Radial plunger type hydraulic motor and working machine

Abstract

The utility model provides a radial plunger type hydraulic motor and a working machine with the same. The radial plunger type hydraulic motor comprises a cylinder body, a distributor and a wave spring. The cylinder body is provided with a plurality of plunger holes and a plurality of cylinder body communication ports communicated with the plunger holes respectively. A plurality of distributor communicating ports are formed in the front end face of the distributor, and the communicating relation between the distributor communicating ports and the cylinder body communicating ports is changed through relative rotation of the distributor and the cylinder body. The wave spring is located behind the dispenser and pushes the dispenser toward the cylinder. The use of the wave spring helps to reduce the manufacturing cost of the radial plunger type hydraulic motor without increasing the axial dimension of the radial plunger type hydraulic motor and without degrading the performance of the radial plunger type hydraulic motor.

Description

Technical Field

[0001] The present disclosure relates to the field of hydraulic technology, and in particular, to a radial piston hydraulic motor and a working machine having the same. Background Art

[0002] A hydraulic motor is a device that can convert liquid pressure energy into mechanical energy. Compared with other types of hydraulic motors, such as axial piston hydraulic motors, radial piston hydraulic motors are usually smaller in the axial direction. Therefore, radial piston hydraulic motors are often used in applications where the axial assembly space is relatively compact. Like other industrial products, there is always a need to improve the manufacturing cost of radial piston hydraulic motors. Utility Model Content

[0003] In view of this, the present disclosure improves the structure of the radial piston hydraulic motor, aiming to help reduce the manufacturing cost of the radial piston hydraulic motor.

[0004] On the one hand, the present disclosure provides a radial piston hydraulic motor, which includes a cylinder body, a distributor and a wave spring. The cylinder body is provided with a plurality of plunger holes and a plurality of cylinder body communication ports respectively connected to the plurality of plunger holes. The front end surface of the distributor is provided with a plurality of distributor communication ports. The relative rotation of the distributor and the cylinder body changes the connection relationship between the plurality of distributor communication ports and the plurality of cylinder body communication ports. The wave spring is located behind the distributor and pushes the distributor toward the cylinder body.

[0005] Compared with the method of opening multiple holes on the distributor to install multiple cylindrical springs, the method of using a wave spring to push the distributor to the cylinder body can reduce the number of components, avoid machining multiple holes, and simplify the assembly steps, thereby helping to reduce manufacturing costs. At the same time, the use of a wave spring will not increase the axial size of the radial piston hydraulic motor and will not deteriorate the performance of the radial piston hydraulic motor.

[0006] In a possible implementation, the radial piston hydraulic motor further includes a housing for accommodating a distributor and a wave spring, wherein the housing is provided with a support surface located behind the distributor, and the wave spring is located between the distributor and the support surface and is elastically deformed by being squeezed by the two.

[0007] The rear side of the wave spring presses against the supporting surface of the housing, and the front side presses against the rear end face of the distributor, and elastic deformation occurs under the extrusion of the two to obtain elastic restoring force. This elastic restoring force pushes the distributor toward the cylinder body, so that the front end face of the distributor is pressed tightly against the rear end face of the cylinder body.

[0008] In a possible implementation, the rear end of the distributor is provided with a first surface and a second surface offset in the axial direction, the wave spring abuts against the first surface, and the second surface is raised relative to the first surface to limit the height of the wave spring after compression.

[0009] After the assembly process is completed, since the second surface is raised relative to the first surface, the supporting surface of the housing will contact the raised second surface, so that a gap with a preset width is formed between the supporting surface and the first surface, and the width is the distance between the two surfaces. The wave spring is placed in the gap and is appropriately pressed. Since the width of the gap is controllable, the degree of compression of the wave spring will also be controllable, which helps to avoid over-extrusion or under-extrusion of the wave spring.

[0010] In a possible implementation, the radial piston hydraulic motor further includes a pin, a pin hole is provided at the rear end of the distributor, the pin extends into the pin hole to prevent the distributor from rotating relative to the housing, and the pin hole is at least partially opened on the second surface.

