Clutch device

Abstract

A clutch device comprises a first disc piece (50), a second disc piece (130), a joint mechanism and a control mechanism. The first disc part (50) and the second disc part (130) are coaxially arranged and can rotate relative to each other; the connecting mechanism comprises a plurality of ratchets and at least two pawls (80), the ratchets are distributed on the periphery of the first disc part (50) in the circumferential direction, and the pawls (80) are installed on the second disc part (130) in the mode that the pawls (80) can rotate relative to the second disc part (130) and can be connected with the ratchets or separated from the ratchets; the actuating mechanism comprises an actuating pin (110), a pin spring (100), a diaphragm spring (90) and an actuator, the actuating pin (110) being axially displaceable relative to the second disc part (130) and having an actuating portion (112) at a longitudinal end facing the second disc part (130). The pin spring (100) bears against the actuating pin (110) at one end and against the second disc (130) at the other end or against a member fixed relative to the second disc (130) in the direction of elastic action, and the diaphragm spring (90) bears against the actuating pin (110) at one end and is actuated by the actuator at the other end in the direction of elastic action.

Description

clutch device Technical Field

[0001] The present application relates to the field of vehicle technology and particularly to a clutch device. Background Art

[0002] The clutch is a crucial component in a vehicle's powertrain. It connects and disconnects the torque transmission path within the powertrain. Current wet clutch technology includes various types, including friction clutches and dog clutches.

[0003] For example, a wet-running friction clutch, such as that disclosed in patent document WO2020064400A1, has large axial and radial dimensions and is expensive to manufacture. For example, a dog clutch, such as that disclosed in patent document US007975796B2, is suitable for situations where the speed difference between the two ends of the clutch is sufficiently small; if the speed difference is large, there is a risk of clutch engagement failure.

[0004] Summary of the Invention

[0005] Therefore, an object of the present application is to provide a clutch device that has a compact structure and is applicable to situations where the speed difference is relatively high. Advantageously, the clutch device has a low manufacturing cost.

[0006] According to the present application, the above-mentioned objectives are achieved by a clutch device. The clutch device comprises: a first disk member, a second disk member, an engagement mechanism, and an operating mechanism. The first disk member and the second disk member are coaxially arranged and rotatable relative to each other. The engagement mechanism comprises a plurality of ratchet teeth and at least two pawls, wherein the plurality of ratchet teeth are circumferentially distributed around the outer periphery of the first disk member; the at least two pawls are mounted on the second disk member so as to be rotatable relative to the second disk member and can engage with or disengage from the ratchet teeth. The operating mechanism includes an actuating pin, a pin spring, a diaphragm spring and an actuator, wherein the actuating pin is capable of axially moving relative to the second disk member and is configured with an actuating portion at a longitudinal end portion toward the second disk member, wherein when the actuating pin approaches the second disk member axially, the actuating portion is capable of acting on the pawl and causing the pawl to engage with the ratchet teeth, and when the actuating pin moves axially away from the second disk member, the pawl is disengaged from the ratchet teeth; the pin spring abuts against the actuating pin at one end along the elastic action direction and against the second disk member or a component fixed relative to the second disk member at the other end; a diaphragm spring and an actuator, wherein the diaphragm spring abuts against the actuating pin at one end along the elastic action direction and is operated by the actuator at the other end.

[0007] In an advantageous embodiment, the clutch device further comprises a hub cover, wherein the hub cover is fixedly connected to the second disc member and is constructed with a section located on the axial side facing away from the second disc member relative to the first disc member, wherein the diaphragm spring is supported at the section with its support portion, abuts the actuating pin with its outer end located radially outside the support portion and abuts the actuator with its inner end located radially inside the support portion.

[0008] Advantageously, the second disk and / or the hub cap are manufactured by a stamping process.

[0009] Advantageously, the actuator is designed as a hydraulic actuator.

