WO2021253617A1 - 离合器分离副缸 - Google Patents

离合器分离副缸 Download PDF

Info

Publication number
WO2021253617A1
WO2021253617A1 PCT/CN2020/110328 CN2020110328W WO2021253617A1 WO 2021253617 A1 WO2021253617 A1 WO 2021253617A1 CN 2020110328 W CN2020110328 W CN 2020110328W WO 2021253617 A1 WO2021253617 A1 WO 2021253617A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
clutch release
elastic member
auxiliary cylinder
housing
Prior art date
Application number
PCT/CN2020/110328
Other languages
English (en)
French (fr)
Inventor
徐志力
Original Assignee
舍弗勒技术股份两合公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 舍弗勒技术股份两合公司 filed Critical 舍弗勒技术股份两合公司
Priority to CN202080099917.5A priority Critical patent/CN115427700A/zh
Priority to EP20940733.7A priority patent/EP4166807A1/de
Publication of WO2021253617A1 publication Critical patent/WO2021253617A1/zh

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F16D25/083—Actuators therefor

Definitions

  • the invention relates to the field of vehicle technology. Specifically, the present invention relates to a clutch release auxiliary cylinder for a motor vehicle.
  • a clutch release auxiliary cylinder such as a concentric slave cylinder (CSC)
  • CSC concentric slave cylinder
  • the clutch release auxiliary cylinder has a housing formed as an annular cylinder, and the housing is arranged around the transmission input shaft.
  • An annular piston that can slide axially is arranged in the housing, and the release bearing of the clutch is carried on the piston.
  • CN 210661115 U discloses a typical two-way piston clutch assembly.
  • the separating auxiliary cylinder has two hydraulic chambers opposite in the axial direction, and a piston is installed in each hydraulic chamber.
  • the technical problem to be solved by the present invention is to provide a clutch release auxiliary cylinder that can reliably provide preload.
  • the clutch release auxiliary cylinder includes a housing, a piston and a release bearing.
  • the housing has an inner cavity with an open end and a closed end opposite to each other in the axial direction.
  • the piston is installed in the inner cavity and can slide along the inner cavity between a retracted position near the closed end and an extended position away from the closed end.
  • the release bearing has a first bearing ring that abuts against the piston in the axial direction and a second bearing ring that faces away from the piston.
  • the first bearing ring and the end of the piston facing away from the closed end can be relatively fixedly connected in the axial direction.
  • the clutch release auxiliary cylinder also includes an elastic member installed on the housing.
  • the elastic member When the piston is in the retracted position, the elastic member abuts between the first bearing ring and the housing in the axial direction or abuts against the housing in the axial direction.
  • the release bearing in the retracted position can be provided with an axial pre-tightening force.
  • the pre-tightening force of the release bearing is provided by the elastic part installed on the housing, which not only simplifies the structure and installation method of the components, but also because the elastic part only contacts the piston or the release bearing in the retracted position, there is no need to adjust the elasticity.
  • the elastic force of the parts is particularly accurately controlled, and there is no need to precisely limit the installation tolerances, and at the same time, it will not interfere with and affect the normal operation of the clutch. Therefore, the production and installation costs can be greatly reduced, and the reliability is higher.
  • the inner cavity may be annular.
  • the clutch release auxiliary cylinder may include an annular elastic member or a plurality of elastic members arranged at intervals in the circumferential direction.
  • the clutch release sub-cylinder has an annular housing, and the clutch release sub-cylinder includes a plurality of independent and separated pistons, and correspondingly, the housing is provided for accommodating the plurality of independent and separated pistons.
  • the multiple independent and separated internal cavities are roughly like a wheel; the cross-sectional shape of the piston and the internal cavity can be any desired shape such as a circle, an ellipse, and a quadrilateral.
  • the elastic element preferably adopts an independent and separate elastic element, and the elastic element can be located between the housing and the first bearing ring, or between the piston and the housing.
  • the housing may have a radially inner side or a radially outer side of the open end of the inner cavity.
  • An annular step portion has a radial surface extending in the radial direction and an axial surface extending in the axial direction, and the elastic member may be installed on the step portion and abut against the radial surface of the step portion in the axial direction.
  • the elastic member abuts between the radial surface of the stepped portion and the first bearing ring of the release bearing in the axial direction.
  • the elastic member may be a wave ring, a coil spring or a disc spring or a rubber member that at least partially surrounds the step portion.
  • the wave ring can be, for example, wave springs of various specifications commonly used in the industry, or other wave-shaped elastic parts. This component has a simple structure and low cost.
  • the elastic member can squeeze the axially extending axial surface of the stepped portion in the radial direction by elastic deformation, so the radial limit of the elastic member is realized by the axial surface of the stepped portion. Bit.
  • the housing may further have a limiting portion protruding radially from the axial surface of the stepped portion, and the radial surface of the stepped portion and the limiting portion respectively face the elastic member from both sides in the axial direction. Perform a limit.
  • the first bearing ring may extend toward the stepped portion on one side in the radial direction, so as to abut the elastic member in the axial direction at the retracted position, and the first bearing ring is on the other side in the radial direction.
  • the connection with the piston can be, for example, snapped into a groove on the piston, so that the first bearing ring and the piston are relatively fixedly connected, particularly in the axial direction.
  • the elastic element can be installed inside the cavity, and when the piston is in the retracted position, the elastic element abuts against Between the piston and the closed end.
  • the elastic member may be constrained in contact with the closed end.
  • the housing may have a guide member, such as a guide post, which extends axially from the closed end of the inner cavity toward the piston, and the elastic member may be guided by the guide member.
  • a guide member such as a guide post
  • an elastic member in the form of a coil spring may surround the corresponding guide member.
  • the guide post can be cylindrical, for example, which can provide radial and axial guidance for the helical spring.
  • the elastic member can be a coil spring, a wave ring, a disc spring or a rubber part or other forms of elastic parts.
