CN213064401U - Clutch for automatic transmission - Google Patents
Clutch for automatic transmission Download PDFInfo
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- CN213064401U CN213064401U CN202021208582.XU CN202021208582U CN213064401U CN 213064401 U CN213064401 U CN 213064401U CN 202021208582 U CN202021208582 U CN 202021208582U CN 213064401 U CN213064401 U CN 213064401U
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- balance
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Abstract
The disclosure relates to the technical field of automatic transmissions and provides a clutch for an automatic transmission. The clutch comprises a friction device, a piston device and a reset device, wherein the friction device comprises a friction plate set, an inner hub and an outer hub, and a mounting cavity is formed on one side of the inner hub; the piston device comprises a main piston and a balance piston, a main piston cavity is formed between the main piston and the balance piston, and a balance piston cavity is formed between the main piston and the inner wall of the inner hub; the return means is arranged to apply a force to the master piston in a direction away from the set of friction plates. The side surface of the inner hub of the clutch is provided with the mounting cavity, and the main piston and the balance piston are both arranged in the mounting cavity, so that the structure is compact, and the occupied space is reduced; the main piston cavity is formed by the main piston and the balance piston, and the structure of the main piston and the balance piston is not limited, so that the shape and the volume of the main piston cavity can be freely designed, hydraulic oil can be quickly filled in the main piston cavity, the reaction speed of the clutch is increased, and the use requirement is met.
Description
Technical Field
The present disclosure relates to the technical field of automatic transmissions, and particularly to a clutch for an automatic transmission.
Background
An automotive transmission is a set of transmission devices for coordinating the rotational speed of an engine and the actual driving speed of wheels, and is used for exerting the best performance of the engine. The transmission can generate different gear ratios between an engine and wheels during the running process of the automobile, and the transmission of rotating speeds of different gears is realized.
The manual transmission mainly comprises gears and a rotating shaft, and the speed change and torque change are generated by different gear combinations; the automatic transmission AT consists of a hydraulic torque converter, a planetary gear and a hydraulic control system, and achieves speed and torque changing through a hydraulic transmission and gear combination mode.
Among them, the automatic transmission has advantages of comfortable driving, reducing fatigue of driver, etc., and has become a development direction of modern car configuration. The automatic transmission utilizes a planetary gear mechanism to change speed, can automatically change speed according to the degree of an accelerator pedal and the change of vehicle speed, and a driver only needs to operate the accelerator pedal to control the vehicle speed, so that the driver can watch road traffic with full attention without being confused by gear shifting.
The automatic transmission includes a plurality of planetary gear assemblies and a plurality of shift elements, wherein the shift elements include clutches and brakes. The clutch includes a friction plate pack and a piston arrangement.
In particular, the inner and outer rings of the friction disc pack are in turn connected with an inner and an outer hub, respectively, which are usually connected with the rotating part, wherein the outer hub is connected with the stationary part when the shifting element is a brake. The piston device comprises a piston support, a main piston and a balance piston, and a piston cavity is formed between the piston support and the main piston. By supplying oil to the piston chamber, the main piston is moved relative to the piston support in the direction of the friction plate set, and the clutch is closed by the main piston pressing against the friction plate set. The balance piston is arranged on one side, far away from the piston cavity, of the main piston, and a balance piston cavity is formed between the balance piston and the main piston, so that the effect of balancing pressure is achieved. One side of the main piston is provided with a return spring, and after the pressure of the hydraulic oil is relieved, the main piston moves towards the direction far away from the friction plate set under the action of the return spring, so that the clutch is opened. The transmission relationship of each planetary transmission assembly is changed through the gear shifting unit, so that the automatic transmission outputs different rotating speeds. However, this arrangement of the shifting element has the following disadvantages:
(1) the structure is comparatively complicated, and occupation space is big, needs additionally to set up the piston and supports, extravagant equipment cost.
(2) The piston chamber formed between the main piston and the piston support has a relatively large chamber volume, and the hydraulic oil takes a relatively long time to fill the piston chamber, resulting in a relatively slow response speed of the shifting element.
SUMMERY OF THE UTILITY MODEL
To solve the above technical problem or at least partially solve the above technical problem, the present disclosure provides a clutch for an automatic transmission.
