high-pressure oil flows from the sliding plate oil chamber 31 through the first drainage hole 42, the second swash plate drainage hole 43, the second radial drainage hole 59, the axial drainage hole 55, and the first radial drainage hole 56 to the oil groove 57.

[0045] In order to make the oil pressure on the oil groove 38 more stable and less affected by external loads, a damping hole can be provided on one or more of the first radial drainage hole; the axial drainage hole; the second radial oil through hole; the first drainage hole 42 of the swash plate and the second drainage hole 43 of the swash plate, for example Figure 2 In the embodiment, a damping hole 59a is provided in the second radial guide hole 59, and the damping hole has a smaller aperture.

[0046] A waist-shaped groove 47 is provided on the high-pressure side of the swash plate, and the first drainage hole 42 of the swash plate is provided within the range of the waist-shaped groove 47. The waist-shaped groove 47 is connected to the sliding plate oil chamber 31, and the first drainage hole 42 of the swash plate is connected to the waist-shaped groove 47 and the second drainage hole 43 of the swash plate respectively.

[0047] In order to ensure that the oil tank 57 can be continuously supplied with high-pressure oil, Figures 5 to 7 As shown, the opening angle (c) of the waist-shaped groove 47 on the swash plate 4 is greater than the angle (b) of the middle sealing zone between the waist-shaped sliding plate oil chambers 31, so that high-pressure oil continuously supplies oil to the oil groove 57 on the swash plate positioning seat 5.

[0048] Another preferred embodiment of the drainage structure is as follows: Figures 8-9 As shown, the drainage holes for introducing high-pressure oil from the sliding plate subassembly are sliding plate drainage holes 39 arranged on the sliding plate 3 and distributed along the radial direction. The sliding plate drainage holes 39 are connected to the sliding plate plunger ball socket 32 ​​and the sliding plate center hole 34. The high-pressure oil is drained to the oil groove 57 on the swash plate positioning seat 5 through the sliding plate drainage holes 39. It should be noted that, in order to facilitate processing, the sliding plate drainage holes 39 are inclined at a certain angle.

[0049] The sliding plate 3 is supported on the swash plate positioning seat 5 through a hydraulic floating support structure. The center points 36 of the sliding plate ball sockets form a ball socket center plane 37. The end surface of the support structure on the plunger side extends out of the ball socket center plane 37. Figure 4As shown, the central part of the sliding plate has a boss portion 35 extending along one side of the plunger, and the boss portion 35 exceeds the ball socket center plane 37 formed by the center of the sliding plate ball socket, and the distance between the two is a, and a is greater than zero. The design is based on the fact that the lateral force of the sliding plate is a force parallel to the swash plate surface and passes through the center point 36 of the sliding plate ball socket. The combined force point of this force should be within the range of the support structure, so that the sliding plate will not overturn and avoid abnormal wear of the sliding plate 3 and the swash plate positioning seat 4 near the sliding plate ball socket center plane 37.

[0050] In order to prevent the sliding plate from moving away from the swash plate and building up pressure, the limit plate portion 51 on the swash plate positioning seat 5 and the boss portion 35 of the sliding plate form a fixed gap structure to constrain the sliding plate from moving away from the swash plate. The gap is ensured by the machining accuracy of the size. Generally, the gap is best controlled within the range of 0 to 0.04 mm, which can ensure that the limit plate portion 51 and the boss portion 35 of the sliding plate can rotate freely relative to each other and that the plunger pump can effectively reduce pressure.

[0051] Since there is a clearance fit between the sliding plate 3 and the swash plate positioning seat 5, there is a small portion of the high-pressure oil outer sealing belt 58a in the oil groove 57; the inner sealing belt 58a leaks out, and the clearance between the limit plate part of the swash plate positioning seat and the sliding plate boss part 35 is small, and it is easy to build up pressure between the two to generate high pressure, thereby adversely affecting the swash plate positioning seat 5 and the sliding plate 3. At least one oil drain groove 38 can be provided on the disk surface of the limit plate part of the swash plate positioning seat 5 or on the end surface of the boss part 35 of the sliding plate. One end of the oil drain groove 38 is connected to the clearance between the sliding plate 3 and the swash plate positioning seat 5, and the other end is connected to the housing cavity.

[0052] Similarly, in order to prevent the oil leakage from the oil groove 57 through the inner sealing belt and the oil leakage between the sliding plate and the swash plate from accumulating in the cavity in the middle area between the sliding plate 3 and the swash plate 4, thereby destroying the oil film support between the sliding plate 3 and the swash plate 4, a swash plate first oil unloading hole 44 and a swash plate second oil unloading hole 45 are provided on the swash plate 4. The swash plate first oil unloading hole 44 and the swash plate second oil unloading hole 45 are communicated with each other, and the swash plate first oil unloading hole is also communicated with the cavity in the middle area between the sliding plate and the swash plate, and the swash plate second oil unloading hole 45 is communicated with the housing cavity.

[0053] In order to prevent the swash plate positioning seat 5 from rotating relative to the swash plate 4 under the action of the friction torque, a limiting hole or a limiting groove structure is provided on the swash plate center positioning hole 41 and / or the positioning portion 53 of the swash plate positioning seat, and a limiting pin or a limiting flat key 60 is provided between the swash plate center positioning hole 41 and the positioning portion 53 of the swash plate positioning seat. Figure 2 ; Figure 6 shown.