  • Figure 1 shows a schematic diagram of a motor vehicle with a clutch release auxiliary cylinder according to the present invention
  • FIG. 3 shows a partial cross-sectional view of the clutch release auxiliary cylinder according to the first embodiment of the present invention
  • FIG. 4 shows a perspective view of the wave ring of the clutch release auxiliary cylinder according to the first embodiment of the present invention
  • Figure 5 shows a partial enlarged view of the clutch release auxiliary cylinder according to the first embodiment of the present invention
  • Fig. 6 shows a perspective cross-sectional view of a clutch release auxiliary cylinder according to a second embodiment of the present invention
  • Figure 7 shows an exploded view of a clutch release auxiliary cylinder according to a second embodiment of the present invention.
  • Figure 8 shows a partial cross-sectional view of a clutch release auxiliary cylinder according to a second embodiment of the present invention.
  • Fig. 9 shows a partial cross-sectional view of a clutch release auxiliary cylinder according to a third embodiment of the present invention.
  • a clutch release auxiliary cylinder for a motor vehicle in particular a centering type release auxiliary cylinder for a hydraulic release system of a clutch system of a motor vehicle.
  • the clutch release auxiliary cylinder 1 is a part of the hydraulic release system 2.
  • the hydraulic release system 2 acts on the clutch release sub-cylinder 1 so that the friction clutch (not shown) of the clutch system 3 can be hydraulically actuated. This actuation process can be accomplished by an actuator (not shown) controlled by the control unit, or it can be manually implemented by the driver using a clutch pedal.
  • the clutch release auxiliary cylinder 1 transmits the required release force to the friction clutch or its lever system, such as a leaf spring or an actuating lever, through a release bearing.
  • the tensioning method of the lever system and the clutch housing determines whether the friction clutch is engaged. Therefore, when the release bearing acting on the lever end of the lever system is acted on, the friction clutch can be separated or engaged under the push of the piston.
  • the transmission input shaft that is connected to the friction clutch torsionally can transmit the torque of the internal combustion engine to the transmission (not shown) through the clutch disc, and then to the driving wheels of the vehicle.
  • FIG. 2 shows a first embodiment of the clutch release auxiliary cylinder 1 according to the present invention.
  • the clutch release sub-cylinder 1 according to the first embodiment includes a housing 10, a piston 20, a release bearing 30, and an elastic member.
  • the housing 10 has an annular structure as a whole.
  • the housing 10 has two annular cavities 11 facing each other in the axial direction.
  • Each inner cavity 11 extends in the axial direction, and each has an open end and a closed end opposite to each other in the axial direction.
  • the closed ends of the two cavities 11 are arranged opposite to each other, and the open ends are arranged opposite to each other.
  • the two inner cavities 11 are basically mirror-symmetrical structures, therefore, only one of them is used as an example for description. However, it should be understood that the following description of any one of the inner cavity 11 and its related parts is also applicable to the other inner cavity 11 and its related parts.
  • the clutch release sub-cylinder 1 is shown as a two-way clutch release sub-cylinder with two inner cavities 11 opposite in the axial direction, this is not limitative.
  • the various embodiments of the present invention are also applicable to a one-way clutch release sub-cylinder, a plurality of clutch release sub-cylinders arranged in parallel in the radial direction, or other suitable types of clutch release sub-cylinders.
  • FIG. 3 shows an enlarged view of the clutch release auxiliary cylinder 1 in the inner cavity 11 in FIG. 2.
  • the annular piston 20 is axially inserted into the inner cavity 11 from the open end of the inner cavity 11, and can slide along the inner cavity 11 between a retracted position close to the closed end and an extended position away from the closed end.
  • An annular seal 70 is respectively provided on the radially inner side and the radially outer side of the piston 20.
  • the sealing member 70 may be, for example, an elastic sealing ring, which abuts between the piston 20 and the side wall of the inner cavity 11 in the radial direction, thereby sealing the hydraulic cavity formed between the piston 20 and the inner cavity 11 from the outside.
  • the release bearing 30 is coaxially mounted on the end of the piston 20 facing away from the closed end.
  • the release bearing 30 is schematically shown as a thrust bearing, which includes a first bearing ring 31, a second bearing ring 32 and a plurality of rollers 33.
  • the first bearing ring 31 and the second bearing ring 32 are arranged coaxially.
  • a plurality of rollers 33 are rotatably arranged between the two bearing rings, so that the two bearing rings can rotate relative to each other.
  • the first bearing ring 31 abuts against the piston 20 in the axial direction, and the second bearing ring 32 faces away from the piston 20.
  • the first bearing ring 31 may be a separate component or formed by the end surface of the piston 20; the release bearing 30 may also be other types of bearings.
  • the radially outer side of the end of the piston 20 may be formed with a convex portion, in which a locking groove 21 that opens toward the radially inner side is formed, and the radially outer side of the first bearing ring 31 is inserted In the locking groove 21, it is relatively fixedly connected with the piston 20 in the axial direction and the radial direction.
  • the clamping groove 21 can preferably be interference fit with the first bearing ring 31, so as to further realize the circumferential fixation of the first bearing ring 31.
  • this installation method is only illustrative, and the first bearing ring 31 may also be fixed on the piston 20 in other ways, for example, by various force fit and shape fit installation methods, or may also be integrally formed with the piston 20.
  • the housing 10 is formed with a stepped portion 12 on the radially inner side of the open end of the inner cavity 11.
  • the step portion 12 has an axial surface extending axially and a radial surface extending radially.
  • the axial surface extends from the radially inner edge of the radial surface toward a direction away from the closed end.
  • the first bearing ring 31 extends toward the radially inner side to above the radial surface of the stepped portion 12.
  • the elastic member is installed on the stepped portion 12.
  • the elastic member may be a wave ring 40.
  • the sheet material (which may be metal or other materials) constituting the wave ring 40 undulates alternately toward both sides in the axial direction while extending in the circumferential direction, thereby forming a wave-like structure.
  • the wave ring 40 extends around the center axis of the housing 10 and abuts on the radial surface of the step portion 12 in the axial direction.