[0011] Since the wave spring is located between the first surface and the supporting surface of the shell, the pin hole is provided on the second surface so as to prevent the distributor from rotating relative to the shell and avoid the wave spring.

[0012] In a possible implementation manner, the first surface is located radially outside the second surface.

[0013] Thus, during the assembly process, the cylindrical surface between the first surface and the second surface can help the wave spring to be positioned quickly and accurately.

[0014] In one possible implementation, the shell is provided with an oil inlet and an oil return port, the inner periphery of the shell is provided with at least two inner ring grooves respectively connected to the oil inlet and the oil return port, the outer periphery of the distributor is provided with at least two outer ring grooves respectively facing and connected to the at least two inner ring grooves, and the outer ring grooves are connected to the distributor connecting port.

[0015] In this way, the connection between the multiple distributor connecting ports and the oil inlet and oil return ports is established.

[0016] In a possible implementation, the radial piston hydraulic motor further includes a housing for accommodating the cylinder body, a cam guide surface is provided on the inner periphery of the housing, a plunger is provided in the cylinder body, and the plunger moves radially reciprocatingly under the guidance of the cam guide surface.

[0017] In this way, the pressure energy of the fluid can be converted into mechanical energy in the form of torque.

[0018] In a possible implementation, the cylinder body is configured to be drivingly coupled to an external device to output torque to the external device.

[0019] In this way, torque output can be achieved.

[0020] In one possible implementation, the outer diameter D of the wave spring ranges from 100 mm to 140 mm, and / or the inner diameter d of the wave spring ranges from 80 mm to 120 mm, and / or the thickness T of the wave spring ranges from 0.5 mm to 3 mm, and / or the height H of the wave spring ranges from 2 mm to 5 mm, and / or the wave number WN of the wave spring ranges from 5 to 15.

[0021] The wave spring with such a structure can provide sufficient pressing force to press the front end surface of the distributor against the rear end surface of the cylinder body well without increasing the axial size of the radial piston hydraulic motor.

[0022] On the other hand, the present disclosure further provides a working machine, which includes the radial piston hydraulic motor mentioned in the above aspect. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] In order to more clearly illustrate the technical solutions of the embodiments of the present disclosure, the drawings required for use in the embodiments are briefly introduced below.

[0024] It should be understood that the following drawings only illustrate some, but not all, embodiments of the present disclosure.

[0025] It should be understood that the same or similar reference numerals are used to indicate the same or similar elements.

[0026] It should be understood that the drawings are merely schematic and that the sizes and proportions of elements in the drawings are not necessarily accurate.

[0027] Figure 1 It is a schematic structural diagram of a radial piston hydraulic motor according to an embodiment of the present disclosure.

[0028] Figure 2 for Figure 1 Longitudinal cross-sectional view of a radial piston hydraulic motor.

[0029] Figure 3 for Figure 2 Schematic diagram of the exploded view of the cylinder body of the radial piston hydraulic motor.

[0030] Figure 4 for Figure 2 Schematic diagram of the structure of the distributor of the radial piston hydraulic motor.

[0031] Figure 5 for Figure 2 Schematic diagram of the structure of the distributor and pin of the radial piston hydraulic motor.

[0032] Figure 6 for Figure 2 A partial enlarged view of part B.

[0033] Figure 7 for Figure 2 A partial enlarged view of part C.

[0034] Figure 8 for Figure 2 A partial enlarged view of part D.

[0035] Fig. 9 for Figure 2 Schematic diagram of the structure of the wave spring.

[0036] Fig.10 for Fig. 9 Side view of the wave spring.

[0037] Fig.11 It is a schematic structural diagram of a working machine according to an embodiment of the present disclosure. DETAILED DESCRIPTION

[0038] The following is an exemplary description of the embodiments of the present disclosure in conjunction with the accompanying drawings. It should be understood that the present disclosure can be implemented in a variety of ways and should not be construed as being limited to the embodiments described here. The embodiments described here are only for a more thorough and clear understanding of the present disclosure.