[0010] In this case, it is particularly advantageous if the actuator comprises a hydraulic chamber formed by the actuator housing and a piston which can be hydraulically extended at least partially into or out of the hydraulic chamber, wherein the actuator housing and the piston are made of plastic.

[0011] In this case, it is particularly advantageous if the piston rests via an axial bearing against the inner end of the diaphragm spring.

[0012] In this case, it is particularly advantageous if a radial bearing is provided radially inwardly of the actuator, by means of which the shaft element, which is non-rotatably connected to the first disk element, can be supported in a rotatable manner on the housing.

[0013] Advantageously, the pin spring surrounds the actuating pin, wherein the pin spring in the spring action direction abuts at one end against a stop formed on the actuating pin and at the other end against the hub cap.

[0014] In this case, it is particularly advantageous if the pin spring is designed as a wave spring.

[0015] In an advantageous embodiment, each pawl is constructed with a first engagement portion and a second engagement portion, and each ratchet tooth is constructed with a first engagement counterpart and a second engagement counterpart, wherein the first engagement portion and the second engagement portion are used to engage with the first engagement counterpart and the second engagement counterpart respectively in two opposite rotational directions.

[0016] The clutch device provided by this application has a compact structure and is relatively lightweight, enabling its placement within the confines of a vehicle's limited space and meeting current lightweight design requirements. Furthermore, the clutch device of this application enables bidirectional torque transmission and supports engagement applications with large speed differentials. Furthermore, the clutch device of this application can be manufactured at low cost. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The features, advantages and technical effects of the embodiments of the present application will be described below with reference to the accompanying drawings.

[0018] FIG1 is an axial half-sectional view of a clutch device in an engaged state according to one embodiment;

[0019] FIG2 is an axial half-sectional view of the clutch device according to the embodiment shown in FIG1 in a disconnected state;

[0020] FIG3 is a radial cross-sectional view of the clutch device at the engagement mechanism according to the embodiment shown in FIG1 ;

[0021] FIG4 is a perspective view of a pawl of the engagement mechanism of the clutch device according to the embodiment shown in FIG1 ;

[0022] 5 is a perspective view of an actuating pin of the operating mechanism of the clutch device according to the embodiment shown in FIG. 1 ;

[0023] FIG6 is a schematic diagram of the cooperation between the pawl shown in FIG4 and the actuating pin shown in FIG5;

[0024] 7 is a schematic diagram of the engagement mechanism of the clutch device according to the embodiment shown in FIG. 1 in an engaged state and transmitting torque in a first rotational direction;

[0025] 8 is a schematic diagram of the engagement mechanism of the clutch device according to the embodiment shown in FIG. 1 in an engaged state and transmitting torque in a second rotational direction;

[0026] FIG9 is a schematic diagram of the engagement mechanism of the clutch device according to the embodiment shown in FIG1 during engagement or disengagement;

[0027] FIG10 is a schematic diagram of the engagement mechanism of the clutch device according to the embodiment shown in FIG1 in a disengaged state. DETAILED DESCRIPTION

[0028] The embodiments provided in FIG. 1 to FIG. 3 provide a clutch device that can be arranged at any position on a torque transmission path between a driving device and a driven device in a vehicle drive system, thereby connecting or disconnecting the transmission of torque.

[0029] Here, the vehicle can be an electric vehicle, a hybrid vehicle, or a traditional fuel vehicle. In this case, the driving device can be a drive motor and / or an internal combustion engine; the driven device can be a vehicle drive wheel. In this embodiment, the structure and working mode of the clutch device are exemplified by taking the torque transmission direction of the vehicle drive wheel driven by the drive motor and / or internal combustion engine as an example. Therefore, in this embodiment, the terms related to "input" and "output" of torque are all based on the torque transmission direction of the above example. For example, the end of the clutch device that receives torque from the drive motor and / or internal combustion engine is called the input end, and the end of the clutch device that transmits torque to the vehicle drive wheel is called the output end. However, this embodiment does not limit the application scenario of the clutch device according to the present application. For example, the clutch device can also be used in energy recovery, internal combustion engine starting, motor operation in generator mode, and other working conditions opposite to the above torque transmission direction.

