Cycloid hydraulic motor with brake structure

Abstract

The utility model relates to the technical field of hydraulic systems, in particular to a cycloid hydraulic motor with a brake structure. A cycloid hydraulic motor with a brake structure comprises a rotor and stator pair; an output shaft; the rotor and stator pair is transmitted to the output shaft through the universal driving shaft, and a convex part is arranged on the universal driving shaft; the piston is assembled in an axial sliding mode, the inner circumferential face of the piston comprises a conical face, and the conical face of the piston is matched with the protruding part for braking. According to one embodiment of the utility model, the convex part is spherical. The technical problems that in the prior art, a brake structure of a cycloid motor is complex, the size is large, and the installation space is large are solved.

Description

Technical Field

[0001] This utility model relates to the field of hydraulic system technology, and in particular to a cycloidal hydraulic motor with a braking structure. Background Technology

[0002] Cycloidal hydraulic motors are widely used in various industries due to their simple structure, small size, and high efficiency. In applications involving engineering vehicles, parking and service braking functions are frequently required. Currently, the braking method for cycloidal motors mainly involves braking the output shaft via friction plates. For example, application CN202310584740.3 discloses a cycloidal motor and its braking method. Its built-in braking assembly includes a friction pair, a retaining ring, and a sleeve. The friction pair is sleeved on the output shaft, and its outer ring is connected to the sleeve. The retaining ring is located between the sleeve and an elastic element. Specifically, the right side of the sleeve contacts the piston, and the left side of the sleeve contacts the retaining ring. The elastic force of the elastic element abuts the retaining ring against the left side of the sleeve. A first annular groove is formed on the side of the piston near the motor assembly. The motor assembly has a high-pressure chamber, and the first annular groove communicates with the high-pressure chamber. It should be noted that when high-pressure oil is introduced into the high-pressure chamber of the motor assembly, the oil can reach the first annular groove through the flow channel. Under the action of the high-pressure oil, the piston begins to move to the left. The sleeve and retaining ring also move to the left under the piston's push. At this time, the compressive force on the elastic element increases, the clamping force on the friction pair decreases, and the friction decreases. The output shaft can rotate under the drive of the motor assembly. When the high-pressure oil supply to the high-pressure chamber stops, the force on the piston decreases, and the piston begins to move to the right. Under the action of the elastic element, the friction pair is clamped again, the friction increases, and the output shaft stops rotating, achieving braking. The friction pair includes multiple steel plates and multiple friction plates. The outer ring of the steel plates is connected to the sleeve, and the inner ring of the friction plates is connected to the output shaft. The steel plates and friction plates are spaced apart. The friction plates include friction plates with oil drain grooves and friction plates without oil drain grooves. When the cycloidal motor brakes, hydraulic oil can be quickly discharged through the friction plates with drain grooves, increasing the friction between the friction plates and the steel plates. Friction plates without drain grooves discharge oil more slowly, resulting in a slower increase in friction. When the hydraulic oil is completely discharged, the friction between both types of friction plates and the steel plates is equal. This invention, through the combined use of two types of friction plates, allows for a smooth increase in braking torque. Furthermore, the braking speed can be controlled by adjusting the ratio of the two types of friction plates. While the aforementioned cycloidal motor braking method uses friction plates, it requires multiple brake pads, resulting in numerous components, significant weight, and a braking component size that exceeds the motor's maximum outer diameter. Therefore, it places high demands on the external space available to the customer and increases maintenance costs. Utility Model Content

[0003] To address the technical problems of complex braking structures, large dimensions, and large installation space in existing cycloidal motors, this utility model provides a cycloidal hydraulic motor with a braking structure, thus solving the aforementioned technical problems.

[0004] To solve the above-mentioned technical problems, this utility model provides a cycloidal hydraulic motor with a braking structure, comprising:

[0005] Stator auxiliary;

[0006] Output shaft;

[0007] The rotor-stator pair is driven to the output shaft via the linkage shaft, and the linkage shaft is provided with a protrusion.