[0039] Exemplary Hydraulic Motors

[0040] refer to Figure 1 The present disclosure provides a radial piston hydraulic motor 100, hereinafter referred to as the hydraulic motor 100. The hydraulic motor 100 may include a housing 10, and the housing 10 may be provided with a plurality of oil ports 11, and the plurality of oil ports 11 may include an oil inlet 11a and an oil return port 11b. The pressurized fluid may flow into the hydraulic motor 100 through the oil inlet 11a, and the depressurized fluid that loses hydraulic energy may be discharged from the hydraulic motor 100 through the oil return port 11b.

[0041] The housing 10 may be composed of a front housing 12 and a rear housing 13 assembled together. For example, a plurality of oil ports 11 may be provided on the rear housing 13. For example, the front housing 12 and the rear housing 13 may be fastened together by a plurality of bolts. Of course, in some embodiments, the housing 10 may be integrally formed, or the housing 10 may be composed of more housing parts assembled together.

[0042] refer to Figure 1 The housing 10 may further include an end cover 20, which may be disposed on the rear side of the rear housing 13 and fixed to the rear housing 13. For example, the end cover 20 may be fastened to the rear housing 13 by a plurality of bolts. The housing 10 may further include a front end cover 21, which closes the front end of the front housing 12. The front housing 12, the rear housing 13, the end cover 20 and the front end cover 21 cooperate to form an inner cavity, and some components of the hydraulic motor 100 are accommodated in the inner cavity. Figure 2 As shown, these components may include a cylinder 30 , a distributor 40 , a brake assembly 50 , and a shaft 60 .

[0043] refer to Figure 2 The cylinder body 30 is accommodated in the housing 10 so as to be rotatable relative to the housing 10 about the axis AA. Figure 3 The cylinder body 30 may be provided with a plurality of plunger holes 31, and a plurality of plungers 32 are respectively disposed in the plurality of plunger holes 31 in a radially movable manner, and each plunger 32 may include a plunger body 321 and a roller 322. Figure 3 The cylinder body 30 may also be provided with a plurality of cylinder body communication ports 33 , and the plurality of cylinder body communication ports 33 are provided on the rear end surface 301 of the cylinder body, and each cylinder body communication port 33 is connected to a corresponding plunger hole 31 .

[0044] Continue to refer Figure 2 The inner circumference of the housing 10 (ie, the front housing 12) may be provided with a cam guide surface 121, and the plurality of plungers 32 move radially reciprocatingly under the guidance of the cam guide surface 121. Specifically, the rollers 322 abut against the guide surface 121 at the radial outer side.

[0045] Continue to refer Figure 2 In order to rotatably support the cylinder body 30 on the housing 10, the hydraulic motor 100 may further include a pair of tapered roller bearings 71. The pair of tapered roller bearings 71 are sleeved on the cylinder body 30 and are located on opposite sides of the plurality of plunger holes 31 in the axial direction. Through the shoulder on the outer periphery of the cylinder body 30 and the shoulder on the inner periphery of the housing 10, the pair of tapered roller bearings 71 fix the cylinder body to the housing 10 in the axial direction and allow the cylinder body 30 to rotate relative to the housing 10 around the axis AA.

[0046] refer to Figures 2 to 4, the hydraulic motor 100 may further include a distributor 40. The distributor 40 is located behind the cylinder body 30, and a plurality of distributor communication ports 43 are provided on the front end face 401 of the distributor. The front end face 401 of the distributor is pressed against the rear end face 301 of the cylinder body to establish a communication relationship between the plurality of distributor communication ports 43 and the plurality of cylinder communication ports 33. The relative rotation of the distributor 40 and the cylinder body 30 can change the communication relationship between the plurality of distributor communication ports 43 and the plurality of cylinder communication ports 33. For example, before the relative rotation of the distributor 40 and the cylinder body 30 occurs, a certain distributor communication port 43 is opposite to a certain cylinder communication port 33 to communicate with each other; after the relative rotation occurs, the distributor communication port 43 turns to be opposite to another cylinder communication port 33 to communicate with each other. As the relative rotation continues, the communication relationship between the plurality of distributor communication ports 43 and the plurality of cylinder communication ports 33 changes continuously. It can be understood that in most cases, the distributor 40 is stationary and the cylinder 30 rotates relative to the distributor 40, but the cylinder 30 can also be set to be stationary and the distributor 40 rotates. The "relative rotation" of the present invention is intended to cover these two situations.

