A cylinder block fixed hydraulic motor

Abstract

A cylinder block-fixed hydraulic motor includes a stationary flow distribution surface and a rotating flow distribution surface. There are cylinder hole windows, an oil inlet window, and an oil outlet window on the stationary flow distribution surface, and there is a flow distribution window on the rotating flow distribution surface. The flow distribution window is a groove that is recessed inward along the rotating flow distribution surface. When the plunger is in the oil discharge section, the cylinder hole window connected to the plunger is communicated with the oil outlet window through the flow distribution window, and the oil fluid is discharged from the cylinder hole. When the plunger is in the oil inlet section, the cylinder hole window connected to the plunger is communicated with the oil inlet window through the flow distribution window, and the oil fluid enters the cylinder hole. The flow distribution window, the oil inlet window, and the oil outlet window on the flow distribution surface are all on the cylinder hole window belt, which can effectively reduce the width of the flow distribution belt and make the structure of the flow distributor more compact. Without increasing the width of the flow distribution belt, by disconnecting the oil inlet channels of a part of the oil inlet windows, the variable displacement of the hydraulic motor can also be achieved.

Description

Technical Field

[0001] The present invention relates to the technical field of hydraulic motors, and particularly to a cylinder block fixed hydraulic motor. Background Art

[0002] At present, most of the domestic housing-rotating hydraulic motors have a fixed cylinder block and a rotating housing with a guide rail to output power. As is well known, the valve plate type motor and pump are reversible, that is, the hydraulic motor can also be used as a hydraulic pump. For the convenience of understanding according to the prior art, the structural names and related parameters in such hydraulic motors or hydraulic pumps are defined and described as follows.

[0003] (1) Cylinder block: The surface of the cylinder block in contact with the flow distributor is called the stationary flow distribution surface. The window on the stationary flow distribution surface communicating with the plunger cylinder hole is called the cylinder hole window. The number of cylinder hole windows is z, and the angular width of the cylinder hole window is α z , and the angular width between the centers of two adjacent cylinder hole windows is ϕ z .

[0004] The channel through which the liquid enters the stationary flow distribution surface from the cylinder block is called the oil inlet channel. The window formed by the oil inlet channel on the stationary flow distribution surface is called the oil inlet window; when the plunger is at the oil inlet section position of the track, the oil enters the cylinder hole window through the oil inlet window and the flow distribution window, and the angular width of the oil inlet window is α a .

[0005] The channel through which the liquid enters the cylinder block from the stationary flow distribution surface is called the oil outlet channel. The window formed by the oil outlet channel on the stationary flow distribution surface is called the oil outlet window; when the plunger is at the oil outlet section position of the track, the oil enters the oil outlet window through the cylinder hole window and the flow distribution window, and the angular width of the oil outlet window is α b .

[0006] The angular width between the oil inlet window and the cylinder hole window is α az , the angular width between the oil outlet window and the cylinder hole window is α bz , and the angular width between the centers of two adjacent oil outlet windows and the oil inlet window is ϕ ab , and the angular width between the edges of two adjacent oil outlet windows and the oil inlet window is α ab .

[0007] The angular width between the center of the cylinder hole and the center of the cylinder hole window communicating therewith is called the angular displacement of the cylinder hole phase β z .

[0008] For the convenience of distinction, the plunger with the upward direction is numbered 1, and the plungers are sequentially numbered 1, 2, 3... in the clockwise direction. The nth plunger is called Qn; the cylinder hole window with the upward direction is numbered 1, and the cylinder hole windows are sequentially numbered 1, 2, 3... Z in the clockwise direction. The nth cylinder hole window is called Zn.

[0009] (2) Guide rail: The cylinder block is fixed, and the guide rail rotates relative to the cylinder block. It is now stipulated that when the guide rail rotates clockwise, it is a forward rotation, and when it rotates counterclockwise, it is a reverse rotation. If the rotation direction is not specified, it is uniformly assumed that the guide rail rotates clockwise.

[0010] The number of action of the guide rail is x. The near dead center points D and F are the center points of the near dead zone of the guide rail, and the far dead center points C, E, and G are the center points of the far dead zone of the guide rail; the angular amplitude of the zero-speed zone at point C is ∆c, the angular amplitude of the zero-speed zone at point D is ∆d, the angular amplitude of the zero-speed zone at point E is ∆e, the angular amplitude of the zero-speed zone at point F is ∆f, and the angular amplitude of the zero-speed zone at point G is ∆g. Generally, in theoretical calculations, ∆c = ∆d = ∆e = ∆f = ∆g = 0 is taken to calculate each flow distribution parameter.