  • the first bearing ring 31 abuts against the wave ring 40 in the axial direction from the direction opposite to the stepped portion 12. Therefore, at this time, the wave ring 40 abuts against the stepped portion 12 in the axial direction.
  • the release bearing 30 can be provided with an axial pre-tightening force.
  • the wave ring 40 may press the axial surface of the step portion 12 in the radial direction by elastic deformation. At this time, the axial surface of the stepped portion 12 provides a radial limit function for the wave ring 40.
  • a limit portion 13 may also be formed on the axial surface of the stepped portion 12. As shown in FIG. 5, the limiting portion 13 extends radially from the axial surface of the stepped portion 12 to above the wave ring 40, thereby defining the wave ring 40 from both sides in the axial direction together with the radial surface of the stepped portion 12 Axial position.
  • the wave ring 40 can also be replaced by ring-shaped disc springs, coil springs, rubber rings and other ring-shaped elastic members.
  • the elastic member may also be a plurality of separate smaller elastic members arranged at intervals in the circumferential direction, for example, a plurality of coil springs, leaf springs, leaf springs or rubber parts arranged at intervals in the circumferential direction.
  • the stepped portion 12 may also be formed on the radially outer side of the open end of the inner cavity 11. In this case, the first bearing ring 31 may be fixedly connected to the piston 20 at the radially inner side, and abut the elastic member at the radially outer side.
  • FIGS. 6 to 8 show a second embodiment of the clutch release auxiliary cylinder 1 according to the present invention.
  • the clutch release sub-cylinder 1 according to the second embodiment also includes a housing 10, a piston 20, a release bearing 30 and an elastic member.
  • the following will mainly describe the differences between the second embodiment and the first embodiment with reference to FIGS. 6 to 8.
  • the clutch release sub-cylinder 1 has a plurality of elastic members. Unlike the wave ring 40 arranged between the housing 10 and the release bearing 30 around the inner cavity 11 in the first embodiment, the elastic member in the second embodiment is installed inside the inner cavity 11 of the housing 10 and runs along Spaced in the circumferential direction. One axial end of each elastic member abuts against the closed end of the inner cavity 11, and the other axial end abuts against the piston 20, so that the piston 20 applies a pretension force to the release bearing 30 in an elastic loading manner.
  • the clutch release auxiliary cylinder 1 may include at least three, preferably three to nine elastic members. These elastic members may preferably be uniformly arranged in the inner cavity 11 along the circumferential direction. In the second embodiment, these elastic members can preferably be designed in the form of a coil spring 50. These coil springs 50 can be seen more clearly from FIGS. 7 and 8.
  • FIG. 8 shows a partial cross-sectional view of the clutch release sub-cylinder 1 according to the second embodiment.
  • the clutch release auxiliary cylinder 1 of the second embodiment is also schematically shown as a two-way clutch release auxiliary cylinder, and therefore has two pistons 20 opposed to each other in the axial direction.
  • the two pistons 20 can be hydraulically actuated in axial directions opposite to each other.
  • the piston 20 on the right is in the extended position, and the other piston 20 on the left is in the retracted position.
  • One end of the elastic member in the form of a coil spring 50 abuts against the closed end of the inner cavity 11, and the other axial end can abut against the end of the piston 20 facing the closed end, so that it is particularly on the left side of FIG. 8 In the retracted position shown, the elastic member can apply an axial pretension force to the release bearing 30 through the piston 20.
  • the housing 10 may further include a plurality of guide posts 14.
  • the guide post 14 may be a cylindrical structure, which is fixed on the closed end of the inner cavity 11 and extends axially toward the open end.
  • Each coil spring 50 respectively surrounds the radially outer side of the corresponding guide post 14 so as to be guided by the guide post 14 in the axial direction and the radial direction at the same time.
  • the guide post 14 may be integrally formed with the housing 10.
  • the guide post 14 can extend into the cavity at the bottom of the piston 20, and its axial extension length can be especially designed not to affect the movement of the piston 20 to the retracted position shown on the left in FIG. 8.
  • the first bearing ring 31 of the release bearing 30 can be mounted on the end of the piston 20 facing away from the closed end in a similar manner to the first embodiment.
  • the elastic force of the elastic member only needs to provide a pre-tensioning force for the release bearing 30 at the retracted position, which is shown in the left part of FIG. 8.
  • the piston 20 In this retracted position, the piston 20 is in its fully retracted operating position, but due to the elastic force of the elastic member, the piston 20 will not hit the closed end of the inner cavity 11 in the axial direction.
  • the clutch release sub-cylinder 1 is actuated under the action of hydraulic fluid, the release bearing 30 can directly obtain the pressing force from the hydraulic system.
  • the coil spring 50 can also be replaced by a leaf spring or other similar elastic components.
  • the clutch release sub-cylinder 1 uses a plurality of coil springs 50 arranged at intervals in the circumferential direction in the inner cavity 11 to provide pretensioning force to the release bearing 30.
  • a single ring-shaped elastic member such as a coil spring, a disc spring or a leaf spring, a rubber member, or a wave spring, instead of a plurality of coil springs.
  • the single ring-shaped elastic member is centered in the axial direction of the housing 10. The line is the center line.
  • FIG. 9 an annular disc spring 60 is installed at the closed end of the inner cavity 11 and surrounds the inner cavity 11 in the circumferential direction. Except for this, the implementation of the third embodiment is basically the same as that of the second embodiment.
  • the release bearing 30 when the piston 20 is in the retracted position, the release bearing 30 is provided with a pre-tightening force through an elastic member installed on the housing 10. It is only necessary to ensure that the axial force applied by the clutch to the second bearing ring 32 at this time is greater than or equal to the elastic force of the elastic member, and it is not necessary to precisely control the magnitude of the pretension force applied by the elastic member. Therefore, this kind of clutch release auxiliary cylinder has simple requirements for elastic parts and is easy to realize. This can reduce production costs, and meet the control requirements of the clutch release system, while also having high reliability.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