[0054] The above are the implementation methods listed in this embodiment, but this embodiment is not limited to the above optional implementation methods. Those skilled in the art can arbitrarily combine the above methods to obtain other various implementation methods. Anyone can derive other various implementation methods under the inspiration of this embodiment. The above specific implementation methods should not be understood as limiting the protection scope of this embodiment. The protection scope of this embodiment should be based on the definition in the claims.

Claims

1. A fully hydraulically supported sliding plate auxiliary structure, comprising a swash plate (4), a sliding plate (3) arranged on the swash plate (4), a swash plate positioning seat (5) for maintaining the axial position of the sliding plate (3) and the swash plate (4), and a pressure plate (2); characterized in that: The swash plate positioning seat (5) comprises a shaft portion connected to the swash plate (4), and the sliding plate (3) is sleeved on the shaft portion and rotates along the shaft portion; the matching surfaces of the shaft portion and the sliding plate (3) are provided with an oil groove, and the oil groove is connected to the positioning seat drainage channel and introduces oil reaching a set pressure through the positioning seat drainage channel so that the sliding plate (3) and the shaft portion form a static pressure support to offset the lateral force.

2. The fully hydraulically supported sliding plate auxiliary structure according to claim 1 is characterized in that: The positioning seat drainage channel comprises an axial drainage hole extending into the shaft portion, the axial drainage hole being connected to the oil groove through a first radial drainage hole and being connected to the swash plate drainage channel through a second radial drainage hole (59).

3. The fully hydraulically supported sliding plate auxiliary structure according to claim 1, characterized in that: A boss structure (35) is formed on the sliding plate (3), and the swash plate positioning seat (5) also includes a limit plate formed at the end of the shaft. When the sliding plate (3) is sleeved and fitted into the swash plate positioning seat (5), the limit plate presses against the boss structure (35) and prevents the sliding plate (3) from moving toward the end of the shaft.

4. The fully hydraulically supported sliding plate auxiliary structure according to claim 3 is characterized in that: The boss structure (35) is continuously arranged along the circumference to form a cylindrical structure, and an oil discharge groove is formed at the top of the boss structure (35) and connects the inner and outer sides of the boss structure (35), or an oil discharge groove is formed on the edge of the limit plate.

5. The fully hydraulically supported sliding plate auxiliary structure according to claim 1, 3 or 4, characterized in that: The sliding disk (3) is provided with a sliding disk center hole (34) corresponding to the shaft portion, and the sliding disk (3) is also provided with a plurality of sliding disk ball sockets (32) for matching the plunger (1) rod at circumferential intervals, and a plurality of sliding disk drainage holes (39) are extended from the sliding disk ball sockets (32) to the sliding disk center hole (34), and the sliding disk drainage holes (39) are used to guide the oil in the sliding disk ball sockets (32) to the oil tank.

6. The fully hydraulically supported sliding plate auxiliary structure according to claim 1 or 2, characterized in that: A waist-shaped hole is formed on the friction surface of the swash plate (4) facing the sliding plate (3), and the waist-shaped hole is connected to the swash plate drainage channel and introduces oil of set pressure through the swash plate drainage channel to form a static pressure support between the sliding plate (3) and the friction surface of the swash plate (4).

7. The fully hydraulically supported sliding plate auxiliary structure according to claim 2, characterized in that: The swash plate drainage channel comprises a swash plate first drainage hole (42) extending from the bottom of the waist-shaped hole to the inside of the swash plate (4), and a swash plate second drainage hole (43) connected to the swash plate first drainage hole (42) and extending from the outside of the swash plate (4) to the swash plate center positioning hole (41).

8. The fully hydraulically supported sliding plate auxiliary structure according to claim 1, characterized in that: An oil unloading channel is provided on the friction surface of the swash plate (4) and the sliding plate (3), and the oil unloading channel includes a first swash plate oil unloading hole extending from the friction surface toward the inside of the swash plate (4), and a second swash plate oil unloading hole (45) connected to the first swash plate oil unloading hole (44) and extending toward the outside of the swash plate (4).

9. The fully hydraulically supported sliding plate auxiliary structure according to claim 1, characterized in that: The swash plate center positioning hole (41) forms a blocking structure for blocking the axial displacement of the shaft portion. The front end of the shaft portion passes through the swash plate center positioning hole (41) and is connected to the backstop assembly. The shaft portion is also provided with a shaft shoulder abutting against the blocking structure.

10. The fully hydraulically supported sliding plate auxiliary structure according to claim 1, characterized in that: A limiting structure is provided between the swash plate positioning seat (5) and the swash plate central positioning hole (41) to prevent the swash plate positioning seat (5) from rotating relative to the swash plate (4).

11. The fully hydraulically supported sliding plate auxiliary structure according to claim 7, characterized in that: The waist-shaped hole is curved along a circle, and the center angle corresponding to the waist-shaped hole is greater than the center angle corresponding to the sealing belt between the sliding plate oil chambers (31) on the sliding plate (3).

12. The fully hydraulically supported sliding plate auxiliary structure according to claim 1, characterized in that: The swash plate positioning seat (5) is provided with an axial oil discharge groove (52a) and / or a radial oil discharge groove (51a), and the axial oil discharge groove (52a) is connected with the radial oil discharge groove (51a) and is used to guide and discharge excess oil between the swash plate positioning seat (5) and the sliding plate center hole (34).

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