A cycloid hydraulic motor with a braking mechanism

Abstract

The utility model relates to technical field of hydraulic system especially relates to a cycloidal hydraulic motor with brake mechanism. A cycloidal hydraulic motor with brake mechanism, include: rotation stator pair, rotation stator pair includes eccentric engagement's outer stator and inner rotor, the inner circumference of inner rotor forms and has inner taper face, brake cylinder, brake cylinder is axially sliding assembly, brake cylinder's one end near inner rotor forms and has outer taper face, when brake cylinder slides towards inner rotor, brake cylinder's outer taper face and inner taper face taper face cooperation of inner rotor with brake. Solve the technical problem of the prior art in the cycloidal hydraulic motor's brake structure complex, the big installation space, lead to the axial dimension of motor increase.

Description

TECHNICAL FIELD

[0001] The utility model relates to hydraulic system technical field especially relates to a cycloid hydraulic motor with brake mechanism. BACKGROUND

[0002] Cycloid hydraulic motor has the advantages of small size and large output torque, and is widely used in various industries. In some engineering vehicles, parking brake and service brake functions are often required. Current service brake is generally realized by hydraulic brake principle of O-type neutral function reversing valve. The main problem of this method is large parking impact and poor operation experience.

[0003] The traditional cycloid hydraulic motor braking principle is basically through the dynamic and static friction plate to brake the output shaft. For example, the application number CN202310584740.3 discloses a cycloid hydraulic motor and its braking method. The built-in brake assembly includes a friction pair, a retaining ring and a sleeve. The friction pair is sleeved on the output shaft, the outer ring of the friction pair is connected with the sleeve, and the retaining ring is located between the sleeve and the elastic member. That is, the right side of the sleeve is in contact with the piston, the left side of the sleeve is in contact with the retaining ring, and the elastic force of the elastic member can abut the left side of the sleeve with the retaining ring. A first ring groove is formed on the side of the piston close to the motor assembly, and the motor assembly has a high-pressure cavity. The first ring groove is in communication with the high-pressure cavity. It should be noted that when the high-pressure cavity of the motor assembly is connected with high-pressure oil, the high-pressure oil can reach the first ring groove through the flow channel. Under the action of high-pressure oil, the piston starts to move to the left, and the sleeve and the retaining ring also move to the left under the push of the piston. At this time, the elastic member is subjected to increased extrusion force, the compression force of the friction pair is reduced, the friction force is reduced, and the output shaft can rotate under the drive of the motor assembly. When the high-pressure cavity stops connecting with high-pressure oil, the acting force on the piston decreases, and the piston starts to move to the right. Under the action of the elastic member, the friction pair is again compressed, the friction force increases, and the output shaft stops rotating to achieve braking. The friction pair includes a plurality of steel sheets and a plurality of friction plates. The outer ring of the steel sheet is connected with the sleeve, the inner ring of the friction plate is connected with the output shaft, and the steel sheet and the friction plate are arranged at intervals. The friction plate includes a friction plate with an oil discharge groove and a friction plate without an oil discharge groove. When the cycloid hydraulic motor brakes, the hydraulic oil can be quickly discharged through the friction plate with the oil discharge groove, the friction force between the friction plate and the steel sheet increases, the friction plate without the oil discharge groove discharges oil slowly, the friction force increases slowly, and when the hydraulic oil is completely discharged, the friction force between the two types of friction plates and the steel sheet is the same. The use of two types of friction plates can make the braking torque increase smoothly. Moreover, by adjusting the proportion of the two types of friction plates, the braking speed can be controlled. The above-mentioned cycloid hydraulic motor adopts friction plates to realize the braking of the cycloid hydraulic motor. However, due to the inevitable sliding friction phenomenon, the service life of the friction plate is short, the reliability is poor, and the service brake cannot be realized at all.