[0030] Fig. 1 shows an axial half-section view of a clutch device according to an embodiment. The clutch device comprises: a first disc 50, a second disc 130, an engagement mechanism, and an operating mechanism.

[0031] The first disc 50 and the second disc 130 are coaxially arranged and rotatable relative to each other. The first disc 50 is mounted in a rotationally fixed manner on a first shaft 140. In this embodiment, the first shaft 140 serves as the input of the clutch device and can be connected to the vehicle's drive system. In other embodiments, the first shaft 140 can be the torque output shaft of the vehicle's drive system. The second disc 130 can be directly or indirectly connected in a rotationally fixed manner to the second shaft 150. In this embodiment, the second disc 130 is fixedly connected to the housing 170, which is in a rotationally fixed manner connected to the second shaft 150, for example, via a spline. This indirectly connects the second disc 130 in a rotationally fixed manner to the second shaft 150. In other embodiments, the second disc 130 can also be directly and rotationally fixedly connected to the second shaft 150. In this case, the second shaft can serve as the output of the clutch device or the input shaft of a downstream device in the torque transmission path.

[0032] It should be noted that, within the scope of this document, unless otherwise specified, the terms "axial," "radial," and "circumferential" all refer to the common rotational axis of the first and second disk members 50, 130, i.e., the rotational axis of the clutch device. Specifically, "axial" refers to the direction of, or parallel to, the rotational axis. "Radial" refers to a direction perpendicular to and intersecting the rotational axis. "Circumferential" refers to a direction surrounding the rotational axis.

[0033] Furthermore, within the scope of this document, the term "rotationally fixed connection" refers to a connection that prevents two components from rotating relative to each other, thereby enabling torque transmission. For example, when two components are rotationally fixedly connected to each other, or one component is rotationally fixedly mounted to another, the two components can transmit torque and rotate together. For example, a spline connection can achieve a rotationally fixed connection. Another example is a fixed connection. Whether the two components of a rotationally fixed connection are capable of axial movement relative to each other is not specified herein.

[0034] The coupling mechanism includes a plurality of ratchets and at least two pawls 80, wherein the plurality of ratchets are distributed along the circumferential direction at the outer periphery of the first disk member 50, and the at least two pawls 80 are respectively mounted on the second disk member 130 in a manner that allows them to rotate relative to the second disk member 130 and can respectively engage with or disengage from the ratchets.

[0035] Preferably, the ratchet teeth are integrally formed with the first disc 50, and the first disc 50 is configured as a ratchet. Preferably, the ratchet teeth are evenly distributed on the outer periphery of the first disc 50 in the circumferential direction.

[0036] FIG4 shows a perspective view of the pawl 80 according to this embodiment. The pawl 80 includes a rotating portion 81 and engaging portions 83 and 84 disposed distally from the rotating portion 81. Preferably, the pawl 80 is mounted on the second disk 130 such that each pawl 80 can pivot relative to the second disk 130 about the rotating portion 81. The pawl 80, and in particular the engaging portions 83 and 84, swing about fixed axes relative to the second disk 130. Preferably, the pivot axes of each pawl 80 are parallel to the rotational axis of the clutch device. Alternatively, the pawl 80 can be mounted on the second disk 130 such that each pawl 80 can pivot relative to the second disk 130 about non-fixed axes. When the pawl 80 is rotated to the engaged position, the engaging portions 83 and 84 of the pawl 80 engage with the ratchet teeth on the first disk 50, thereby enabling the first disk 50 and the second disk 130 to rotate together, thereby connecting the torque transmission path. When the pawl 80 is rotated to the disconnected position, the engaging portions 83 and 84 of the pawl 80 are decoupled from the ratchet teeth on the first disk 50, thereby disconnecting the torque transmission path. The number of pawls depends on the torque to be transmitted. Preferably, at least two pawls 80 are evenly distributed around the second disk 130 in the circumferential direction.