[0047] refer to Figure 6 The inner circumference of the housing 10 may be provided with at least two inner ring grooves 131 respectively connected to the oil inlet 11a and the oil return port 11b, a part of the inner ring groove 131 is connected to the oil inlet 11a, and another part of the inner ring groove 131 is connected to the oil return port 11b. The outer circumference of the distributor 40 is provided with at least two outer ring grooves 45 respectively facing and connected to the at least two inner ring grooves 131, and each inner ring groove 131 and a corresponding outer ring groove 45 together form an annular flow channel. Figure 4 , a part of the outer ring groove 45 is connected to a part of the distributor communication port 43, and another part of the outer ring groove 45 is connected to another part of the distributor communication port 43. In this way, the connection between the multiple distributor communication ports 43 and the oil inlet 11a and the oil return port 11b is established. It can be understood that for some hydraulic motors, more inner ring grooves 131 and outer ring grooves 45 can also be set, such as four inner ring grooves 131 and four outer ring grooves 45, to form four groups of annular flow channels, two of which are connected to the oil inlet 11a, and two of which are connected to the oil outlet 11b.

[0048] Furthermore, since the multiple distributor communication ports 43 are respectively connected to the multiple cylinder communication ports 33, and each cylinder communication port 33 is connected to a corresponding plunger hole 31, as the cylinder 30 rotates relative to the distributor 40, the connection relationship between the multiple distributor communication ports 43 and the multiple cylinder communication ports 33 changes periodically, that is, the connection relationship between the multiple plunger holes 31 and the oil inlet port 11a and the oil return port 11b changes periodically.

[0049] Specifically, some plunger holes 31 are connected to the oil inlet 11a. Under the action of the fluid, the plungers 32 located in these plunger holes 31 move radially outward. Due to the special shape of the guide surface 121, such as a cam shape, the cooperation between these plungers 32 moving radially outward and the guide surface 121 can obtain torque, thereby converting the liquid pressure energy of the pressurized fluid into mechanical energy.

[0050] Other plunger holes 31 are connected to the oil return port 11b. As the cylinder body 30 and the housing 10 rotate relative to each other, the plungers 32 located in these plunger holes 31 are pressed and moved radially inward under the action of the guide surface 121, so that the fluid in these plunger holes 31 is discharged through the oil return port 11b. At the same time, as the cylinder body 30 and the housing 10 continue to rotate relative to each other, the connection relationship between the multiple plunger holes 31 and the oil inlet port 11a and the oil return port 11b changes periodically to continuously obtain torque.

[0051] In the process of obtaining torque, one of the cylinder body 30 and the housing 10 can be a rotating part and the other can be a non-rotating part. For example, in the current example, the cylinder body 30 is a rotating part and the housing 10 is a non-rotating part. In particular, in the current example, the cylinder body 30 can be a torque output part, that is, the cylinder body 30 can be directly connected to an external device to transmit torque to the external device. Of course, in other examples of the present disclosure, the hydraulic motor 100 can also include another component connected to the cylinder body 30, such as a shaft 60, which can be used as a torque output part. In this case, a portion of the shaft 60 can extend outside the housing 10. Of course, in some embodiments, the hydraulic motor 100 can output torque through other parts, for example, through a portion of the housing 10.

[0052] In order to press the front end face 401 of the distributor well onto the rear end face 301 of the cylinder body, a pressing force needs to be provided. In the related art, the pressing force is provided by a plurality of cylindrical springs spaced apart along the circumferential direction. The distributor in the related art is provided with a plurality of mounting holes open to the rear and spaced apart along the circumferential direction, and a plurality of cylindrical springs are respectively placed in the plurality of mounting holes to reduce the occupation of the axial space. This method of providing the pressing force by a plurality of cylindrical springs is widely accepted in the related art and is even considered to be irreplaceable, because this method can provide sufficient pressing force, the pressing force is more evenly distributed in the circumferential direction, and the occupied axial space is small.