[0008] A piston, which is axially slidably assembled, has an inner circumferential surface including a tapered surface, and the tapered surface of the piston engages with the protrusion for braking.

[0009] According to one embodiment of the present invention, the protrusion is spherical.

[0010] According to one embodiment of the present invention, the piston moves under the action of an elastic element and high-pressure oil.

[0011] According to one embodiment of the present invention, under the action of the elastic element, the conical surface of the piston contacts the protrusion to form a brake; under the action of high-pressure oil, the piston moves against the action of the elastic element, and the conical surface of the piston disengages from the protrusion.

[0012] According to one embodiment of the present invention, the piston is slidably assembled in the brake housing, and a brake cavity is formed between the piston and the brake housing to introduce high-pressure oil.

[0013] According to one embodiment of the present invention, the inner surface of the brake housing extends with an inner protrusion that slides with the piston, and the outer surface of the piston extends with an outer protrusion that slides with the brake housing, and the brake cavity is formed between the inner protrusion and the outer protrusion.

[0014] According to one embodiment of the present invention, a damping hole is formed on the outer protrusion, and the braking cavity and the receiving cavity where the elastic element is located are connected through the damping hole.

[0015] According to one embodiment of the present invention, the brake housing is further provided with an anti-rotation structure, which restricts the rotation of the piston.

[0016] According to one embodiment of the present invention, the anti-rotation structure includes a positioning pin disposed on the inner protrusion, and a corresponding positioning groove is disposed on the piston. The positioning pin extends into the positioning groove to limit the piston to only slide.

[0017] According to one embodiment of the present invention, one end of the linkage shaft is driven to the rotor-stator pair, and the other end of the linkage shaft is driven to the output shaft. The protrusion is located between the rotor-stator pair and the output shaft in the axial direction.

[0018] Based on the above technical solution, the technical effects that this utility model can achieve are as follows:

[0019] This utility model discloses a cycloidal hydraulic motor with a braking structure, which is equipped with a piston that slides axially to brake the linkage shaft. The piston simultaneously serves as an axial drive and a friction pair, integrating the piston and friction pair in the prior art into a single design. This simplifies the braking structure, greatly reduces the size of the braking part, and minimizes the installation space.

[0020] The cycloidal hydraulic motor with braking structure of this utility model has a spherical protrusion. When braking, the radial load of the spherical and conical surfaces is used to achieve braking. In this way, the sliding friction braking is changed to the main radial load braking, which can effectively improve the reliability of braking.

[0021] This utility model discloses a cycloidal hydraulic motor with a braking structure. The piston moves under the action of an elastic element and high-pressure oil. When the cycloidal hydraulic motor is not in operation, the elastic element pushes the piston until the conical surface contacts the convex surface, forming a brake. The linkage shaft is locked by the piston and cannot rotate, achieving self-locking when the cycloidal hydraulic motor is not working. When the cycloidal hydraulic motor is in operation with high-pressure oil, the high-pressure oil enters the braking chamber and acts on the piston. The piston overcomes the force of the elastic element and pushes the piston away from the convex part, preventing the piston from interfering with the rotation of the linkage shaft, allowing the motor to operate normally.

[0022] The cycloidal hydraulic motor with braking structure of this utility model has a damping hole. After the high-pressure oil supply is stopped, the hydraulic oil in the braking chamber can be gradually discharged through the damping hole under the action of the elastic element.

[0023] This utility model discloses a cycloidal hydraulic motor with a braking structure. The anti-rotation structure prevents the piston from rotating under excessive external load, thus avoiding the situation where the linkage shaft drives the piston to rotate. Furthermore, the anti-rotation structure comprises a locating pin and a locating groove, which simultaneously serve as a guide and prevent rotation. Attached Figure Description

[0024] Figure 1 This is a schematic diagram of the cycloidal hydraulic motor with braking structure of this utility model.

[0025] Figure 2 This is a schematic diagram of the linkage shaft.