[0004] In order to solve the problem of the cycloid hydraulic motor, the file with application No. CN202410013748.9 discloses a motor with brake function, which comprises a rotating stator pair, a brake ring and a piston. The rotating stator pair comprises an eccentrically engaged outer stator and an inner rotor. An annular groove is formed on the end face of the inner rotor. The brake ring is formed by at least two brake sub-rings arranged in a circle. The piston is located on the side of the brake ring away from the rotating stator pair. The piston can axially move to trigger the brake sub-ring to brake the inner rotor. When the motor works normally, the brake sub-ring does not affect the rotation of the inner rotor in the outer stator. When braking, the piston moves axially to trigger the brake sub-ring to slide radially outward, and the brake sub-ring abuts against the groove wall of the annular groove of the inner rotor, thereby playing a role in braking the inner rotor. The brake structure of the above motor adopts two semicircular brake rings to contact and brake the brake hole on the rotor in a radial direction. The brake ring contacts the piston. However, the brake ring still needs to be triggered by the axial movement of the piston, and the brake ring plays a role in braking the inner rotor. Therefore, the cooperation of the piston and the brake ring is required, the structure is complex, the installation space is large, and the axial size of the motor is increased. Practical new type content

[0005] In order to solve the technical problems of the brake structure of the existing cycloid hydraulic motor, the installation space is large, and the axial size of the motor is increased, the utility model provides a cycloid hydraulic motor with a brake mechanism, which solves the above technical problems.

[0006] In order to solve the above technical problems, the utility model provides a cycloid hydraulic motor with a brake mechanism, which comprises:

[0007] A rotating stator pair, which comprises an eccentrically engaged outer stator and an inner rotor. An inner taper surface is formed on the inner peripheral surface of the inner rotor.

[0008] A brake cylinder, which is axially slidably assembled. An outer taper surface is formed on one end of the brake cylinder close to the inner rotor. When the brake cylinder slides towards the inner rotor, the outer taper surface of the brake cylinder cooperates with the inner taper surface of the inner rotor to brake.

[0009] According to an embodiment of the utility model, the brake cylinder moves axially under the action of high-pressure oil and an elastic member.

[0010] According to an embodiment of the utility model, the elastic member provides an acting force towards the inner rotor to the brake cylinder, and the high-pressure oil acts on the brake cylinder to move against the acting force of the elastic member.

[0011] According to one embodiment of the utility model, the brake cylinder is assembled in the brake shell, the brake shell is located at one side of the rotating stator, the outer surface of brake cylinder is formed with outer protrusion which is in sliding fit with the brake shell, the inner surface of brake shell is formed with inner protrusion which is in interactive fit with the brake cylinder, brake cavity is formed between the inner protrusion and the outer protrusion.

[0012] According to one embodiment of the utility model, the relative sliding surface of the inner protrusion and the outer protrusion is kept sealed by the sealing piece.

[0013] According to one embodiment of the utility model, the brake cylinder and the brake shell are provided with anti-rotation structure.

[0014] According to one embodiment of the utility model, the anti-rotation structure includes pin shaft and guide groove, the pin shaft and the guide groove are arranged on the brake cylinder and the brake shell respectively, and the pin shaft slides into the guide groove.

[0015] According to one embodiment of the utility model, the high-pressure oil enters the brake cavity through oil channel, and a one-way valve is arranged on the oil channel.

[0016] According to one embodiment of the utility model, a damping hole is further arranged on the brake cylinder, and the elastic cavity where the elastic piece is located is in communication with the brake cavity where the high-pressure oil is located through the damping hole.

[0017] According to one embodiment of the utility model, a linkage shaft is further included, the inner rotor is driven to the output shaft through the linkage shaft, and the brake cylinder is in clearance fit with the linkage shaft.

[0018] Based on the above technical scheme, the utility model can realize the following technical effects:

[0019] The cycloid hydraulic motor with brake mechanism of the utility model is driven by sliding, the brake cylinder and the inner rotor are in taper surface fit to realize braking, that is, the brake cylinder is directly driven to slide axially, so that the brake and unbrake of the inner rotor can be realized.

[0020] This utility model discloses a cycloidal hydraulic motor with a braking mechanism. The brake cylinder moves axially under the action of high-pressure oil and an elastic element. The elastic element provides a force towards the inner rotor to the brake cylinder, while the high-pressure oil provides the opposite force. When the cycloidal hydraulic motor is not working, there is no high-pressure oil inside. The brake cylinder slides towards the inner rotor under the action of the elastic element, generating friction between the cylinder and the inner rotor's conical surface, causing the cycloidal hydraulic motor to self-lock and achieve braking. When the cycloidal hydraulic motor is working, high-pressure oil is introduced into the motor and enters the braking chamber, providing the brake cylinder with a force opposite to that of the elastic element. This causes the outer conical surface of the brake cylinder to disengage from the inner conical surface of the inner rotor, and the brake cylinder does not affect the rotation of the inner rotor. The cycloidal hydraulic motor automatically releases the brake. In other words, the forces exerted by the elastic element and high-pressure oil on the brake cylinder meet the requirements for normal operation of the cycloidal hydraulic motor.