The present disclosure provides a clutch for an automatic transmission, comprising:
the friction device comprises a friction plate group, an inner hub and an outer hub, wherein the inner hub and the outer hub are respectively arranged on an inner ring and an outer ring of the friction plate group;
the piston device comprises a main piston and a balance piston which are arranged in the mounting cavity, the main piston is in sliding fit with the inner wall of the inner hub along the axial direction of the inner hub, the outer ring of the main piston extends out of the mounting cavity and is supported on the outer side of the friction plate group, the inner ring of the balance piston is axially limited with the inner wall of the inner hub, the outer ring of the balance piston is supported on the inner wall of the main piston and is in sliding fit with the main piston along the axial direction, a main piston cavity is formed between the main piston and the balance piston, and a balance piston cavity is formed between the main piston and the inner wall of the inner hub;
and the resetting device is arranged in the balance piston cavity and is used for applying force towards the direction far away from the friction plate group to the main piston.
Optionally, the inner hub includes an inner sleeve for rotationally cooperating with an input shaft of the transmission and an outer sleeve for connecting with the friction plate set, a connection disc is provided between the inner sleeve and the outer sleeve, and the connection disc, facing the main piston, and the inner sleeve and the outer sleeve form the mounting cavity.
Optionally, the main piston comprises a main piston inner cylinder, a main piston outer cylinder and a main piston connecting disc, the main piston inner cylinder is in sliding fit with the inner sleeve along the axial direction, the main piston outer cylinder is in sliding fit with the outer sleeve along the axial direction, an inner ring and an outer ring of the main piston connecting disc are respectively connected to one side, facing the connecting disc, of the main piston inner cylinder and one side, facing the connecting disc, of the main piston outer cylinder, and a balance piston cavity is defined by the inner sleeve, the outer sleeve, the connecting disc and the main piston connecting disc.
Optionally, the inner ring of the main piston connecting disc is bent towards the direction of the balance piston cavity to form a pressure bearing part, the pressure bearing part is connected with the main piston inner cylinder through an arc-shaped transition section, an oil supply cavity is defined by the main piston inner cylinder, the arc-shaped transition section and the pressure bearing part, the balance piston is provided with a counter-support part matched with the oil supply cavity in shape, and the main piston cavity is defined by the counter-support part, the pressure bearing part, the arc-shaped transition section and the main piston inner cylinder.
Optionally, the distance between the main piston inner cylinder and the counter support part is 1.5-2.1 mm.
Optionally, the distance between the pressure bearing part and the counter-support part is 1.5-2.1 mm.
Optionally, the distance between the arc-shaped transition section and the counter support is 2.1-2.5 mm.
Optionally, a distance between the arc-shaped transition section and the counter support portion is greater than a distance between the main piston inner cylinder and the counter support portion, and a distance between the arc-shaped transition section and the counter support portion is greater than a distance between the pressure bearing portion and the counter support portion.
Optionally, the inner hub is provided with a first oil path for communicating with the main piston cavity and a second oil path for communicating with the balance piston cavity.
Optionally, the return device includes a return spring disposed inside the balance piston cavity, one end of the return spring is supported on the side wall of the main piston, and the other end of the return spring is supported on the inner wall of the inner hub.
Compared with the prior art, the technical scheme provided by the embodiment of the disclosure has the following advantages:
the side surface of the inner hub of the clutch is provided with the mounting cavity, and the main piston and the balance piston are both arranged in the mounting cavity, so that the structure is compact, the occupied space is reduced, no additional supporting part is required, and the equipment cost is saved; the main piston cavity is formed by the main piston and the balance piston, and the structure of the main piston and the balance piston is not limited, so that the shape and the volume of the main piston cavity can be freely designed, hydraulic oil can be quickly filled in the main piston cavity, the reaction speed of the clutch is increased, and the use requirement is met.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present disclosure and together with the description, serve to explain the principles of the disclosure.
In order to more clearly illustrate the embodiments or technical solutions in the prior art of the present disclosure, the drawings used in the description of the embodiments or prior art will be briefly described below, and it is obvious for those skilled in the art that other drawings can be obtained according to the drawings without inventive exercise.
FIG. 1 is a cross-sectional view of a clutch according to an embodiment of the present disclosure installed in a transmission;
fig. 2 is an enlarged view of a point a in fig. 1.
Wherein, 10, friction plate group; 20. an inner hub; 21. an inner sleeve; 22. an outer sleeve; 23. a connecting disc; 24. a first oil passage; 25. a second oil passage; 30. a primary piston; 31. a main piston inner cylinder; 32. a main piston outer cylinder; 33. a main piston connecting disc; 331. a pressure-bearing portion; 332. an arc-shaped transition section; 40. a balance piston; 41. a counter support; 50. a primary piston chamber; 60. a balance piston cavity; 70. a return spring.