[0026] Figure 3 This is a schematic diagram of the piston structure;

[0027] Figure 4 A cross-sectional view of a cycloidal hydraulic motor with a braking structure;

[0028] Figure 5 A cross-sectional view of a cycloidal hydraulic motor with a braking structure in another section;

[0029] In the diagram: 1-Stator pair; 11-Stator; 12-Rotor; 13-Pin tooth; 2-Output shaft; 3-Linkage shaft; 31-Protrusion; 32-First end; 33-Second end; 4-Piston; 41-Conical surface; 42-Outer protrusion; 43-Seal; 44-Damping hole; 45-Positioning groove; 5-Elastic element; 6-Brake chamber; 7-Brake housing; 71-Inner protrusion; 72-One-way valve; 73-Positioning pin; 8-Connecting plate; 9-Outer shell; 10-Oil passage. Detailed Implementation

[0030] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present utility model or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of the present utility model without creative effort are within the scope of protection of the present utility model.

[0031] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0032] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0033] In the description of this utility model, it should be understood that the directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this utility model. The directional terms "inner" and "outer" refer to the inner and outer contours of each component itself.

[0034] 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.

[0035] 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.

[0036] like Figure 1-5 As shown, this embodiment proposes a cycloidal hydraulic motor with a braking structure, including a rotor-stator pair 1, an output shaft 2, a linkage shaft 3, and a piston 4. The rotor-stator pair 1 transmits power to the output shaft 2 via the linkage shaft 3. During braking, the piston 4 acts on the linkage shaft 3 to achieve the braking effect. When the cycloidal hydraulic motor is working normally, the piston 4 does not affect the normal transmission of the linkage shaft 3; during braking, the piston 4 contacts the linkage shaft 3, causing the linkage shaft 3 to be unable to rotate due to friction, thus achieving the braking effect on the cycloidal hydraulic motor.

[0037] like Figure 1 As shown, the rotor-stator pair 1 includes an eccentrically meshing stator 11 and a rotor 12. The stator 11 is located on the outer periphery of the rotor 12, and needle teeth 13 are distributed on the inner circumferential surface of the stator 11. The rotor 12 rotates eccentrically within the stator 11.

[0038] One end of the output shaft 2 is rotatably mounted inside the housing 9, while the other end of the output shaft 2 is located outside the housing 9. The end of the output shaft 2 located inside the housing 9 is engaged with the linkage shaft 3 for transmission.

[0039] As a preferred embodiment, the output shaft 2, located inside the housing 9, is configured as a hollow structure with one end open, and the linkage shaft 3 can extend into the interior of the output shaft 2 to perform transmission with the output shaft 2. Preferably, gear transmission can be used between the output shaft 2 and the linkage shaft 3.

[0040] The linkage shaft 3 serves a transmission function. The first end 32 of the linkage shaft 3 is in transmission engagement with the rotor-stator pair 1, and the second end 33 of the linkage shaft 3 is in transmission engagement with the output shaft 2. A protrusion 31 is also provided on the outer circumferential surface of the linkage shaft 3. The protrusion 31 is located between the first end 32 and the second end 33 of the linkage shaft 3 and is used to cooperate with the piston 4 for braking.

[0041] As a preferred technical solution of this embodiment, the first end 32 and the second end 33 of the linkage shaft 3 are respectively provided with external teeth, the output shaft 2 is provided with internal teeth, and the inner circumferential surface of the rotor 12 of the rotor-stator pair 1 is also provided with internal teeth. The two ends of the linkage shaft 3 are respectively connected to the rotor-stator pair 1 and the output shaft 2 for gear transmission.

[0042] As a preferred technical solution in this embodiment, the protrusion 31 is provided in a spherical shape.

[0043] The piston 4 is ring-shaped and is sleeved outside the linkage shaft 3, allowing for axial sliding motion. The piston 4 is positioned near the protrusion 31 of the linkage shaft 3. The inner circumferential surface of the piston 4 includes a conical surface 41. When the piston 4 slides axially, its conical surface 41 can move closer to or away from the protrusion 31. When the conical surface 41 approaches and contacts the protrusion 31, the radial load between the spherical surface of the protrusion 31 and the conical surface 41 of the piston 4 can achieve braking, transforming sliding friction braking into primary radial load braking, which can effectively improve reliability.