[0011] The action angular amplitude corresponding to DF is ϕ x , and the phase displacement angular amplitude β of the guide rail x = 0. When rotating clockwise, the FE section is the oil outlet section, and the ED section is the oil inlet section; that is, the section in the direction of rotation of the outer dead center is the oil inlet section, and the section in the reverse rotation direction is the oil outlet section.

[0012] (3) Flow distributor: The flow distributor rotates synchronously with the guide rail relative to the cylinder block. Therefore, the number of pairs of flow distribution windows is equal to the number of actions of the guide rail. Since the flow distribution windows of the present invention can be connected to both the oil inlet window and the oil outlet window, the number of flow distribution windows of the present invention is equal to the number of actions of the guide rail.

[0013] The number of flow distribution windows is r, and the angular amplitude between the centers of two adjacent flow distribution windows is ϕ r , and the angular amplitude of the flow distribution window is α r , and the angular amplitude between two adjacent flow distribution windows is α r0 . Then ϕ r = 2π / r, and α r0 = 2π / r – α r .

[0014] The angular amplitude between the center line of the outer dead center of the guide rail and the center line of the flow distribution window is called the phase displacement angular amplitude β of the guide rail x .

[0015] (4) Flow distribution zone: The curved surface zone formed by all the windows and channels on the flow distribution surface rotating one week along the rotation center axis of the hydraulic motor / pump and connected end to end is called the flow distribution zone; among them, the curved surface zone formed by the cylinder hole window rotating one week along the rotation center is called the cylinder hole window zone, the curved surface zone formed by the oil inlet window rotating one week along the rotation center is called the oil inlet window zone, the curved surface zone formed by the oil outlet window rotating one week along the rotation center is called the oil outlet window zone, and the curved surface zone formed by the flow distribution window rotating one week along the rotation center is called the flow distribution window zone. The width of the flow distribution zone is called the flow distribution zone width. The smaller the flow distribution zone width, the smaller and more compact the flow distributor can be made.

[0016] The Hagglunds Viking motor in Sweden is a radial shaft - flow piston motor with a double - displacement cylinder block fixed and a housing rotating. The flow - distribution band of the Viking motor includes an oil - inlet window B band, an oil - inlet window A band, an oil - outlet window C band, and three sealing bands. This hydraulic motor has problems such as a complex flow - distribution band structure and a wide flow - distribution band width.

[0017] Patent Document 1: Chinese Utility Model Patent "A Housing - Rotating Hydraulic Motor" with application number 201621055806.1 (publication number: CN 206092285 U) discloses a cylinder - block fixed hydraulic motor. Its flow - distribution structure has an annular window on each of the inner and outer sides of the cylinder - hole window. The cylinder - hole window is connected to the annular oil - inlet window or oil - outlet window through a flow - distribution window to complete the flow - distribution. Its flow - distribution structure also has problems such as a wide flow - distribution band width, a large radial dimension required for the flow - distribution pair, and a complex structure.

[0018] Patent Document 2: Chinese Utility Model Patent "An Internal - Curve Low - Speed High - Torque Hydraulic Motor with a Rotating Housing for Outputting Torque" with application number 201621249879.4 (publication number: CN 206221143 U) discloses a cylinder - block fixed hydraulic motor. Its flow - distribution structure has two annular windows on the outer sides of the cylinder - hole window. The cylinder - hole window is connected to the annular oil - inlet window or oil - outlet window through a bridge - type flow - distribution window to complete the flow - distribution. Its flow - distribution band includes a cylinder - hole window band, an oil - outlet window band, an oil - inlet window band, and two sealing widths. Its flow - distribution structure also has problems such as a wide flow - distribution band width and an oversized structural dimension. Summary of the Invention

[0019] Aiming at the problems of a wide flow - distribution band width and a large structural dimension existing in the above - mentioned prior art, the present invention provides a cylinder - block fixed hydraulic motor, and the flow - distribution structure can effectively reduce the width of the flow - distribution band and make the flow - distributor structure more compact.

[0020] To achieve the above object, the technical solution adopted by the present invention is as follows:

[0021] A cylinder - block fixed hydraulic motor includes: a stationary flow - distribution surface with a cylinder - hole window, an oil - inlet window, and an oil - outlet window thereon, and a rotating flow - distribution surface with a flow - distribution window thereon. The flow - distribution window is a groove recessed inward along the rotating flow - distribution surface. Among them, the oil - inlet window band, the oil - outlet window band, the flow - distribution window band, and the cylinder - hole window band coincide.