[0021] The present invention relates to a cycloidal hydraulic motor with a braking mechanism. The brake cylinder and the brake housing are respectively provided with an outer protrusion and an inner protrusion, so that a brake chamber can be formed between the outer protrusion and the inner protrusion to introduce high-pressure oil. The setting of the sealing element can ensure the sealing of the brake chamber. In addition, the inner protrusion can limit the sliding range of the brake cylinder by limiting the outer protrusion.

[0022] The present invention relates to a cycloidal hydraulic motor with a braking mechanism. The brake cylinder is also provided with a damping hole. The elastic cavity where the elastic element is located is connected to the brake cavity where the high-pressure oil is located through the damping hole. When the oil supply to the cycloidal hydraulic motor stops, the high-pressure oil in the brake cavity can be discharged through the damping hole under the action of the elastic element. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the structure of the cycloidal hydraulic motor with braking mechanism of this utility model;

[0024] Figure 2 This is a schematic diagram of the brake cylinder.

[0025] Figure 3 A cross-sectional view of a cycloidal hydraulic motor with a braking mechanism;

[0026] Figure 4 A cross-sectional view of a cycloidal hydraulic motor with a braking mechanism, taken from another section.

[0027] In the diagram: 1-Stabilizer pair; 11-Outer stator; 12-Inner rotor; 121-Inner conical surface; 13-Pin tooth; 2-Brake cylinder; 21-Outer conical surface; 22-Outer protrusion; 23-Circumferential surface; 24-Damping hole; 25-Seal; 26-Pin; 3-Brake housing; 31-Inner protrusion; 311-Guide groove; 32-One-way valve; 4-Brake chamber; 5-Elastic element; 6-Linkage shaft; 7-Output shaft; 8-Intermediate plate; 81-Elastic chamber; 9-Outer shell; 10-Oil passage. DETAILED DESCRIPTION

[0028] The technical solutions in the embodiments of the present application will be clearly and completely described with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. The description of the at least one exemplary embodiment is actually only illustrative, but not as any limitation on the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.

[0029] It should be noted that the terms used herein are only intended to describe specific embodiments, and are not intended to limit the exemplary embodiments according to the present application. As used herein, the singular form is intended to include the plural form, unless the context clearly indicates otherwise, and it should also be understood that when the terms "comprise" and / or "include" are used in the specification, there is a feature, step, operation, device, component and / or combination thereof.

[0030] Unless specifically stated otherwise, the relative arrangement of components and steps, numerical expressions, and numerical values set forth in the various embodiments described herein are not meant to limit the scope of the present application. At the same time, it should be understood that the sizes of the various parts shown in the drawings are not drawn in proportion. The techniques, methods and devices known to those skilled in the art can not be discussed in detail, but should be considered as part of the specification. In all examples shown and discussed herein, any specific value should be interpreted as merely exemplary, and not as a limitation. Therefore, other examples of exemplary embodiments can have different values. It should be noted that similar reference numbers and letters represent similar items in the following drawings, so that once an item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0031] In the description of the present application, it should be understood that the orientation words such as "front, rear, upper, lower, left, right", "horizontal, vertical, perpendicular, horizontal" and "top, bottom" and the like indicate the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and in the absence of contrary statements, these orientation words do not indicate and imply that the indicated device or element must have a specific orientation or be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the scope of protection of the present application; the orientation words "inner, outer" refer to the inner and outer of the contour of each component itself.

[0032] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0033] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this utility model.

[0034] like Figures 1-4 As shown, this embodiment proposes a cycloidal hydraulic motor with a braking mechanism, including a rotor-stator pair 1 and a brake cylinder 2. The rotor-stator pair 1 includes an eccentrically meshing outer stator 11 and an inner rotor 12. The brake cylinder 2 is slidably mounted on one side of the rotor-stator pair 1. One end of the brake cylinder 2 can extend into the inner rotor 12 and engage with the inner rotor 12 on a conical surface to achieve braking of the inner rotor 12.