[0044] Piston 4 is slidably mounted in brake housing 7, and piston 4 slides under the action of elastic element 5 and high-pressure oil.

[0045] As a preferred technical solution in this embodiment, the inner circumferential surface of the piston 4 is a tapered surface 41. The tapered surface 41 extends from one end of the piston 4 along the axial direction to the other end, and the end with the larger inner diameter of the tapered surface 41 is located near the protrusion 31.

[0046] As a preferred technical solution in this embodiment, under the action of the elastic element 5, the piston 4 slides axially, and its conical surface 41 approaches the protrusion 31 until it contacts it, forming a brake; under the action of high pressure oil, the piston 4 overcomes the action of the elastic element 5 and slides axially, and its conical surface 41 moves away from the protrusion 31, without affecting the transmission function of the linkage shaft 3.

[0047] As a preferred embodiment, a brake cavity 6 is formed between the piston 4 and the brake housing 7, and high-pressure oil can be introduced into the brake cavity 6. Specifically, an inner protrusion 71 extends from the inner surface of the brake housing 7 to slide and engage with the piston 4, and an outer protrusion 42 extends from the outer surface of the piston 4 to slide and engage with the brake housing 7. The inner protrusion 71 and the outer protrusion 42 are staggered, and the brake cavity 6 is formed between the inner protrusion 71 and the outer protrusion 42. Both the inner protrusion 71 and the outer protrusion 42 are annular protrusions.

[0048] As a preferred technical solution in this embodiment, in order to ensure the sealing of the brake chamber 6, a sealing element 43 is provided at the position where the piston 4 slides with the brake housing 7. In this embodiment, a sealing element 43 is provided on the outer peripheral surface of the outer protrusion 42 of the piston 4, and a sealing element 43 is also provided on the outer peripheral surface of the piston 4 that slides with the inner protrusion 71.

[0049] As a preferred embodiment, in order to introduce high-pressure oil into the brake chamber 6, oil passages 10 are provided on the rear end cover, distributor plate, stator 11, and brake housing 7, through which high-pressure oil can enter the brake chamber 6. A one-way valve 72 is provided on the oil passage 10 in the brake housing 7 to control the one-way flow of high-pressure oil.

[0050] As a preferred technical solution of this embodiment, the elastic element 5 can be set as a disc spring, a rotor-stator pair 1 is provided on one side of the brake housing 7, and a connecting plate 8 is provided on the other side of the brake housing 7. A receiving cavity is formed on the end face of the connecting plate 8 near the brake housing 7, and the elastic element 5 is located in the receiving cavity and acts on the piston 4.

[0051] As a preferred technical solution in this embodiment, a damping hole 44 is formed on the piston 4 to facilitate oil drainage from the brake chamber 6. The damping hole 44 connects the brake chamber 6 and the receiving cavity where the elastic element 5 is located. When the high-pressure oil supply stops, the oil in the brake chamber 6 can gradually drain under the action of the elastic element 5.

[0052] To prevent excessive external load from causing the linkage shaft 3 to rotate the piston 4, an anti-rotation structure is provided on the brake housing 7 to limit the rotation of the piston 4. Specifically, the anti-rotation structure includes a positioning pin 73, which is disposed on the inner protrusion 71 of the brake housing 7 and faces the piston 4; correspondingly, the piston 4 is provided with a positioning groove 45, and the positioning pin 73 extends into the positioning groove 45 and slides. The positioning pin 73 extends parallel to the axial direction, and at least two positioning pins 73 can be provided, and they are evenly distributed along the circumference.

[0053] Based on the above technical solution, in the cycloidal hydraulic motor with braking structure of this embodiment, when no oil is supplied, the elastic member 5 pushes the piston 4 toward the protrusion 31, so that the position of the smaller inner diameter of the conical surface 41 of the piston 4 contacts the protrusion 31 of the linkage shaft 3 to form a fit, and the linkage shaft 3 will be locked by the piston 4 and cannot rotate.