[0022] Furthermore, the number of flow - distribution windows is equal to the number of guide - rail actions. At any position of the guide - rail, when the plunger is in the oil - outlet section, the cylinder - hole window is connected to the oil - outlet window through the flow - distribution window, and when the plunger is in the oil - inlet section, the cylinder - hole window is connected to the oil - inlet window through the flow - distribution window.

[0023] Furthermore, there is at least one oil - inlet window in the counter - clockwise direction and at least one oil - outlet window in the clockwise direction for any cylinder - hole window.

[0024] Further, the number of cylinder hole windows on the stationary flow distribution surface is even. For any cylinder hole window with an odd number, there is at least one oil inlet window in the counterclockwise direction and at least one oil outlet window in the clockwise direction. For any cylinder hole window with an even number, there is at least one oil outlet window in the counterclockwise direction and at least one oil inlet window in the clockwise direction.

[0025] Further, for any adjacent cylinder hole window, the central angular amplitude ϕ z = 2π / z, and for any adjacent oil inlet window center and oil outlet window center, the central angular amplitude ϕ ab = 2π / z.

[0026] Further, for at least one set of guide rails, the guide rail phase displacement angular amplitude β x = 0, and for at least one set of guide rails, the guide rail phase displacement angular amplitude β x = π / x.

[0027] Further, for the cylinder hole connected to the cylinder hole window with an odd number, its cylinder hole phase displacement angular amplitude β z = 0, and for the cylinder hole connected to the cylinder hole window with an even number, its cylinder hole phase displacement angular amplitude β z = n·π / x, where n is an odd number.

[0028] Further, at least one oil inlet window is divided into two independent oil inlet windows.

[0029] Further, at least one independent oil inlet window can be disconnected from the oil inlet channel.

[0030] Further, the on / off of at least one oil inlet window and the oil inlet channel can be controlled.

[0031] Compared with the prior art, the present invention has the following beneficial effects: Since the oil inlet window band, the oil outlet window band, the flow distribution window band, and the cylinder hole window band of the present invention coincide, the width of the flow distribution band can be effectively reduced, making the structure of the flow distributor more compact. At the same time, since there is no other flow distribution band outside the cylinder hole window band, the leakage in the width direction of the flow distribution band is reduced. Further, without increasing the width of the flow distribution band, variable displacement of the hydraulic motor / pump can be achieved. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] Figure 1 It is a schematic diagram of the flow distribution structure of the hydraulic motor of the present invention.

[0033] Figure 2 It is a schematic diagram of the shaft flow distribution structure of the hydraulic motor of the present invention.

[0034] Figure 3 It is a schematic diagram of the phase displacement of the flow distribution window and the guide rail in the present invention.

[0035] Figure 4 This is a schematic diagram of the phase displacement between the cylinder hole window and the cylinder hole in the present invention.

[0036] Figure 5 This is a schematic cross-sectional view of a ten-acting three-plunger hydraulic motor in the present invention.

[0037] Figure 6 This is a schematic diagram of the unfolded parts of a ten-acting three-plunger hydraulic motor in the present invention.

[0038] Figure 7 This is a schematic cross-sectional view of a ten-acting six-plunger hydraulic motor in the present invention.

[0039] Figure 8 This is a schematic diagram of the unfolded parts of a ten-acting six-plunger hydraulic motor in the present invention.

[0040] Figure 9 This is a schematic cross-sectional view of a ten-acting nine-plunger hydraulic motor in the present invention.

[0041] Figure 10 This is a schematic diagram of the unfolded parts of a ten-acting nine-plunger hydraulic motor in the present invention.

[0042] Figure 11 This is a schematic cross-sectional view of a ten-acting nine-plunger end-face porting hydraulic motor in the present invention.

[0043] Figure 12 This is a schematic diagram of the unfolded parts of a ten-acting nine-plunger end-face porting hydraulic motor in the present invention.

[0044] As shown in the figure: 100, cylinder block; 101, cylinder hole window; 102, inlet window; 102c, inlet window C; 102d, inlet window D; 103, outlet window; 103c, outlet window C; 103d, outlet window D; 104, cylinder hole; 105, plunger; 106, inlet passage; 106c, inlet passage C; 106d, inlet passage D; 107, outlet passage; 107c, outlet passage C; 107d, outlet passage D; 200, guide rail; 200a, guide rail A; 200b, guide rail B; 201, outlet section; 202, inlet section; 300, flow distributor; 301, porting window; 400, porting band. Detailed Embodiment

[0045] The following further describes the embodiments and examples of the present invention in conjunction with the accompanying drawings:

[0046] As is well known, except for the valve-type porting type, which cannot be used as a motor, the flow distributor structure of a flow-distributing plate or flow-distributing shaft type plunger pump can be changed to be used as a hydraulic motor, and the two are reversible.