一种离合器分离副缸，包括壳体（10）、活塞（20）和分离轴承（30），壳体（10）具有内腔（11），内腔（11）具有沿轴向相对的开放端和封闭端，活塞（20）安装在内腔（11）中并且能够沿内腔（11）在缩回位置与伸出位置之间滑动，分离轴承（30）具有沿轴向抵接活塞（20）的第一轴承圈（31）和背向活塞（20）的第二轴承圈（32），还包括安装在壳体（10）上的弹性件，当活塞（20）处于缩回位置时，弹性件沿轴向抵接在第一轴承圈（31）与壳体（10）之间或者沿轴向抵接在活塞（20）与壳体（10）之间。

Description

离合器分离副缸 技术领域
本发明涉及车辆技术领域。具体地，本发明涉及一种用于机动车辆的离合器分离副缸。
背景技术
在机动车辆的液压离合系统中，通常在离合器踏板和离合器之间设置有离合器分离副缸，比如对中式分离副缸(concentric slave cylinder，CSC)。离合器分离副缸具有形成为环形缸的壳体，该壳体围绕变速器输入轴设置。在壳体中设置有可以轴向滑动的环形活塞，离合器的分离轴承承载在该活塞上。当通过液压管线向活塞施加液压载荷时，活塞产生的预紧载荷可以作用于分离轴承，从而操作离合器。
例如，CN 210661115 U公开了一种典型的双向活塞式离合器总成。在这种离合器中，分离副缸具有沿轴向相对的两个液压腔，每个液压腔中分别安装有一个活塞。
在这种离合器分离副缸中，当活塞处于缩回位置时，需要精准地控制液压压力水平来向分离轴承提供轴向的预紧力。但当前的液压泵系统通常无法满足这种精度需求，而如果出现控制误差，则有可能导致离合器不当地接合或分离。
发明内容
因此，本发明需要解决的技术问题是，提供一种能够可靠地提供预紧力的离合器分离副缸。
上述技术问题通过根据本发明的一种离合器分离副缸而得到解决。该离合器分离副缸包括壳体、活塞和分离轴承。壳体具有内腔，该内腔具有沿轴向相对的开放端和封闭端。活塞安装在内腔中并且能够沿内腔在靠近 封闭端的缩回位置与远离封闭端的伸出位置之间滑动。分离轴承具有沿轴向抵接活塞的第一轴承圈和背向活塞的第二轴承圈，特别地，第一轴承圈与活塞的背向封闭端的一端可以在轴向上相对固定地连接。其中，该离合器分离副缸还包括安装在壳体上的弹性件，当活塞处于缩回位置时，弹性件沿轴向抵接在第一轴承圈与壳体之间或者沿轴向抵接在活塞与壳体之间，从而能够为处于缩回位置的分离轴承提供轴向的预紧力。通过安装在壳体上的弹性件来为分离轴承提供预紧力，不仅使得部件结构和安装方式得以简化，而且由于弹性件仅在缩回位置才会接触活塞或分离轴承，因此不需要对弹性件的弹性力进行特别精准的控制，并且不需要精确地限定安装公差，同时不会对离合器的正常操纵过程产生干扰和影响，因此可以大大降低生产和安装成本，并且可靠性更高。
根据本发明的一个优选实施例，由于离合器分离副缸通常具有环形的壳体，因此内腔可以为环形。该离合器分离副缸可以包括一个环形的弹性件或沿周向间隔布置的多个弹性件。
替代地，离合器分离副缸具有环形的壳体，而该离合器分离副缸包括有多个独立的、分离的活塞，相应的在壳体上设置有用于容纳所述多个独立的、分离的活塞的多个独立的、分离的内腔，大致如转轮状；活塞和内腔的横截面的形状可以为圆形、椭圆形、四边形等任意所需的形状。在这种结构下，弹性件优选地采用独立的、分离的弹性件，弹性件可以位于壳体与第一轴承圈之间，也可以位于活塞与壳体之间。
根据本发明的另一优选实施例，对于弹性件抵接在分离轴承的第一轴承圈与壳体之间的情况，壳体可以具有形成在内腔的开放端的径向内侧或径向外侧的环形台阶部，该台阶部具有沿径向延伸的径向表面和沿轴向延伸的轴向表面，而弹性件可以安装在台阶部上并且沿轴向抵接台阶部的径向表面。在这种情况下，当活塞处于缩回位置时，弹性件沿轴向抵接在台阶部的径向表面与分离轴承的第一轴承圈之间。在这种情况下，弹性件可以为至少部分地环绕台阶部的波形环、螺旋弹簧或碟形弹簧或橡胶部件。波形环例如可以是工业中常见的各种规格的波形弹簧，或者其他的波形的弹性件。这种部件结构简单且成本低廉。
根据本发明的另一优选实施例，弹性件可以通过弹性变形沿径向挤压台阶部的沿轴向延伸的轴向表面，因此通过台阶部的轴向表面实现了对弹性件的径向限位。
根据本发明的另一优选实施例，壳体还可以具有从台阶部的轴向表面沿径向突起的限位部，台阶部的径向表面与限位部分别从轴向两侧对弹性件进行限位。
根据本发明的另一优选实施例，第一轴承圈可以在径向一侧朝向台阶部延伸，从而能够在缩回位置沿轴向抵接弹性件，并且第一轴承圈在径向另一侧与活塞连接，例如可以卡合到活塞上的卡槽中，从而使第一轴承圈与活塞特别是在轴向上相对固定地连接在一起。
根据本发明的一个替代实施例，对于弹性件抵接在活塞与壳体之间的情况，弹性件可以安装在内腔的内部，当活塞处于缩回位置时，弹性件沿轴向抵接在活塞与封闭端之间。
在上述情况下，根据本发明的一个优选实施例，弹性件可以以与封闭端相接触的方式被约束。优选地，壳体可以具有引导部件，例如引导柱，该引导部件从内腔的封闭端朝向活塞轴向延伸，弹性件可以被引导部件引导，例如螺旋弹簧形式的弹性件可以环绕在相应的引导柱的径向外侧。引导柱例如可以为圆柱形，其可以为螺旋弹簧提供径向和轴向的引导。弹性件可以为螺旋弹簧、波形环、碟形弹簧或橡胶部件或其他形式的弹性部件。
附图说明
以下结合附图进一步描述本发明。图中以相同的附图标记来代表功能相同的元件。其中：