[0054] When high-pressure oil is introduced, it enters from oil passage 10, opens one-way valve 72, and reaches the brake chamber 6 formed by piston 4 and brake housing 7. The pressure acts on piston 4, which will overcome the elastic force of elastic element 5 and push piston 4. The smaller inner diameter of the conical surface 41 of piston 4 will disengage from the linkage shaft 3, while the larger inner diameter of the conical surface 41 will not interfere with the rotation of linkage shaft 3, and the cycloidal hydraulic motor will rotate normally.

[0055] When the oil supply to the oil port stops, due to the design of the damping hole 44, the hydraulic oil in the brake chamber 6 formed by the piston 4 and the brake housing 7 will gradually leak out under the action of the elastic element 5. The piston 4 will move towards the protrusion 31 again, and the linkage shaft 3 and the conical surface 41 of the piston 4 will contact each other again to form a friction surface. The linkage shaft 3 will be locked again, and the cycloidal hydraulic motor will stop rotating.

[0056] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present invention.

Claims

1. A cycloidal hydraulic motor with a braking structure, characterized in that, include: Stator auxiliary (1); Output shaft (2); Linkage shaft (3), the rotor-stator pair (1) is driven to the output shaft (2) through the linkage shaft (3), and the linkage shaft (3) is provided with a protrusion (31). The piston (4) is axially slidably assembled, and the inner circumferential surface of the piston (4) includes a tapered surface (41), which engages with the protrusion (31) for braking.

2. A cycloidal hydraulic motor with a braking structure according to claim 1, characterized in that, The protrusion (31) is spherical.

3. A cycloidal hydraulic motor with a braking structure according to claim 1, characterized in that, The piston (4) moves under the action of the elastic element (5) and the high-pressure oil.

4. A cycloidal hydraulic motor with a braking structure according to claim 3, characterized in that, Under the action of the elastic element (5), the conical surface (41) of the piston (4) contacts the protrusion (31) to form a brake; under the action of high pressure oil, the piston (4) moves against the action of the elastic element (5), and the conical surface (41) of the piston (4) disengages from the protrusion (31).

5. A cycloidal hydraulic motor with a braking structure according to any one of claims 3-4, characterized in that, The piston (4) is slidably mounted in the brake housing (7), and a brake cavity (6) is formed between the piston (4) and the brake housing (7) to introduce high-pressure oil.

6. A cycloidal hydraulic motor with a braking structure according to claim 5, characterized in that, The inner surface of the brake housing (7) extends an inner protrusion (71) that slides with the piston (4), and the outer surface of the piston (4) extends an outer protrusion (42) that slides with the brake housing (7). The brake cavity (6) is formed between the inner protrusion (71) and the outer protrusion (42).

7. A cycloidal hydraulic motor with a braking structure according to claim 6, characterized in that, A damping hole (44) is formed on the outer protrusion (42), and the receiving cavity where the braking cavity (6) and the elastic element (5) are located are connected through the damping hole (44).

8. A cycloidal hydraulic motor with a braking structure according to claim 6, characterized in that, The brake housing (7) is also provided with an anti-rotation structure, which restricts the rotation of the piston (4).

9. A cycloidal hydraulic motor with a braking structure according to claim 8, characterized in that, The anti-rotation structure includes a positioning pin (73) disposed on the inner protrusion (71), and a corresponding positioning groove (45) is disposed on the piston (4). The positioning pin (73) extends into the positioning groove (45) to limit the piston (4) to only slide.

10. A cycloidal hydraulic motor with a braking structure according to claim 1, characterized in that, One end of the linkage shaft (3) is driven by the rotor-stator pair (1), and the other end of the linkage shaft (3) is driven by the output shaft (2). The protrusion (31) is located between the rotor-stator pair (1) and the output shaft (2) in the axial direction.

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