[0035] like Figure 1 As shown, the rotor-stator pair 1 includes an outer stator 11 and an inner rotor 12. A pin tooth 13 is provided between the outer stator 11 and the inner rotor 12, and the inner rotor 12 rotates eccentrically within the outer stator 11. The rotor-stator pair 1 transmits power to the output shaft 7 via the linkage shaft 6.

[0036] As a preferred technical solution in this embodiment, the interior of the inner rotor 12 is configured as a hollow structure, and internal teeth are distributed on part of the inner circumferential surface of the inner rotor 12 to facilitate gear transmission with the linkage shaft 6.

[0037] As a preferred embodiment, in order to cooperate with the brake cylinder 2, the inner circumferential surface of one end of the inner rotor 12 is an inner conical surface 121, and the inner circumferential surface of the other end of the inner rotor 12 is a cylindrical surface with internal teeth distributed thereon, which are used for transmission cooperation with the linkage shaft 6. Preferably, the inner conical surface 121 extends from one end face of the inner rotor 12 to the middle position, with the inner conical surface 121 having a larger inner diameter near the end face of the inner rotor 12 and a smaller inner diameter near the middle position of the inner rotor 12.

[0038] Brake cylinder 2 is axially slidably mounted, such as Figure 2 As shown, the brake cylinder 2 has an outer conical surface 21 formed at one end near the inner rotor 12. This end of the brake cylinder 2 with the outer conical surface 21 can extend into the inner rotor 12 and form a friction pair with the conical surface of the inner conical surface 121 to achieve braking. The other end of the brake cylinder 2 is located outside the inner rotor 12 and can form a sliding assembly.

[0039] Specifically, the brake cylinder 2 is slidably mounted inside the brake housing 3, and part of the outer surface of the brake cylinder 2 slides in contact with the inner surface of the brake housing 3.

[0040] As a preferred technical solution of this embodiment, an outer protrusion 22 extends from the outer surface of the brake cylinder 2 away from the outer conical surface 21, and the outer protrusion 22 and the outer conical surface 21 are connected by a circumferential surface 23; correspondingly, an inner protrusion 31 extends from the inner surface of the brake housing 3, and both the inner protrusion 31 and the outer protrusion 22 can be configured as annular protrusions. The inner protrusion 31 and the outer protrusion 22 are staggered. The inner protrusion 31 slides with the circumferential surface 23 of the brake cylinder 2, and the outer protrusion 22 slides with the inner circumferential surface of the brake housing 3.

[0041] In a preferred embodiment, a brake chamber 4 is formed between the outer protrusion 22 and the inner protrusion 31, through which high-pressure oil is introduced. To ensure the sealing of the brake chamber 4, a sealing element 25 is provided on the outer circumferential surface of the outer protrusion 22 of the brake cylinder 2, which ensures sealed sliding between the outer protrusion 22 and the inner surface of the brake housing 3; a sealing element 25 is also provided on the circumferential surface 23 of the brake cylinder 2, which ensures sealed sliding between the inner protrusion 31 and the circumferential surface 23. The sealing element 25 may be, but is not limited to, a sealing ring.

[0042] As a preferred technical solution in this embodiment, such as Figure 3 As shown, to prevent the brake cylinder 2 from rotating with the inner rotor 12, an anti-rotation structure is also provided between the brake cylinder 2 and the brake housing 3. The anti-rotation structure includes a pin 26 fixed to the outer protrusion 22 of the brake cylinder 2; a guide groove 311 is correspondingly provided on the inner protrusion 31 of the brake housing 3, and the pin 26 extends into the guide groove 311 to slide, thus limiting the brake cylinder 2 to only sliding motion and preventing rotation. Alternatively, the pin 26 can be positioned on the brake housing 3, and the guide groove 311 can be positioned on the brake cylinder 2, which also serves as an anti-rotation mechanism. Besides the anti-rotation structure using a pin and guide groove, an anti-rotation structure using a keyway fit between the relative sliding surfaces of the brake cylinder 2 and the brake housing 3 can also be used to prevent rotation; or, an anti-rotation structure can be used where the outer surface of the brake cylinder 2 that slides with the brake housing 3 is a non-circular outer surface.