[0047] Such as Figure 1The shown flow distribution structure, when used as a pump, the guide rail 200 drives the plunger 105 to translate. The oil inlet window 102 is actually the oil suction port of the pump, and the oil outlet window 103 is actually the oil pressure port of the pump. The oil is sucked in the oil inlet section 202, and then the high-pressure oil is discharged in the oil outlet section 201.

[0048] When used as a motor, the oil inlet window 102 is actually the pressure oil window, and the oil outlet window 103 is actually the oil return window. The pressure oil pushes the plunger 105 to move outward in the oil inlet section 202 to drive the guide rail 200 to rotate and output power. In the oil outlet section 201, the plunger 105 retracts and discharges the oil through the oil outlet window 103.

[0049] As Figure 1 、 Figure 2 shown, a cylinder block fixed hydraulic motor includes a stationary flow distribution surface and a rotating flow distribution surface. There are cylinder hole windows 101, an oil inlet window 102, and an oil outlet window 103 on the stationary flow distribution surface, and there is a flow distribution window 301 on the rotating flow distribution surface. The flow distribution window 301 is a groove recessed inward along the rotating flow distribution surface. On the flow distribution surface, the cylinder hole window 101 and the oil inlet window 102 or the oil outlet window 103 are communicated through the space left by the groove on the flow distribution window 301.

[0050] In the prior art, there are an oil inlet window 102 and an oil outlet window 103 outside the cylinder hole window 101. The external oil inlet window 102 sends the oil into the cylinder hole window 101 through the flow distribution window 301, and the oil in the cylinder hole window 101 discharges the oil into the external oil outlet window 103 through the flow distribution window 301.

[0051] This flow distribution belt 400 has a large width and occupies a large space.

[0052] The present invention makes the oil inlet window belt, the oil outlet window belt, the flow distribution window belt, and the cylinder hole window belt coincide, and the width of the flow distribution belt 400 is the smallest. Among them, in the present invention, the guide rail 200 and the flow distributor 300 rotate synchronously, and the number of flow distribution windows 301 on the flow distributor 300 is equal to the number of actions of the guide rail.

[0053] At any position of the guide rail 200, when the plunger 105 is in the oil outlet section 201, the cylinder hole window 101 is communicated with the oil outlet window 103 through the flow distribution window 301. When the plunger 105 is in the oil inlet section 202, the cylinder hole window 101 is communicated with the oil inlet window 102 through the flow distribution window 301.

[0054] As Figure 1 、 Figure 2As shown, points C, D, E, F, and G on the guide rail 200 are the intersection points of oil inlet and outlet. For example, point E is the end point of oil inlet and at the same time the starting point of oil outlet, which will cause the oil inlet and outlet cavities to communicate and result in internal leakage. Therefore, there should be a dead zone near these points. However, the existence of the dead zone will reduce the effective working angular range of the curve.

[0055] For the convenience of calculation and explanation, theoretically, there can be no dead zone, that is, the plunger 105 is either in the oil inlet section 202 or in the oil outlet section 201. At the same time, a cylinder hole window 101 and the connected oil inlet window 102 and oil outlet window 103 in the figure are defined as a structural unit.

[0056] According to Figure 1 , Figure 2 the schematic diagram of the structural unit, the motion analysis of a single structural unit is as follows:

[0057] As Figure 1 shown, the plunger 105 on the structural unit acts on the outer dead point E. At this time, the continuous transition of the oil inlet and outlet should satisfy:

[0058] α ab =α az +α z +α bz =α r

[0059] When the guide rail 200 rotates clockwise, the action point of the plunger 105 moves from point E to point F. The flow distribution window 301 rotates synchronously with the guide rail 200, connecting the cylinder hole window 101 and the oil outlet window 103, and the oil in the cylinder hole 104 is discharged. When it rotates to point F, the flow distribution window 301 leaves the cylinder hole window 101, disconnecting the cylinder hole window 101 and the oil outlet window 103. At this time, the next flow distribution window 301 is about to connect the oil inlet window 102 and the cylinder hole window 101. The continuous transition of the oil inlet and outlet should satisfy:

[0060] α z =α r0 =2π / r–α r

[0061] That is, when the flow distribution window 301 leaves the cylinder hole window 101, the angular position of α r0 coincides with the cylinder hole window 101.