[0053] When faced with the technical problem of how to reduce the manufacturing cost of radial piston hydraulic motors, the inventor creatively discovered that changing the way the clamping force between the distributor and the cylinder body is provided can help reduce the manufacturing cost of radial piston hydraulic motors. On the one hand, in the methods provided in the relevant field, the number of cylindrical springs is large, which leads to a higher cost of parts. On the other hand, in order to reduce the axial space occupied, the distributor needs to have multiple mounting holes, which increases the processing cost. On the other hand, the process of installing multiple springs into multiple mounting holes is relatively complicated, which increases the difficulty of the assembly process and thus increases the manufacturing cost.

[0054] It is not enough to simply realize that changing the way of providing the clamping force can help reduce manufacturing costs, because the way of providing the clamping force in the related art can meet the various requirements mentioned above, and it is difficult to provide a new way of providing the clamping force that can both reduce costs and meet the various requirements mentioned above. The inventor has overcome this difficulty and creatively proposed a new way of providing the clamping force, which is described below with an example.

[0055] refer to Figure 2 and Fig. 9 In the present disclosure, the hydraulic motor 100 may further include a wave spring 80. Figure 3 and Figure 4 , the wave spring 80 is located behind the distributor 40 and pushes the distributor 40 toward the cylinder 30 so that the front end face 401 of the distributor is pressed against the rear end face 301 of the cylinder. That is, in the present disclosure, the pressing force that presses the front end face 401 of the distributor against the rear end face 301 of the cylinder is provided by the wave spring 80.

[0056] Compared with the method of opening multiple holes on the distributor to install multiple cylindrical springs, the method of using a wave spring 80 to push the distributor 40 to the cylinder body can reduce the number of components, avoid processing multiple holes, and simplify the assembly steps, thereby helping to reduce manufacturing costs. At the same time, the wave spring 80 itself is annular, so the compression force it provides is distributed more evenly in the circumferential direction. In addition, the size of the compression force provided by the wave spring 80 can be changed by configuring its number of waves, without necessarily relying on a large height and inner and outer diameter difference. In other words, the wave spring 80 can ensure that it can provide sufficient compression force by setting more waves without having a large height or inner and outer diameter difference, which makes the use of the wave spring 80 not, or at least not significantly, increase the required installation space, especially the axial space. It can be seen that the use of the wave spring 80 can help reduce the manufacturing cost of the radial piston hydraulic motor 100, while not increasing the axial size of the radial piston hydraulic motor 100, and not degrading the performance of the radial piston hydraulic motor 100.

[0057] refer to Figure 2 and Figure 7 The housing 10, namely the rear housing 13, accommodates the distributor 40 and the wave spring 80, and is provided with a support surface 132 located behind the distributor 40. The wave spring 80 is located between the distributor 40 and the support surface 132 and is elastically deformed by being squeezed by the two.

[0058] During assembly, the rear side of the wave spring 80 presses against the support surface 132 of the rear housing 13, and the front side thereof presses against the rear end surface (specifically the first surface 41, see the following description) of the distributor 40, and elastically deforms under the pressure of the two to obtain elastic restoring force. The elastic restoring force pushes the distributor 40 toward the cylinder 30, so that the front end surface 401 of the distributor is pressed against the rear end surface 301 of the cylinder.

[0059] Continue to refer Figure 7 , the rear end of the distributor 40 may be provided with a first surface 41 and a second surface 42 staggered in the axial direction, the wave spring 80 abuts against the first surface 41, and the second surface 42 protrudes relative to the first surface 41 to limit the height of the wave spring 80 after compression. After the assembly process is completed, since the second surface 42 protrudes relative to the first surface 41, the support surface 132 of the housing 10 will contact the protruding second surface 42, so that a gap with a preset width is formed between the support surface 132 and the first surface 41, and the width is the distance between the two surfaces. The wave spring 80 is placed in the gap and is appropriately pressed. Since the width of the gap is controllable, the degree of compression of the wave spring 80 will also be controllable, which helps to avoid excessive or insufficient compression of the wave spring 80.