Detailed Description
In order that the above objects, features and advantages of the present disclosure may be more clearly understood, aspects of the present disclosure will be further described below. It should be noted that the embodiments and features of the embodiments of the present disclosure may be combined with each other without conflict.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present disclosure, but the present disclosure may be practiced in other ways than those described herein; it is to be understood that the embodiments disclosed in the specification are only a few embodiments of the present disclosure, and not all embodiments.
As shown in fig. 1, the present embodiment provides a clutch for an automatic transmission including a friction device, a piston device, and a return device.
The friction device comprises a friction plate group 10, an inner hub 20 and an outer hub which are respectively arranged on an inner ring and an outer ring of the friction plate group 10, and a mounting cavity is formed on one side of the inner hub 20. The present solution mainly protects the arrangement between the inner hub 20, the main piston 30 and the balance piston 40, and therefore the outer hub is not shown in the drawings. However, the connection of the friction plate sets 10 to the inner hub 20 and the outer hub is common in the art, and thus, the arrangement of the outer hub can be obtained by a person skilled in the art in combination with the common knowledge.
As shown in fig. 1 and 2, the piston device includes a main piston 30 and a balance piston 40 disposed inside the mounting cavity, wherein the disposition inside the mounting cavity does not mean that the main piston 30 and the balance piston 40 are disposed completely inside the mounting cavity, i.e., the main piston 30 and the balance piston 40 may be partially disposed inside the mounting cavity, and another portion is exposed. The main piston 30 is slidably fitted to an inner wall of the inner hub 20 in an axial direction of the inner hub 20, wherein the main piston 30 and the inner hub 20 are both rotary members and have an axis coincident with an axis of an input shaft of the transmission. The outer race of the primary piston 30 extends out of the mounting cavity and is supported outside of the friction plate pack 10.
The inner ring of the balance piston 40 is axially limited from the inner wall of the inner hub 20, i.e. the balance piston 40 is not movable in the axial direction relative to the inner hub 20, and the axial direction is the axial direction of the inner hub 20. Preferably, the balance piston 40 is connected to the inner hub 20 by a circlip. The outer race of the balance piston 40 is supported on the inner wall of the main piston 30 and is in sliding engagement with the main piston 30 in the axial direction, which is also referred to as the axial direction of the input shaft. A main piston chamber 50 is formed between the main piston 30 and the balance piston 40, and a balance piston chamber 60 is formed between the main piston 30 and the inner wall of the inner hub 20. The inner hub 20 is provided with a first oil passage 24 for communicating with the master piston chamber 50 and a second oil passage 25 for communicating with the balance piston chamber 60. A reset device is disposed within balance piston chamber 60 for applying a force to master piston 30 in a direction away from friction plate set 10.
In the use process, the first oil path 24 and the second oil path 25 are both filled with hydraulic oil, wherein the hydraulic oil entering the main piston cavity 50 pushes the main piston 30 to move towards the direction of the friction plate set 10, so that the main piston 30 compresses the friction plate set 10 to close the clutch, and the hydraulic oil in the balance piston cavity 50 plays a role in balancing the main piston 30. When the clutch is opened, hydraulic oil is relieved and the reset device pushes the master piston 30 to move away from the friction plate set 10.
The side surface of the clutch inner hub 20 is provided with the mounting cavity, and the main piston 30 and the balance piston 40 are both arranged in the mounting cavity, so that the structure is compact, the occupied space is reduced, no additional supporting component is required, and the equipment cost is saved; the main piston cavity 50 is formed by the main piston 30 and the balance piston 40, and the structures of the main piston 30 and the balance piston 40 are not limited, so that the shape and the volume of the main piston cavity 50 can be freely designed, hydraulic oil can be quickly filled in the main piston cavity 50, the reaction speed of the clutch is increased, and the use requirement is met.
As shown in fig. 1, the inner hub 20 includes an inner sleeve 21 for rotationally cooperating with an input shaft of the transmission and an outer sleeve 22 for connecting with the friction plate group 10, a connecting disc 23 is provided between the inner sleeve 21 and the outer sleeve 22, and a mounting cavity is defined between a side of the connecting disc 23 facing the main piston 30 and the inner sleeve 21 and the outer sleeve 22. The connecting discs 23 are not arranged on the sides of the inner sleeve 21 and the outer sleeve 22, namely, the connecting discs 23 extend out of two ends of the inner sleeve 21, the connecting discs 23 extend out of two ends of the outer sleeve 22, so that a mounting cavity is formed conveniently, one side of each connecting disc 23 far away from the mounting cavity can be used for mounting other components, and the structure compactness is improved.