[0062] As Figure 2 shown, the plunger 105 on the structural unit acts on the inner dead point F of the guide rail 200. Continuing to rotate clockwise, the action point of the plunger 105 moves from point F to point G. During this process, the flow distribution window 301 rotates synchronously with the guide rail 200, connecting the cylinder hole window 101 and the oil inlet window 102, and the oil enters the cylinder hole 104.

[0063] From point E to point G, the hydraulic motor completes the work of an angular stroke. Continuing to rotate, it will work continuously in a cycle.

[0064] In actual design, to prevent the direct connection between the oil inlet and outlet chambers, it can be solved by separately reducing the angular stroke of the flow distribution window 301.

[0065] As Figure 5 , Figure 6 shown, Embodiment 1 of the present invention: Application of a cylinder-fixed hydraulic motor on a ten-stroke three-plunger hydraulic motor.

[0066] A structural unit can independently meet the usage requirements of the pump. However, when used as a hydraulic motor, it cannot rotate actively at the dead zone position, and the utilization rate of the cylinder block 100 is too low. Therefore, multiple structural units can be arranged on the cylinder block 100 to improve the utilization rate of the cylinder block 100.

[0067] The structural units can be arranged arbitrarily on the cylinder block 100, but there should be no situation where the oil inlet and outlet are connected between two adjacent structural units. At this time, it should satisfy: α ab ≥α r .

[0068] For the convenience of machining and manufacturing, the structural units are generally evenly distributed on the circumference.

[0069] As in Embodiment 1, in the ideal state, the structural parameters can be selected as:

[0070] x = 10, r = 10, z = 3, α z = 12°, α r = 24°, α az = α bz = 6°, ϕ ab = π / z = 60°, ϕ z = 2π / z = 120°

[0071] Satisfy the working conditions of α az + α z + α bz = α r and α z = α r0 = 2π / r – α r .

[0072] At this time, the oil inlet window 102, the oil outlet window 103, and the cylinder hole window 101 on the stationary flow distribution surface are arranged in a cycle clockwise in the order of oil inlet window 102 – cylinder hole window 101 – oil outlet window 103 – oil inlet window 102 – cylinder hole window 101 – oil outlet window 103 – oil inlet window 102 – cylinder hole window 101 – oil outlet window 103.

[0073] Each structural unit meets the working requirements of the motor, and the motion analysis of the plunger 105 will not be described separately.

[0074] As Figure 6 shown, the plunger 105 Q1 is at the outer dead center, and the cylinder bore window 101 Z1 is not connected to either the inlet window 102 or the outlet window 103; Q2 is in the inlet section 202, and Z2 is connected to the inlet window 102 through the porting window 301, generating a force that causes the guide rail 200 to rotate clockwise; Q3 is in the outlet section 201, and Z3 is connected to the outlet window 103 through the porting window 301 to discharge the oil.

[0075] From the description of Embodiment 1, it can be seen that when the number z of the cylinder bore windows 101 increases, α a and α b will become smaller and smaller, which limits the increase in the number of cylinder bore windows 101.

[0076] To continue increasing the number of cylinder bore windows 101, a cylinder bore window 101 can be added between two adjacent structural units. This cylinder bore window 101 borrows the outlet window 103 and the inlet window 102 on the adjacent structural units respectively to form a reverse structural unit. That is, in the rotational direction, the positions of the inlet window 102 and the outlet window 103 are swapped compared with the structural unit.

[0077] The reverse structural unit causes the plunger 105 on the newly added cylinder bore window 101 to work out of adjustment, generating a force that prevents the motor from rotating and affecting the normal operation of the motor. To make the reverse structural unit meet the working requirements, the phase displacement amplitude angle β x ( Figure 3 shown) and the cylinder bore phase displacement amplitude angle β z ( Figure 4 shown) can be changed, or the amplitude angles of both can be changed simultaneously to meet the working requirements.

[0078] As Figure 7 , Figure 8 shown, Embodiment 2 of the present invention is: an application of a cylinder block fixed hydraulic motor on a ten - action six - plunger hydraulic motor.

[0079] After adding the reverse structural unit, to achieve the working requirements, Embodiment 2 realizes it by changing the phase displacement amplitude angle β x of the guide rail.

[0080] The structural parameters are as follows:

[0081] x = 10, r = 10, z = 6, α z = 12°, α r = 24°, α az = α bz = 6°, α a = αb = 36°, φ ab = 2π / z = 60°, φ z = 2π / z = 60°.

[0082] Satisfy α az + α z + α bz = α r and α z = α r0 = 2π / r – α r working conditions.

[0083] The guide rail phase displacement amplitude angle β of the guide rail A 200a x = 0.

[0084] The guide rail phase displacement amplitude angle β of the guide rail B 200b x = π / x = 18°.