[0060] refer to Figure 2 and Figure 5 In order to fix the distributor 40 to the housing 10 in the axial direction, the hydraulic motor 100 further includes a pin 81. A pin hole 44 is provided at the rear end of the distributor 40. The pin 81 extends into the pin hole 44 to prevent the distributor 40 from rotating relative to the housing 10. The pin hole 44 is at least partially opened on the second surface 42. Figure 7 Since the wave spring 80 is located between the first surface 41 and the support surface 132 of the housing 10 , the pin hole 44 is provided on the second surface 42 to prevent the distributor 40 from rotating relative to the housing and to avoid the wave spring 80 .

[0061] refer to Figure 7 , the first surface 41 is radially located outside the second surface 42. In this way, during the assembly process, the cylindrical surface between the first surface 41 and the second surface 42 can help the wave spring 80 to be positioned quickly and accurately. On the other hand, this can make the size of the wave spring 80 as large as possible, thereby providing a greater pressing force.

[0062] refer to Fig. 9The wave spring 80 is annular and has an inner circular shape and an outer circular shape. In addition, the surface of the wave spring 80 has a wavy structure, and these waves can increase the softness and flexibility of the spring, so that the wave spring can absorb vibration or store energy. A wave can refer to a shape from a peak to a trough and then to the next peak. The number of waves of the wave spring 80 can refer to the number of waves.

[0063] The present disclosure does not place any particular limitation on the parameters of the wave spring 80 , and a set of exemplary parameters will be given below.

[0064] For ease of understanding, before giving this set of parameters, the meaning of the common parameters of the wave spring 80 is briefly introduced. The outer diameter of the wave spring 80 may refer to the diameter of the outer circle of the spring. Fig.10 The inner diameter of the wave spring 80 may refer to the outer diameter. Fig.10 The thickness of the wave spring 80 may refer to the thickness of the wave spring material in the cross section, and the thickness is related to the stiffness and strength of the spring. Fig.10 The height of the wave spring 80 may refer to the vertical distance from the bottom to the top of the wave spring. The height is related to the working stroke and deformation range of the spring. Fig.10 The wave number of the wave spring 80 refers to the number of waves in the spring. Fig.10 It is represented by the letters WN.

[0065] This set of exemplary parameters may be: the outer diameter D of the wave spring is in the range of 100 mm to 140 mm, and / or the inner diameter d of the wave spring is in the range of 80 mm to 120 mm, and / or the thickness T of the wave spring is in the range of 0.5 mm to 3 mm, and / or the height H of the wave spring is in the range of 2 mm to 5 mm, and / or the number of waves WN of the wave spring is in the range of 5 to 15. It can be understood that although the ranges of the outer diameter D and the inner diameter d are given here, it does not mean that the width of the wave spring is limited by the two. When selecting a wave spring, it can be selected according to the outer diameter D or the inner diameter d, for example, the outer diameter D is 140 mm and the inner diameter d is 110 mm, or the inner diameter d is 80 mm and the outer diameter D is 90 mm, which are all within the numerical range of the present invention. The wave spring 80 with such a structure can provide sufficient pressing force to press the distributor front end face 401 against the cylinder rear end face 301 well without increasing the axial dimension of the radial piston hydraulic motor 100 .

[0066] In order to output torque, the cylinder 30 may be configured to be transmission-connected to an external device, so as to serve as a torque output member of the hydraulic motor 100 and output torque to the external device. Figure 2As shown, the cylinder body 30 is provided with a plurality of connection holes 301, and the front end cover 21 is provided with a plurality of front end cover through holes 211. Each front end cover through hole 211 is aligned with a corresponding first connection hole 301, so as to allow an external fastener passing through the front end cover through hole 211 and the first connection hole 301 to drivably connect the cylinder body 30 with a torque input member of an external device.

[0067] refer to Figure 2 The hydraulic motor 100 may further include a brake device 50, which is used to brake the torque output member of the hydraulic motor 100 when necessary. The brake device 50 may include a brake disc set 51. Figure 8 The brake disc set 51 may include a plurality of first brake discs 511 and a plurality of second brake discs 512. The plurality of first brake discs 511 and the plurality of second brake discs 512 may be alternately stacked in the axial direction.