图1示出具有根据本发明的离合器分离副缸的机动车辆的示意图；
图2示出根据本发明的第一实施例的离合器分离副缸的剖视图；
图3示出根据本发明的第一实施例的离合器分离副缸的局部剖视图；
图4示出根据本发明的第一实施例的离合器分离副缸的波形环的立体图；
图5示出根据本发明的第一实施例的离合器分离副缸的局部放大图；
图6示出根据本发明的第二实施例的离合器分离副缸的立体剖视图；
图7示出根据本发明的第二实施例的离合器分离副缸的分解图；
图8示出根据本发明的第二实施例的离合器分离副缸的局部剖视图；和
图9示出根据本发明的第三实施例的离合器分离副缸的局部剖视图。
具体实施方式
以下将结合附图描述根据本发明的离合器分离副缸的具体实施方式。下面的详细描述和附图用于示例性地说明本发明的原理，本发明不限于所描述的优选实施例，本发明的保护范围由权利要求书限定。
根据本发明的实施例，提供了一种用于机动车辆的离合器分离副缸，特别是用于机动车辆的离合系统的液压分离系统的对中式分离副缸。如图1所述，该离合器分离副缸1是液压分离系统2的一部分。液压分离系统2作用在离合器分离副缸1上，从而能够对离合系统3的摩擦式离合器(未示出)进行液压致动。这种致动过程可以通过由控制单元控制的致动器(未示出)来完成，或者也可以由驾驶员使用离合器踏板来手动实现。离合器分离副缸1通过分离轴承将所需的分离力传递至摩擦离合器或者其杠杆系统，例如板簧或致动杠杆等。杠杆系统与离合器壳体的张紧方式决定了摩擦离合器是否接合。因此，当作用在杠杆系统的杠杆末端上的分离轴承受到作用时，摩擦离合器可以在活塞的推动下分离或接合。当摩擦离合器处于接合状态时，与摩擦离合器抗扭连接的变速器输入轴可以将内燃机的扭矩通过离合器盘传递至变速器(未显示)，继而传递至车辆的驱动轮。
下面将参照图2至图9详细描述根据本发明的离合器分离副缸的多个不同实施例。以上的总体介绍对于以下描述的各个不同实施例均适用。
图2至图5示出了根据本发明的离合器分离副缸1的第一实施例。如图2所示，根据第一实施例的离合器分离副缸1包括壳体10、活塞20、分离轴承30和弹性件。
壳体10整体呈环形结构。壳体10具有沿轴向相对的两个环形的内腔11。每个内腔11沿轴向延伸，并且各自具有沿轴向相对的开放端和封闭 端。两个内腔11的封闭端相向地布置，而开放端相背地布置。这两个内腔11基本是镜像对称的结构，因此，下面仅以其中一个为例来进行说明。但应当理解，以下对于其中任意一个内腔11及其相关部件的说明也同样地适用于另一个内腔11及其相关部件。另外，在本发明的各个实施例中，虽然该离合器分离副缸1示出为具有沿轴向相对的两个内腔11的双向离合器分离副缸，但这并非限制性的。本发明的各个实施例也适用于单向的离合器分离副缸、径向上平行排布的多个离合器分离副缸或其他合适类型的离合器分离副缸。
图3示出了图2中的离合器分离副缸1在内腔11处的放大图。如图3所示，环形的活塞20从内腔11的开放端沿轴向插入内腔11中，并且能够沿内腔11在靠近封闭端的缩回位置与远离封闭端的伸出位置之间滑动。在活塞20的径向内侧和径向外侧分别设置有一个环形的密封件70。密封件70例如可以是弹性的密封圈，其沿径向抵接在活塞20与内腔11的侧壁之间，从而将活塞20与内腔11之间形成的液压腔相对于外界密封。
分离轴承30同轴地安装在活塞20的背向封闭端的一端上。在本发明的实施例中，分离轴承30示意性地示出为推力轴承，其包括第一轴承圈31、第二轴承圈32和多个滚子33。第一轴承圈31和第二轴承圈32同轴地布置。多个滚子33可滚动地布置在两个轴承圈之间，使得两个轴承圈能够进行相对转动。第一轴承圈31沿轴向抵接在活塞20上，而第二轴承圈32背向活塞20。需要注意的是，这里的轴承的自身结构不构成对本发明的限制，第一轴承圈31可以是单独的部件，也可以由活塞20的端面构成；分离轴承30也可以是其他类型的轴承。
如图3所示，活塞20的端部的径向外侧可以形成有凸起部分，在该凸起部分中形成有朝向径向内侧开口的卡槽21，第一轴承圈31的径向外侧插入卡槽21中，从而在轴向和径向上与活塞20相对固定地连接在一起。卡槽21优选地可以与第一轴承圈31过盈配合，从而进一步实现对第一轴承圈31的周向固定。但是，这种安装方式仅是示意性的，第一轴承圈31也可以通过其他方式固定在活塞20上，例如通过各种力配合、形状配合的安装方式，或者也可以与活塞20一体形成。
相应地，壳体10在内腔11的开放端的径向内侧形成有台阶部12。台阶部12具有轴向延伸的轴向表面和径向延伸的径向表面，轴向表面从径向表面的径向内边缘开始朝向远离封闭端的方向延伸。第一轴承圈31朝向径向内侧延伸到台阶部12的径向表面的上方。弹性件安装在台阶部12上。
如图4所示，在第一实施例中，弹性件可以是波形环40。构成波形环40的片材(可以为金属或其他材料)在沿周向延伸的同时向着轴向两侧交替起伏，从而形成波状结构。波形环40环绕壳体10的中心轴线延伸并且沿轴向抵接在台阶部12的径向表面上。同时，当活塞20运动到缩回位置时，第一轴承圈31从与台阶部12相对的方向沿轴向抵接波形环40，因此，此时波形环40沿轴向抵接在台阶部12与第一轴承圈31之间，从而能够为分离轴承30提供轴向的预紧力。