As shown in fig. 2, the main piston 30 includes a main piston inner cylinder 31, a main piston outer cylinder 32, and a main piston connecting disc 33, the main piston inner cylinder 31 is slidably fitted to the inner sleeve 21 in the axial direction, and the main piston outer cylinder 32 is slidably fitted to the outer sleeve 22 in the axial direction, which is the axial direction of the input shaft. The inner ring and the outer ring of the main piston connecting disc 33 are respectively connected to one side of the main piston inner cylinder 31 and one side of the main piston outer cylinder 32 facing the connecting disc 23, and a balance piston cavity 60 is defined by the inner sleeve 21, the outer sleeve 22, the connecting disc 23 and the main piston connecting disc 33. The main piston outer cylinder 32 extends out of the mounting cavity and extends in a direction away from the input shaft, and the extension section of the main piston outer cylinder is bent in a direction towards the friction plate group 10 and used for pressing the friction plate group 10. Further preferably, a seal ring is provided between the main piston inner cylinder 31 and the inner sleeve 21, and a seal ring is also provided between the main piston outer cylinder 32 and the outer sleeve 22, in order to increase the sealing effect.
As shown in fig. 2, the inner ring of the main piston connecting disc 33 is bent toward the balance piston cavity 60 to form a pressure receiving portion 331, the pressure receiving portion 331 is connected to the main piston inner cylinder 31 through an arc-shaped transition section 332, an oil supply cavity is defined by the main piston inner cylinder 31, the arc-shaped transition section 332 and the pressure receiving portion 331, and the balance piston 40 has a counter support portion 41 matching the shape of the oil supply cavity. The counter support portion 41, the pressure-bearing portion 331, the arc-shaped transition section 332 and the main piston inner cylinder 31 enclose a main piston cavity 50. The reverse support part 41 plays a reverse supporting role for the movement of the main piston 30, and the design mode reduces the volume of the main piston cavity 50, so that the hydraulic oil is quickly filled in the main piston cavity 50, and the response speed of the clutch is increased.
Further optimally, the distance between the main piston inner cylinder 31 and the counter support 41 is 1.5-2.1 mm. The distance between the pressure-bearing part 331 and the counter-support part 41 is 1.5-2.1 mm. The distance between the arc transition section 332 and the counter support 41 is 2.1-2.5 mm. A main piston chamber 50 at this size meets the pressure requirements of the main piston 30 while increasing the response speed of the clutch.
The distance between the arc-shaped transition section 332 and the counter support 41 is greater than the distance between the main piston inner cylinder 31 and the counter support 41, and the distance between the arc-shaped transition section 332 and the counter support 41 is greater than the distance between the pressure receiving portion 331 and the counter support 41. When the hydraulic oil enters between the main piston inner cylinder 31 and the counter support portion 41, the oil pressure is large, so that buffering needs to be performed through the arc transition section 332, and the distance between the arc transition section 332 and the counter support portion 41 is large, which is beneficial to reducing the oil pressure of the hydraulic oil, the reduced hydraulic oil enters into a space surrounded by the pressure bearing portion 331 and the counter support portion 41, so that the hydraulic oil presses the pressure bearing portion 331 to move towards the direction of the balance piston cavity 60, and when the main piston 30 moves relative to the balance piston 40, the hydraulic oil in the main piston cavity 50 fills the gap between the main piston 30 and the balance piston 40.
As shown in fig. 1 and 2, the restoring means includes a restoring spring 70 disposed inside the balance piston chamber 60, and one end of the restoring spring 70 is supported on a side wall of the main piston 30 and the other end is supported on an inner wall of the inner hub 20 to restore the main piston 30. And return spring 70 is preferably a diaphragm spring, reducing space usage.
It is noted that, in this document, relational terms such as "first" and "second," and the like, may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other identical elements in a process, method, article, or apparatus that comprises the element.
The foregoing are merely exemplary embodiments of the present disclosure, which enable those skilled in the art to understand or practice the present disclosure. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the disclosure. Thus, the present disclosure is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (10)
1. A clutch for an automatic transmission, comprising:
the friction device comprises a friction plate group (10), and an inner hub (20) and an outer hub which are respectively arranged on an inner ring and an outer ring of the friction plate group (10), wherein one side of the inner hub (20) forms an installation cavity;
the piston device comprises a main piston (30) and a balance piston (40) which are arranged inside the mounting cavity, wherein the main piston (30) is in sliding fit with the inner wall of the inner hub (20) along the axial direction of the inner hub (20), the outer ring of the main piston (30) extends out of the mounting cavity and is supported on the outer side of the friction plate group (10), the inner ring of the balance piston (40) is axially limited with the inner wall of the inner hub (20), the outer ring of the balance piston (40) is supported on the inner wall of the main piston (30) and is in sliding fit with the main piston (30) along the axial direction, a main piston cavity (50) is formed between the main piston (30) and the balance piston (40), and a balance piston cavity (60) is formed between the main piston (30) and the inner wall of the inner hub (20);
a return means disposed within the balance piston chamber (60) for applying a force to the master piston (30) in a direction away from the set of friction plates (10).