[0068] The first brake disc 511 may be referred to as a dynamic disc, which may be fixed to the torque output member of the hydraulic motor 100 in the circumferential direction. The second brake disc 512 may be referred to as a static disc, which may be fixed to the non-rotating member of the hydraulic motor 100 in the circumferential direction. When the brake disc group 51 is subjected to axial pressure, the adjacent first brake disc 511 and second brake disc 512 are pressed against each other, and the torque output member is braked by the friction force therebetween. When the axial pressure on the brake disc group 51 is released, the brake is released.

[0069] The torque output member may be a cylinder 30, and the non-rotating member may be a shaft 60. In this case, the cylinder 30 may surround the brake disc set 51, and the brake disc set 51 may surround the shaft 60. In other words, the brake disc set 51 may be located between the cylinder 30 and the shaft 60. At the same time, the shaft 60 needs to be fixed to the housing 10 at least in the circumferential direction.

[0070] The inner circumference of the cylinder 30 may be provided with a cylinder spline, and the plurality of first brake discs 511 may be circumferentially fixed to the cylinder 30 via the cylinder spline. The shaft 60 may be provided with a shaft spline, and the plurality of second brake discs 512 may be circumferentially fixed to the shaft 60 via the shaft spline. The shaft 60 may also be circumferentially fixed to the housing 10 via the spline.

[0071] To apply and release the brakes, refer to Figure 2 The brake device 50 may further include a brake piston 52 and a spring 53. The spring 53 may be supported by the end cover 20 and press the brake piston 52 forward so as to press the brake disc set 51 through the brake piston 52 to brake the cylinder 30. When the cylinder 30 is required to output torque, a pressurized fluid may be introduced into the release oil chamber 521 located at the front side of the brake piston 51. Under the action of the pressurized fluid, the brake piston 52 overcomes the pressure of the spring 53 and slides backward, thereby no longer pressing the brake disc set 51, so that the brake is released and the cylinder 30 is released.

[0072] The brake piston 52 may directly press the brake disc set 51, or may indirectly press the brake disc set 51 through one or more intermediate members. Figure 2 and Figure 3 The brake device 50 may further include a plurality of brake pins 54 and gaskets 55, and the pressing force from the spring 53 may be transmitted forward to the brake disc assembly 51 through the brake piston 52, the brake pins 54 and the gaskets 55 in sequence. In particular, the hydraulic motor 100 may further include a padding member 56, which may be located between the brake disc assembly 51 and the brake ring 55 to compensate for the accumulated tolerances in manufacturing and assembly of the brake disc assembly 51. During assembly, the padding member 56 having a specific thickness may be selected according to individual differences.

[0073] In the above embodiment, the brake disc set 51 of the hydraulic motor 100 is located between the cylinder body 30 and the shaft 60, the torque output member is the cylinder body 30, and the non-rotating member is the shaft 60. It can be understood that in other examples, the brake disc set 51 of the hydraulic motor 100 can also be located between the housing 10, that is, the rear housing 13, and the shaft 60, in which case the rotating member is the shaft 60 and the non-rotating member is the housing 10.

[0074] Exemplary Work Machines

[0075] The present disclosure also provides a working machine 200. The working machine 200 may be, but is not limited to, various types of engineering machinery, mining machinery, metallurgical machinery, ship machinery, port machinery, etc. In particular, Fig.11 As shown, the working machine 200 may be a road roller 200. The working machine 200 may include the hydraulic motor 100 mentioned in the above aspect.

[0076] In the present disclosure, axial direction may refer to the extension direction of the rotation axis AA of the torque output member of the hydraulic motor, radial direction may refer to the direction on a radial plane orthogonal to the axis AA and intersecting the axis AA, circumferential direction may refer to the circumferential direction around the axis AA, the directional term "rear" may refer to the direction from the cylinder body 30 to the distributor 40 along the axis AA, and correspondingly, the directional term "front" may refer to the direction from the distributor 40 to the cylinder body 30 along the axis AA.