为了更好地安装波形环40，波形环40可以通过弹性变形沿径向挤压台阶部12的轴向表面。此时，台阶部12的轴向表面为波形环40提供了径向限位作用。为了在分离轴承30不抵接波形环40时定位波形环40，在台阶部12的轴向表面上还可以形成有限位部13。如图5所示，限位部13从台阶部12的轴向表面开始径向延伸到波形环40的上方，从而与台阶部12的径向表面一起分别从轴向两侧限定波形环40的轴向位置。
在第一实施例中，波形环40也可以由环形的碟形弹簧、螺旋弹簧、橡胶环等其他环形的弹性件来代替。另外，弹性件也可以是沿周向间隔布置的多个单独的较小的弹性件，例如沿周向间隔布置的多个螺旋弹簧、板簧、片弹簧或橡胶部件等。同时，在第一实施例中，台阶部12也可以形成在内腔11的开放端的径向外侧。在这种情况下，第一轴承圈31可以在径向内侧处与活塞20固定连接，并且在径向外侧处抵接弹性件。
图6至图8示出了根据本发明的离合器分离副缸1的第二实施例。如图6所示，根据第二实施例的离合器分离副缸1同样包括壳体10、活塞20、分离轴承30和弹性件。下面将参照图6至图8主要关于第二实施例与第一实施例的不同之处进行说明。
如图7所示，在第二实施例中，离合器分离副缸1具有多个弹性件。 不同于第一实施例中环绕内腔11布置在壳体10与分离轴承30之间的波形环40，第二实施例中的弹性件安装在壳体10的内腔11的内部，并且沿着周向方向间隔分布。每个弹性件的轴向一端抵接在内腔11的封闭端上，而轴向另一端抵接在活塞20上，使得活塞20以弹性加载的方式向分离轴承30施加预紧力。根据优选的实施例，离合器分离副缸1可以包括至少三个、优选在三个至九个弹性件。这些弹性件优选地可以沿着周向方向均匀地布置在内腔11中。在第二实施例中，这些弹性件优选地可以设计成螺旋弹簧50的形式。从图7和图8中可以更清楚地看到这些螺旋弹簧50。
图8示出了根据第二实施例的离合器分离副缸1的局部剖视图。如图8所示，与第一实施例类似，第二实施例的离合器分离副缸1同样示意性地示出为双向离合器分离副缸，并且因此具有两个沿轴向相对的活塞20，这两个活塞20可以在彼此相对的轴向方向上液压致动。在图8中，右侧的活塞20处于伸出位置，而左侧的另一活塞20则处于缩回位置。
螺旋弹簧50形式的弹性件的轴向一端抵接在内腔11的封闭端上，而轴向另一端则可以抵接在活塞20的朝向封闭端的端部上，使得特别是在图8左侧所示的缩回位置时，弹性件能够通过活塞20向分离轴承30施加轴向的预紧力。
如图8所示，壳体10还可以包括多个引导柱14。引导柱14可以是圆柱形结构，其固定在内腔11的封闭端上并且朝向开放端沿轴向延伸。每个螺旋弹簧50分别环绕在相应的引导柱14的径向外侧，从而同时在轴向方向和径向方向上受到引导柱14的引导。优选地，引导柱14可以与壳体10一体形成。此外，引导柱14可以延伸到活塞20的底部的空腔中，并且其轴向延伸长度特别是可以设计为不影响活塞20运动到图8中左侧所示的缩回位置。
分离轴承30的第一轴承圈31可以通过与第一实施例类似的方式安装在活塞20的背向封闭端的端部上。
弹性件的弹性力仅需要在缩回位置处为分离轴承30提供预紧力，该缩回位置在图8的左侧部分中示出。在该缩回位置处，活塞20处于其完全缩回的操作位置，但是由于弹性件的弹性力作用，活塞20不会沿轴向 撞击到内腔11的封闭端上。一旦离合器分离副缸1在液压流体的作用下发生致动，分离轴承30就可以直接从液压系统获得压紧力。
在第二实施例中，螺旋弹簧50也可以由片弹簧或其他类似的弹性部件来代替。
在图6至图8所示的第二实施例中，离合器分离副缸1使用沿周向间隔布置在内腔11中的多个螺旋弹簧50来向分离轴承30提供预紧力。但是，也可以使用单个环形的弹性部件，例如螺旋弹簧、碟形弹簧或板簧、橡胶部件、波形弹簧来代替多个螺旋弹簧，所述单个的环形的弹性部件以壳体10的轴向中心线为中心线。这在图9所示的第三实施例中示意性地示出。如图9所示，环形的碟形弹簧60安装在内腔11的封闭端处，并且沿着周向方向环绕内腔11。除此之外，第三实施例的实施方式基本与第二实施例相同。
在根据本发明的离合器分离副缸中，当活塞20处于缩回位置时，通过安装在壳体10上的弹性件来为分离轴承30提供预紧力。只需要确保此时离合器施加到第二轴承圈32的轴向力大于或等于弹性件的弹性力即可，而不必需要精确地控制弹性件所施加的预紧力大小。因此，这种离合器分离副缸对弹性件的要求简单，容易实现。这能够降低了生产成本，并且满足离合器分离系统的控制要求，同时还具有很高的可靠性。
虽然在上述说明中示例性地描述了可能的实施例，但是应当理解到，仍然通过所有已知的和此外技术人员容易想到的技术特征和实施方式的组合存在大量实施例的变化。此外还应该理解到，示例性的实施方式仅仅作为一个例子，这种实施例绝不以任何形式限制本发明的保护范围、应用和构造。通过前述说明更多地是向技术人员提供一种用于转化至少一个示例性实施方式的技术指导，其中，只要不脱离权利要求书的保护范围，便可以进行各种改变，尤其是关于所述部件的功能和结构方面的改变。
附图标记表
1   离合器分离副缸
2   液压分离系统
3   离合系统
4   机动车辆
10  壳体
11  内腔
12  台阶部
13  限位部
14  引导柱
20  活塞
21  卡槽
30  分离轴承
31  第一轴承圈
32  第二轴承圈
33  滚子
40  波形环
50  螺旋弹簧
60  碟形弹簧
70  密封件