[0085] The cylinder bore 104 communicating with the cylinder bore windows 101 with odd numbers (Z1, Z3, Z5), and the plungers 105 (Q1, Q3, Q5) inside act on the guide rail A 200a; the cylinder bore 104 communicating with the cylinder bore windows 101 with even numbers (Z2, Z4, Z6), and the plungers 105 (Q2, Q4, Q6) inside act on the guide rail B 200b.

[0086] At this time, the oil inlet window 102, the oil outlet window 103 and the cylinder bore window 101 on the stationary port plate are arranged in a clockwise cycle in the order of oil inlet window 102 – cylinder bore window 101 – oil outlet window 103 – cylinder bore window 101 – oil inlet window 102 – cylinder bore window 101 – oil outlet window 103 – cylinder bore window 101 – oil inlet window 102 – cylinder bore window 101 – oil outlet window 103 – cylinder bore window 101.

[0087] The cylinder bore windows 101 with odd numbers are structural units that meet the working requirements, and the cylinder bore windows 101 with even numbers are reverse structural units.

[0088] For the reverse structural unit, the oil outlet window 103 is in the counterclockwise direction of the cylinder bore window 101, and the oil inlet window 102 is in the clockwise direction. If it acts on the guide rail A 200a with β x = 0, a force that hinders the rotation of the motor will be generated, causing the motor to not work properly. Because the acting sections of the guide rail B 200b and the guide rail A 200a are exactly opposite, the phase of the plunger 105 on the reverse structural unit is corrected after acting on the guide rail B 200b, so that the plunger 105 communicating with the reverse structural unit acts on the correct guide rail section, enabling the motor to work properly.

[0089] Such as Figure 8As shown, the plunger 105 Q1 is located at the outer dead center of the guide rail A 200a, and the cylinder bore window 101 Z1 is not connected to both the inlet window 102 and the outlet window 103; Q2 is located in the inlet section 202 of the guide rail B 200b, and Z2 is connected to the inlet window 102 through the porting window 301, generating a force that causes the guide rail to rotate clockwise; Q3 is located in the inlet section 202 of the guide rail A 200a, and Z3 is connected to the inlet window 102 through the porting window 301, generating a force that causes the guide rail to rotate clockwise; Q4 is located at the inner dead center of the guide rail B 200b, and the cylinder bore window 101 Z4 is not connected to both the inlet window 102 and the outlet window 103; Q5 is located in the outlet section 201 of the guide rail A 200a, and Z5 is connected to the outlet window 103 through the porting window 301 to discharge the oil; Q6 is located in the outlet section 201 of the guide rail B 200b, and Z6 is connected to the outlet window 103 through the porting window 301 to discharge the oil.

[0090] It can be concluded from the above that the second embodiment 2 meets the working requirements.

[0091] As Figure 9 、 Figure 10 shown, the third embodiment of the present invention is: an application of a cylinder block fixed hydraulic motor on a nine-plunger hydraulic motor with ten actions.

[0092] The second embodiment can increase the utilization rate of the cylinder block 100, but since the plunger 105 is distributed on at least two working surfaces, the thickness of the hydraulic motor is increased.

[0093] In order to increase the number of plungers 105 without increasing the thickness of the motor, the angular displacement amplitude β of the cylinder bore phase of the reverse structure unit can also be changed z to make the plunger 105 in the correct guide rail section.

[0094] In the second embodiment, the included angle between the outer dead center and the inner dead center is n·π / x, where n is an odd number, and the guide rail 200 has a period of 2π / x. Therefore, there is only one included angle of π / x. If the acting guide rail of the reverse structure unit remains unchanged, the angular displacement amplitude of the cylinder bore

[0095] β z = n·π / x, where n is an odd number, can be used to make the plunger 105 in the cylinder bore 104 of the reverse structure unit act on the correct guide rail section.

[0096] In the third embodiment, the problem of the acting section of the reverse structure unit is realized by changing the angular displacement amplitude β of the cylinder bore z =π / x = 18°.

[0097] The structural parameters are as follows:

[0098] x = 10, r = 10, z = 9, α z= 12°, α r = 24°, α az = α bz = 6°, α ac = α ad = 12°, α b = 36°, ϕ z = 60°.

[0099] Meet α az + α z + α bz = α r And α z = α r0 = 2π / r – α r Working conditions.

[0100] The oil inlet window 102 is divided into two independent oil inlet windows C 102c and oil inlet window D 102d in the clockwise direction. Among them, the oil inlet window C 102c is communicated with the oil inlet passage C 106c, and the oil inlet window D 102d is communicated with the oil inlet passage D 106d.