2. Clutch for an automatic transmission according to claim 1, wherein the inner hub (20) comprises an inner sleeve (21) for rotational engagement with an input shaft of the transmission and an outer sleeve (22) for connection with the set of friction plates (10), a connection disc (23) being provided between the inner sleeve (21) and the outer sleeve (22), the connection disc (23) enclosing the mounting cavity between the inner sleeve (21) and the outer sleeve (22) on the side of the connection disc (23) facing the master piston (30).
3. The clutch for an automatic transmission according to claim 2, wherein the main piston (30) includes a main piston inner cylinder (31), a main piston outer cylinder (32), and a main piston connecting disc (33), the main piston inner cylinder (31) is slidably fitted with the inner sleeve (21) along the axial direction, the main piston outer cylinder (32) is slidably fitted with the outer sleeve (22) along the axial direction, inner and outer rings of the main piston connecting disc (33) are respectively connected to a side of the main piston inner cylinder (31) and the main piston outer cylinder (32) facing the connecting disc (23), and the inner sleeve (21), the outer sleeve (22), the connecting disc (23), and the main piston connecting disc (33) enclose the balance piston cavity (60) therebetween.
4. The clutch for the automatic transmission according to claim 3, wherein an inner ring of the main piston connecting disc (33) is bent towards the direction of the balance piston cavity (60) to form a bearing portion (331), the bearing portion (331) is connected with the main piston inner cylinder (31) through an arc-shaped transition section (332), an oil supply cavity is defined by the main piston inner cylinder (31), the arc-shaped transition section (332) and the bearing portion (331), the balance piston (40) is provided with a counter support portion (41) matched with the shape of the oil supply cavity, and the main piston cavity (50) is defined by the counter support portion (41), the bearing portion (331), the arc-shaped transition section (332) and the main piston inner cylinder (31).
5. Clutch for an automatic transmission according to claim 4, characterized in that the distance between the main piston inner cylinder (31) and the counter support (41) is 1.5-2.1 mm.
6. The clutch for an automatic transmission according to claim 4, wherein a distance between the pressure receiving portion (331) and the counter support portion (41) is 1.5-2.1 mm.
7. Clutch for an automatic transmission according to claim 4, characterized in that the distance between the arc-shaped transition section (332) and the counter support (41) is 2.1-2.5 mm.
8. The clutch for an automatic transmission according to claim 4, characterized in that a distance between the arcuate transition section (332) and the counter support portion (41) is larger than a distance between the main piston inner cylinder (31) and the counter support portion (41), and a distance between the arcuate transition section (332) and the counter support portion (41) is larger than a distance between the pressure receiving portion (331) and the counter support portion (41).
9. The clutch for an automatic transmission according to claim 1, wherein a first oil passage (24) for communicating with the master piston chamber (50) and a second oil passage (25) for communicating with the balance piston chamber (60) are provided on the inner hub (20).
10. The clutch for an automatic transmission according to claim 1, characterized in that the return means includes a return spring (70) disposed inside the balance piston chamber (60), one end of the return spring (70) being supported on a side wall of the main piston (30) and the other end being supported on an inner wall of the inner hub (20).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021208582.XU CN213064401U (en) | 2020-06-24 | 2020-06-24 | Clutch for automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021208582.XU CN213064401U (en) | 2020-06-24 | 2020-06-24 | Clutch for automatic transmission |
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| Publication Number | Publication Date |
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| CN213064401U true CN213064401U (en) | 2021-04-27 |
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| CN202021208582.XU Active CN213064401U (en) | 2020-06-24 | 2020-06-24 | Clutch for automatic transmission |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113251084A (en) * | 2021-07-08 | 2021-08-13 | 盛瑞传动股份有限公司 | Mounting structure of piston assembly for transmission and transmission |
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2020
- 2020-06-24 CN CN202021208582.XU patent/CN213064401U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113251084A (en) * | 2021-07-08 | 2021-08-13 | 盛瑞传动股份有限公司 | Mounting structure of piston assembly for transmission and transmission |
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