Claims (11)

  1. 一种离合器分离副缸，包括壳体(10)、活塞(20)和分离轴承(30)，所述壳体(10)具有内腔(11)，所述内腔(11)具有沿轴向相对的开放端和封闭端，所述活塞(20)安装在所述内腔(11)中并且能够沿所述内腔(11)在靠近所述封闭端的缩回位置与远离所述封闭端的伸出位置之间滑动，所述分离轴承(30)具有沿轴向抵接所述活塞(20)的第一轴承圈(31)和背向所述活塞(20)的第二轴承圈(32)，
    其特征在于，
    所述离合器分离副缸还包括安装在所述壳体(10)上的弹性件，当所述活塞(20)处于所述缩回位置时，所述弹性件沿轴向抵接在所述第一轴承圈(31)与所述壳体(10)之间或者沿轴向抵接在所述活塞(20)与所述壳体(10)之间。
  2. 根据权利要求1所述的离合器分离副缸，其特征在于，所述内腔(11)为环形，所述离合器分离副缸包括一个环形的弹性件或沿周向间隔布置的多个所述弹性件；或者，
    所述内腔为沿周向间隔布置的、独立分离的多个腔体，所述离合器分离副缸包括沿周向间隔布置的多个所述弹性件。
  3. 根据前述权利要求2所述的离合器分离副缸，其特征在于，当所述内腔为沿周向间隔布置的、独立且分离的多个腔体时，腔体的横截面为圆形、椭圆形或多边形。
  4. 根据前述权利要求中任一项所述的离合器分离副缸，其特征在于，所述壳体(10)具有形成在所述内腔(11)的所述开放端的环形台阶部(12)，所述台阶部(12)具有沿径向延伸的径向表面，所述弹性件安装在所述台阶部(12)上并且沿轴向抵接所述台阶部(12)的径向表面。
  5. 根据前述权利要求中任一项所述的离合器分离副缸，其特征在于，所述弹性件为至少部分地环绕所述台阶部(12)的螺旋弹簧、波形环(40)、碟形弹簧或橡胶部件。
  6. 根据前述权利要求中任一项的离合器分离副缸，其特征在于，所述 弹性件通过弹性变形沿径向挤压所述台阶部(12)的沿轴向延伸的轴向表面。
  7. 根据前述权利要求中任一项的离合器分离副缸，其特征在于，所述壳体(10)还具有从所述台阶部(12)的轴向表面沿径向突起的限位部(13)，所述台阶部(12)的径向表面与所述限位部(13)分别从轴向两侧对所述弹性件进行限位。
  8. 根据前述权利要求1至3中任一项所述的离合器分离副缸，其特征在于，所述弹性件安装在所述内腔(11)的内部，当所述活塞(20)处于所述缩回位置时，所述弹性件沿轴向抵接在所述活塞(20)与所述封闭端之间。
  9. 根据前述权利要求8所述的离合器分离副缸，其特征在于，所述弹性件以与所述封闭端相接触的方式被约束。
  10. 根据权利要求8或9所述的离合器分离副缸，其特征在于，所述壳体(10)具有引导部件，所述引导部件从所述封闭端朝向所述活塞(20)轴向延伸，所述弹性件被所述引导部件引导。
  11. 根据权利要求8至10中任一项的离合器分离副缸，其特征在于，所述弹性件为螺旋弹簧(50)、波形环、碟形弹簧或橡胶部件。
PCT/CN2020/110328 2020-06-15 2020-08-20 离合器分离副缸 WO2021253617A1 (zh)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN202080099917.5A CN115427700A (zh) 2020-06-15 2020-08-20 离合器分离副缸
EP20940733.7A EP4166807A1 (de) 2020-06-15 2020-08-20 Hilfszylinder zum lösen einer kupplung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020115699.5A DE102020115699A1 (de) 2020-06-15 2020-06-15 Zentralausrückeranordnung
DE102020115699.5 2020-06-15

Publications (1)

Publication Number Publication Date
WO2021253617A1 true WO2021253617A1 (zh) 2021-12-23

Family

ID=78718599

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2020/110328 WO2021253617A1 (zh) 2020-06-15 2020-08-20 离合器分离副缸