[0101] At this time, the oil inlet window 102, the oil outlet window 103, and the cylinder hole window 101 on the stationary flow distribution surface are arranged in a cycle in the clockwise direction according to the order of oil inlet window C 102c - oil inlet window D 102d – cylinder hole window 101 – oil outlet window 103 – cylinder hole window 101 – oil inlet window C 102c - oil inlet window D 102d – cylinder hole window 101 – oil outlet window 103 – cylinder hole window 101 – oil inlet window C 102c - oil inlet window D 102d – cylinder hole window 101 – oil outlet window 103 – cylinder hole window 101.

[0102] The cylinder hole windows 101 with odd numbers (Z1, Z3, Z5) are each connected to a plunger 105; the cylinder hole windows 101 with even numbers (Z2, Z4, Z6) are each connected to two plungers 105, and the phase displacement amplitude angle β of these two cylinder holes 104 from the center of the cylinder hole window 101 z = π / x = 18°; among them, the oil inlet window C 102c is adjacent to the cylinder hole window 101 with an even number, and the oil inlet window D 102d is adjacent to the cylinder hole window 101 with an odd number.

[0103] In Embodiment 2, each oil inlet window 102 can supply liquid to two adjacent cylinder hole windows 101 in the clockwise and counterclockwise directions.

[0104] In Embodiment 3, the oil inlet window C 102c supplies liquid to the cylinder hole window 101 with an even number, and the oil inlet window D 102d supplies liquid to the cylinder hole window 101 with an odd number.

[0105] Such as Figure 10As shown, the plunger 105 Q1 is located at the outer dead center of the guide rail 200, and the cylinder bore window 101 Z1 is not connected to the inlet window 102 or the outlet window 103; Q2 and Q3 are located in the inlet section 202 of the guide rail 200, and Z2 is connected to the inlet window C 102c through the porting window 301, generating a force that causes the guide rail 200 to rotate clockwise; Q4 is located in the inlet section 202 of the guide rail 200, and Z3 is connected to the inlet window D 102d through the porting window 301, generating a force that causes the guide rail 200 to rotate clockwise; Q5 and Q6 are located at the inner dead center of the guide rail 200, and the cylinder bore window 101 Z4 is not connected to the inlet window 102 or the outlet window 103; Q7 is located in the outlet section 201 of the guide rail 200, and Z5 is connected to the outlet window 103 through the porting window 301 to discharge the oil; Q8 and Q9 are located in the outlet section 201 of the guide rail 200, and Z6 is connected to the outlet window 103 through the porting window 301 to discharge the oil.

[0106] From the above, it can be concluded that the present Embodiment 3 meets the working requirements.

[0107] Connect the inlet window C 102c to the pressure oil pipeline A1 and the inlet window D 102d to the pressure oil pipeline A2. If the displacement of each plunger 105 is V:

[0108] If both A1 and A2 are connected to the pressure oil, the displacement of the motor is 9V (Q1~Q9).

[0109] If A1 is connected to the pressure oil and A2 is not connected to the pressure oil, the displacement of the motor is 6V (Q2, Q3, Q5, Q6, Q8, Q9).

[0110] If A2 is connected to the pressure oil and A1 is not connected to the pressure oil, the displacement of the motor is 3V (Q1, Q4, Q7).

[0111] Therefore, by disconnecting the connection of a part of the independent inlet window 102 to the pressure oil, the displacement of the motor can be changed.

[0112] As Figure 11 、 Figure 12 shown, Embodiment 4 of the present invention is: an application of a cylinder block fixed hydraulic motor on a nine-plunger end-face porting hydraulic motor with ten actions.

[0113] Embodiment 3 can achieve a change in displacement when the motor rotates clockwise. When rotating counterclockwise, the original inlet window 102 becomes the outlet window 103, and the original outlet window 103 becomes the inlet window 102. As can be seen from Figure 9, when rotating counterclockwise, the number of inlet windows 102 becomes three. Although the displacement can be changed in this way, it cannot change the displacement as it does during forward rotation.

[0114] In order to enable the displacement to be changed in the same way when the motor rotates forward and backward, both the oil inlet window 102 and the oil outlet window 103 are designed as two independent windows.

[0115] The structural parameters are as follows:

[0116] x = 10, r = 10, z = 9, α z = 12°, α r = 24°, α az = α bz = 6°, α ac = α ad = 12°, α bc = α bd = 12°, ϕ z = 60°.

[0117] Meet the working conditions of α az + α z + α bz = α r and α z = α r0 = 2π / r – α r .