[0043] As a preferred technical solution of the embodiment, the outer protrusion 22 of the brake cylinder 2 is provided with a damping hole 24 penetrating the outer protrusion 22 in the axial direction, so as to facilitate the oil in the brake chamber 4 to be discharged.

[0044] The brake cylinder 2 is driven to slide by the elastic member 5 and the high-pressure oil. The elastic member 5 provides a force to the brake cylinder 2 in the direction of the inner rotor 12, and the high-pressure oil is introduced into the brake chamber 4 to drive the brake cylinder 2 to slide against the force of the elastic member 5.

[0045] As a preferred technical solution of the embodiment, the elastic member 5 can be selected but is not limited to a disc spring.

[0046] As a preferred technical solution of the embodiment, the brake housing 3 is provided with an intermediate plate 8 away from the side of the rotating stator pair 1, the intermediate plate 8 is formed with an elastic chamber 81 close to the end face of the brake housing 3, and the elastic member 5 is accommodated in the elastic chamber 81 and acts on the brake cylinder 2. The elastic chamber 81 can be an annular chamber.

[0047] The rotating stator pair 1 is driven to the output shaft 7 through the linkage shaft 6, one end of the output shaft 7 is arranged in the housing 9 and is rotatably assembled, and the other end of the output shaft 7 extends out of the housing 9. The side of the rotating stator pair 1 away from the brake housing 3 is also provided with a port plate and an end cover, and the housing 9, the intermediate plate 8, the brake housing 3, the outer stator 11, the port plate and the end cover are sequentially fixedly connected. All the foregoing components can be connected into one body by long bolts, or part of them can be fixedly connected into one body by multiple short bolts. The linkage shaft 6 is arranged inside, one end of the linkage shaft 6 is in driving cooperation with the inner rotor 12, and the other end of the linkage shaft 6 is in driving cooperation with the output shaft 7.

[0048] As a preferred technical solution of the embodiment, the end of the output shaft 7 located in the housing 9 is formed into a hollow structure with an open end, and the linkage shaft 6 extends into the output shaft 7 and is in driving cooperation with the output shaft 7. Specifically, the driving cooperation can be achieved in a gear transmission mode.

[0049] As a preferred technical solution of the embodiment, the brake cylinder 2 is sleeved on the outer periphery of the linkage shaft 6, and there is a gap between the inner surface of the brake cylinder 2 and the linkage shaft 6, so as not to affect the driving effect of the linkage shaft 6.

[0050] As a preferred technical solution of the embodiment, as shown in Figure 4 In order to introduce the high-pressure oil into the brake chamber 4, the end cover, the port plate, the outer stator 11 and the brake housing 3 are formed with an oil channel 10, so as to facilitate the high-pressure oil to be introduced into the brake chamber 4 when the cycloid hydraulic motor is supplied with oil. Preferably, a one-way valve 32 can be arranged in the oil channel 10 to control the one-way flow of the oil. Specifically, the one-way valve 32 can be arranged in the brake housing 3 to control the one-way flow of the oil.

[0051] Based on the above structure, the working principle of the cycloid hydraulic motor with the brake mechanism in the embodiment is as follows: when the cycloid hydraulic motor is not working, no high-pressure oil is in the interior of the cycloid hydraulic motor, no pressure is in the brake cavity 4, but the elastic member 5 is in a compressed state and provides a pressure to the brake cylinder 2 towards the rotating stator pair 1, the brake cylinder 2 moves axially towards the rotating stator pair 1, and the outer conical surface 21 of the brake cylinder 2 contacts the inner conical surface 121 of the inner rotor 12 to generate a friction force. The inner rotor 12 must overcome the friction force to rotate, and the starting torque of the cycloid hydraulic motor is greatly increased. The cycloid hydraulic motor does not provide power to the inner rotor 12 in the non-working state, and the torque generated by external interference working conditions is almost impossible to be greater than the starting torque of the cycloid hydraulic motor after the increase, so that the cycloid hydraulic motor is self-locked to achieve the purpose of braking.