[0077] In the present disclosure, if a component is fixed to another component in the axial direction, it means that there will be no obvious axial relative displacement between the former and the latter. In addition, in the present disclosure, if a component is fixed to another component in the circumferential direction, it means that there will be no obvious circumferential relative displacement between the former and the latter; specifically, if the former is a torque output component, the latter will rotate with it when the former rotates; if the former is a non-rotating component, the latter is also a non-rotating component.

[0078] It should be understood that the term "including" and its variations used in the present disclosure are open inclusions, i.e., "including but not limited to". The term "according to" means "at least in part according to". The term "one embodiment" means "at least one embodiment"; the term "another embodiment" means "at least another embodiment".

[0079] It should be understood that although the terms “first” or “second” etc. may be used in the present disclosure to describe various elements, for example, a first side and a second side, these elements are not defined by these terms, and these terms are only used to distinguish one element from another.

[0080] The protection scope of the present disclosure is not limited to the above-mentioned embodiments. Any changes or substitutions that can be conceived by any person skilled in the art within the technical scope disclosed in the present disclosure should be included in the protection scope of the present disclosure. Therefore, the protection scope of the present disclosure should be based on the protection scope of the claims.

Claims

1. A radial piston hydraulic motor, characterized in that: include: A cylinder body, provided with a plurality of plunger holes and a plurality of cylinder body communication ports respectively connected with the plurality of plunger holes; A distributor, wherein a front end surface of the distributor is provided with a plurality of distributor communication ports, and the relative rotation of the distributor and the cylinder body changes the communication relationship between the plurality of distributor communication ports and the plurality of cylinder body communication ports; as well as A wave spring is located behind the distributor and pushes the distributor toward the cylinder.

2. The radial piston hydraulic motor according to claim 1, characterized in that: It also includes a shell for accommodating the distributor and the wave spring. The shell is provided with a support surface located behind the distributor. The wave spring is located between the distributor and the support surface and is elastically deformed by being squeezed by the two.

3. The radial piston hydraulic motor according to claim 2, characterized in that: The distributor rear end is provided with a first surface and a second surface staggered in the axial direction, the wave spring abuts against the first surface, and the second surface is raised relative to the first surface to limit the height of the wave spring after compression.

4. The radial piston hydraulic motor according to claim 3, characterized in that: It also includes a pin, a pin hole is provided at the rear end of the distributor, the pin extends into the pin hole to prevent the distributor from rotating relative to the shell, and the pin hole is at least partially opened on the second surface.

5. The radial piston hydraulic motor according to claim 3, characterized in that: The first surface is located radially outward of the second surface.

6. The radial piston hydraulic motor according to claim 2, characterized in that: The shell is provided with an oil inlet and an oil return port, the inner periphery of the shell is provided with at least two inner ring grooves respectively connected with the oil inlet and the oil return port, the outer periphery of the distributor is provided with at least two outer ring grooves respectively facing and connected with the at least two inner ring grooves, and the outer ring groove is connected with the distributor connecting port.

7. The radial piston hydraulic motor according to claim 1, characterized in that: It also includes a housing for accommodating the cylinder body, wherein a cam guide surface is provided on the inner periphery of the housing, and a plunger is provided in the cylinder body, and the plunger moves radially back and forth under the guidance of the cam guide surface.

8. The radial piston hydraulic motor according to claim 7, characterized in that: The cylinder body is configured to be transmission-connected to an external device so as to output torque to the external device.

9. The radial piston hydraulic motor according to any one of claims 1 to 8, characterized in that: The outer diameter D of the wave spring is in the range of 100 mm to 140 mm, and / or the inner diameter d of the wave spring is in the range of 80 mm to 120 mm, and / or the thickness T of the wave spring is in the range of 0.5 mm to 3 mm, and / or the height H of the wave spring is in the range of 2 mm to 5 mm, and / or the wave number WN of the wave spring is in the range of 5 to 15.

10. A working machine, characterized in that: It comprises a radial piston hydraulic motor according to any one of claims 1 to 9.

Images