Country Status (4)

Country Link
EP (1) EP4166807A1 (zh)
CN (1) CN115427700A (zh)
DE (1) DE102020115699A1 (zh)
WO (1) WO2021253617A1 (zh)

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5950788A (en) * 1997-04-07 1999-09-14 Mannesmann Sachs Ag Operating device for operating a friction clutch
WO2005113998A2 (en) * 2004-05-22 2005-12-01 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Clutch release bearing assembly with concentric slave cylinders
DE102009043242A1 (de) * 2008-10-27 2010-04-29 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Kupplungseinheit mit Ausrückvorrichtung
JP2010116984A (ja) * 2008-11-13 2010-05-27 Toyota Motor Corp クラッチ断接装置
WO2012000476A1 (de) * 2010-06-29 2012-01-05 Schaeffler Technologies Gmbh & Co. Kg Anbindung einer ausrückereinrichtung an eine kupplungsvorrichtung
DE102012208750A1 (de) * 2011-06-20 2012-12-20 Schaeffler Technologies AG & Co. KG Nehmerzylinder mit einem zweiteiligen Gehäuse und axial reduziertem Bauraumbedarf
DE102013218116A1 (de) * 2012-09-20 2014-03-20 Schaeffler Technologies AG & Co. KG Kolben-Zylinder-Anordnung und Verfahren zur Herstellung einer Kolben-Zylinder-Anordnung
DE102013222065A1 (de) * 2012-11-22 2014-05-22 Schaeffler Technologies Gmbh & Co. Kg Nehmerzylinder
DE102017122845A1 (de) * 2017-10-02 2019-04-04 Schaeffler Technologies AG & Co. KG Nehmerzylinder und Federhalterring für Nehmerzylinder
DE102018105963A1 (de) * 2018-03-15 2019-09-19 Schaeffler Technologies AG & Co. KG Hydraulische Ausrücklageranordnung
CN210661115U (zh) 2019-09-24 2020-06-02 上汽通用汽车有限公司 一种双向活塞及湿式离合器总成

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5950788A (en) * 1997-04-07 1999-09-14 Mannesmann Sachs Ag Operating device for operating a friction clutch
WO2005113998A2 (en) * 2004-05-22 2005-12-01 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Clutch release bearing assembly with concentric slave cylinders
DE102009043242A1 (de) * 2008-10-27 2010-04-29 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Kupplungseinheit mit Ausrückvorrichtung
JP2010116984A (ja) * 2008-11-13 2010-05-27 Toyota Motor Corp クラッチ断接装置
WO2012000476A1 (de) * 2010-06-29 2012-01-05 Schaeffler Technologies Gmbh & Co. Kg Anbindung einer ausrückereinrichtung an eine kupplungsvorrichtung
DE102012208750A1 (de) * 2011-06-20 2012-12-20 Schaeffler Technologies AG & Co. KG Nehmerzylinder mit einem zweiteiligen Gehäuse und axial reduziertem Bauraumbedarf
DE102013218116A1 (de) * 2012-09-20 2014-03-20 Schaeffler Technologies AG & Co. KG Kolben-Zylinder-Anordnung und Verfahren zur Herstellung einer Kolben-Zylinder-Anordnung
DE102013222065A1 (de) * 2012-11-22 2014-05-22 Schaeffler Technologies Gmbh & Co. Kg Nehmerzylinder
DE102017122845A1 (de) * 2017-10-02 2019-04-04 Schaeffler Technologies AG & Co. KG Nehmerzylinder und Federhalterring für Nehmerzylinder
DE102018105963A1 (de) * 2018-03-15 2019-09-19 Schaeffler Technologies AG & Co. KG Hydraulische Ausrücklageranordnung
CN210661115U (zh) 2019-09-24 2020-06-02 上汽通用汽车有限公司 一种双向活塞及湿式离合器总成

Also Published As

Publication number Publication date
CN115427700A (zh) 2022-12-02
EP4166807A1 (de) 2023-04-19
DE102020115699A1 (de) 2021-12-16

Similar Documents

Publication Publication Date Title
US6405837B1 (en) Combined parking and service brake
KR101498751B1 (ko) 클러치 구동 시스템
CN112334675B (zh) 离合装置
US8752686B2 (en) Multi-disc frictional engagement mechanism
US8240445B2 (en) Multiplate clutch and motor vehicle having the same
US8151964B2 (en) Multiple disc clutch apparatus
US20080173515A1 (en) Disk spring hydraulic release brake
US20070095619A1 (en) Dual actuator friction brake assembly
CN115210484B (zh) 具有用于将两个子盘接合到从动轴上的彼此独立地作用的弹簧板单元的多盘式离合器装置
JPH06193649A (ja) 流体作動型の摩擦装置
US5964333A (en) Friction clutch and a slave cylinder for the operation of a friction clutch
JP5191819B2 (ja) 多板クラッチ
WO2021253617A1 (zh) 离合器分离副缸
US8857592B2 (en) Clutch assembly performance enhancement apparatus and method
US5794751A (en) Piston for torque transmitting systems
EP2249064B1 (en) Hydraulic actuator for vehicle
CN110678664A (zh) 具有用于离合器弹簧的定向元件的离合器支承装置
CN116438386A (zh) 具有复位弹簧元件的摩擦设备和变速器设备
US10844940B2 (en) Torque converter with charge pressure compensation
JP6539496B2 (ja) フリーホイールハブ機構
CN112313422A (zh) 离合器装置
CN104235224B (zh) 一种湿式双离合器
EP3998413B1 (en) Dual clutch device
KR102487177B1 (ko) 자동변속기용 엔드 브레이크 장치
WO2021147540A2 (zh) 离合机构及车辆离合器

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 20940733

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2020940733

Country of ref document: EP

Effective date: 20230116