[0052] When the cycloid hydraulic motor is working normally, high-pressure oil is introduced into the brake cavity 4 through the oil channel 10 and the one-way valve 32. The high-pressure oil in the brake cavity 4 provides a force opposite to the elastic member 5 to the brake cylinder 2, and the pressure is greater than the pressure provided by the elastic member 5, so that the brake cylinder 2 moves away from the rotating stator pair 1 until the outer conical surface 21 of the brake cylinder 2 is separated from the inner conical surface 121 of the inner rotor 12, the brake cylinder 2 no longer affects the rotation of the inner rotor 12, and the brake cylinder 2 no longer moves. At this time, the cycloid hydraulic motor automatically releases the brake. And since the rotating track of the inner rotor 12 is a cycloid, when the brake cylinder 2 no longer affects the rotation of the inner rotor 12, the brake cylinder 2 and the inner rotor 12 still have a common area in the axial space, so that the internal space of the cycloid hydraulic motor can be fully utilized, the size of the cycloid hydraulic motor can be reduced as much as possible, and the advantage of small volume of the cycloid hydraulic motor can be maintained.

[0053] The embodiments of the utility model are described in detail in combination with the drawings above, but the utility model is not limited to the above-mentioned embodiments, and various changes can be made within the knowledge range of ordinary skilled persons in the art without departing from the purpose of the utility model.

Claims

1. A gerotor hydraulic motor with a brake mechanism, characterized by, The application relates to a brake cylinder assembly. The brake cylinder assembly comprises a rotating-stator pair (1) which comprises an eccentrically engaged outer stator (11) and an inner rotor (12), the inner periphery of the inner rotor (12) is formed with an inner taper surface (121); a brake cylinder (2) which is axially slidably assembled, one end of the brake cylinder (2) close to the inner rotor (12) is formed with an outer taper surface (21), when the brake cylinder (2) slides towards the inner rotor (12), the outer taper surface (21) of the brake cylinder (2) is taperingly matched with the inner taper surface (121) of the inner rotor (12) to brake. The brake cylinder (2) is axially moved under the action of high-pressure oil and an elastic element (5).

2. The vane hydraulic motor with a brake mechanism according to claim 1, wherein The elastic element (5) provides an acting force towards the inner rotor (12) to the brake cylinder (2), and the high-pressure oil acts on the brake cylinder (2) to move the brake cylinder (2) against the action of the elastic element (5).

3. The vane hydraulic motor with a brake mechanism according to claim 2, wherein The brake cylinder (2) is assembled in a brake housing (3), the brake housing (3) is located on one side of the rotating-stator pair (1), the outer surface of the brake cylinder (2) is formed with an outer protrusion (22) which is slidably matched with the brake housing (3), the inner surface of the brake housing (3) is formed with an inner protrusion (31) which is interactively matched with the brake cylinder (2), and a brake cavity (4) is formed between the inner protrusion (31) and the outer protrusion (22).

4. A vane motor with a brake mechanism according to any one of claims 2-3, characterized in that, The relative sliding surfaces of the inner protrusion (31) and the outer protrusion (22) are sealed by a sealing element (25).

5. The vane hydraulic motor with a brake mechanism according to claim 4, wherein Anti-rotation structures are arranged between the brake cylinder (2) and the brake housing (3).

6. The vane hydraulic motor with a brake mechanism according to claim 4, wherein The anti-rotation structures comprise a pin shaft (26) and a guide groove (311), the pin shaft (26) and the guide groove (311) are arranged on the brake cylinder (2) and the brake housing (3) respectively, and the pin shaft (26) slides into the guide groove (311).

7. The vane hydraulic motor with a brake mechanism according to claim 6, wherein The high-pressure oil enters the brake cavity (4) through an oil channel (10), and a one-way valve (32) is arranged on the oil channel (10).

8. The vane hydraulic motor with a brake mechanism according to claim 4, wherein A damping hole (24) is further arranged on the brake cylinder (2), and an elastic cavity (81) in which the elastic element (5) is arranged is communicated with the brake cavity (4) in which the high-pressure oil is arranged through the damping hole (24).

9. The vane hydraulic motor with a brake mechanism according to claim 2, wherein The brake cylinder assembly further comprises a linkage shaft (6), the inner rotor (12) is driven to an output shaft (7) through the linkage shaft (6), and the brake cylinder (2) is gap-matched with the linkage shaft (6).

10. The vane hydraulic motor with a brake mechanism according to claim 1, wherein ​

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