[0118] The oil inlet window 102 is divided into two independent oil inlet windows C 102c and D 102d in the clockwise direction. Among them, the oil inlet window C 102c is communicated with the oil inlet passage C 106c, and the oil inlet window D 102d is communicated with the oil inlet passage D 106d. The oil outlet window 103 is divided into two independent oil outlet windows C 103c and D 103d in the clockwise direction. Among them, the oil outlet window C 103c is communicated with the oil outlet passage C 107c, and the oil outlet window D 103d is communicated with the oil outlet passage D 107d.

[0119] At this time, on the static flow distribution surface, the oil inlet window 102, the oil outlet window 103 and the cylinder hole window 101 are arranged in a cycle in the clockwise direction according to the order of oil inlet window C 102c - oil inlet window D 102d – cylinder hole window 101 – oil outlet window C 103c – oil outlet window D 103d – cylinder hole window 101 – oil inlet window C 102c - oil inlet window D 102d – cylinder hole window 101 – oil outlet window C 103c – oil outlet window D 103d – cylinder hole window 101 – oil inlet window C 102c - oil inlet window D 102d – cylinder hole window 101 – oil outlet window C 103c – oil outlet window D 103d – cylinder hole window 101.

[0120] The structure of Embodiment 4 is similar to that of Embodiment 3. When rotating in the reverse direction, the curved surface sections acting during forward rotation also change due to the change of the oil inlet and outlet window 103.

[0121] Such as Figures 5 to 12For any of the hydraulic motors therein, when any one of the oil inlet windows 102 and the oil inlet passage 106 is disconnected, there will be no liquid flowing into the corresponding cylinder bore window 101, which will reduce the displacement of the motor. For example, Figure 5 in Figure 5 , when the oil inlet window 102 in the counterclockwise direction of Z1 is disconnected from the oil inlet passage 106, Z1 no longer participates in the operation and the displacement of the motor decreases.

[0122] The present invention is not limited to the above specific embodiments. Those skilled in the art can make various transformations starting from the above structure without creative labor, and all of them fall within the protection scope of the present invention.

Claims

1. A cylinder block fixed hydraulic motor, comprising: Stationary flow distribution surface, on which there are cylinder hole windows, oil inlet windows and oil outlet windows; Rotating flow distribution surface, on which there are flow distribution windows, and the flow distribution windows are grooves recessed inward along the rotating flow distribution surface. It is characterized in that the oil inlet window band, the oil outlet window band, the flow distribution window band and the cylinder hole window band coincide.

2. The cylinder block fixed hydraulic motor according to claim 1, wherein, The number of flow distribution windows is equal to the number of guide rail actions. At any position of the guide rail, when the plunger is in the oil outlet section, the cylinder hole window is communicated with the oil outlet window through the flow distribution window; when the plunger is in the oil inlet section, the cylinder hole window is communicated with the oil inlet window through the flow distribution window.

3. The cylinder block fixed hydraulic motor according to claim 1, wherein, There is at least one oil inlet window in the counterclockwise direction of any cylinder hole window and at least one oil outlet window in the clockwise direction.

4. The cylinder block fixed hydraulic motor according to claim 1, wherein, The number of cylinder hole windows on the stationary flow distribution surface is even. For any cylinder hole window numbered odd, there is at least one oil inlet window in the counterclockwise direction and at least one oil outlet window in the clockwise direction; for any cylinder hole window numbered even, there is at least one oil outlet window in the counterclockwise direction and at least one oil inlet window in the clockwise direction.

5. The cylinder block fixed hydraulic motor according to claim 4, wherein, The angular amplitude of the center of any adjacent cylinder hole window ϕz = 2π / z, and the angular amplitude of the center of any adjacent oil inlet window and oil outlet window ϕab = 2π / z.

6. The cylinder block fixed hydraulic motor according to any one of claims 1 or 4, wherein, The angular displacement amplitude of the guide rail phase of at least one group of guide rails βx = 0, and the angular displacement amplitude of the guide rail phase of at least one group of guide rails βx = π / x.

7. The cylinder block fixed hydraulic motor according to any one of claims 1 or 4, wherein, For the cylinder connected to the cylinder hole window numbered odd, the angular displacement amplitude of the cylinder hole phase βz = 0; for the cylinder connected to the cylinder hole window numbered even, the angular displacement amplitude of the cylinder hole phase βz = n·π / x, where n is odd.

8. The cylinder block fixed hydraulic motor according to claim 4, wherein, At least one oil inlet window is divided into two independent oil inlet windows.

9. The cylinder block fixed hydraulic motor according to claim 8, wherein, It is possible to disconnect at least one independent oil inlet window from the oil inlet channel.

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