[0037] In this embodiment, the clutch device further includes a hub cap 120. The hub cap 120 is fixedly connected to the second disc 130, for example, by an interference fit. Preferably, the second disc 130 and / or the hub cap 120 are manufactured by a stamping process. Advantageously, the connection section where the second disc 130 and the hub cap 120 are fixedly connected to each other is located radially outside the first disc 50. Preferably, the hub cap 120 is configured with a section located axially away from the second disc 130 relative to the first disc 50. Thus, the hub cap 120 and the second disc can protect the coupling mechanism, such as the ratchet area and the pawl 80 of the first disc 50, and facilitate the compact arrangement of the components to be described in detail later.

[0038] The rotary motion of the pawl 80 between the engagement position and the disconnection position is realized in a direction of rotation by an operating mechanism and on the other hand by a return spring that is not shown in detail. Here, the return spring is tensioned between the pawl 80 and the second disk 130 along its elastic action direction.

[0039] Here, the operating mechanism includes an actuating pin 110 , a pin spring 100 , a diaphragm spring 90 and an actuator.

[0040] Figure 5 shows a perspective view of the actuating pin 110 according to this embodiment. Specifically, the actuating pin 110 comprises a substantially cylindrical body 111. The actuating pin 110 is axially movable relative to the second disk 130. To this end, the actuating pin 110 is preferably at least partially axially extendable into or out of the accommodating cavity formed by the second disk 130. As shown in Figure 5, the actuating pin 110 is configured with an actuating portion 112 at its longitudinal end facing the second disk 130. As further shown in Figure 4, the pawl 80 is further configured with an actuating mating portion 82 at a position distal from the rotating portion 81. The actuating mating portion 82 of the pawl 80 and the actuating portion 112 of the actuating pin 110 form cooperating surfaces, such that when the actuating pin 110 is moved in its longitudinal direction, i.e., in this embodiment, in the axial direction of the clutch device, the pawl 80 is caused to rotate. See Figure 6 for a schematic diagram illustrating the cooperating action of the pawl 80 and the actuating pin 110. Advantageously, the actuating counterpart 82 of the pawl 80 and the actuating portion 112 of the actuating pin 110 are configured as matching inclined surfaces. Advantageously, the actuating portion 112 of the actuating pin 110 is realized by a chamfer.

[0041] The movement of the actuating pin 110 in its longitudinal direction is achieved in one direction by the pin spring 100. As shown in FIG1 , the pin spring 100 is configured as a wave spring and surrounds the actuating pin 110. The pin spring 100 is tensioned between a stopper 113 configured at the actuating pin 110 and a hub cover 120 in the elastic action direction.

[0042] The actuator enables longitudinal movement of the actuating pin 110 in the other direction. In this embodiment, a diaphragm spring 90 is also provided in the torque transmission path between the actuator and each actuating pin 110. Referring to FIG1 , the diaphragm spring 90 is an annular disk-shaped structure and comprises a circular edge section with multiple fingers distributed along the circumference. The fingers extend radially inward from the edge section in a meandering manner. The diaphragm spring 90 is mounted via a centering screw 70 to the section of the hub cap 120 located axially away from the second disk 130 relative to the first disk 50, allowing for relative axial movement and deformation. The diaphragm spring 90 acts as a lever spring, acting like a lever between the actuator and the actuating pin 110. The diaphragm spring 90 is supported at its support portion via a support ring 60 in the aforementioned section of the hub cap 120, with this support point forming the lever fulcrum. The diaphragm spring 90 abuts against the actuating pin 110 with its outer end located radially outside the support portion, that is, the annular edge section; and the diaphragm spring 90 abuts against the actuating member 30 of the actuator with its inner end located radially inside the support portion, that is, the free end of the finger.

[0043] In this embodiment, the actuator is configured as a hydraulic actuator. Advantageously, the actuator includes a hydraulic chamber formed by the actuator housing 10 and a piston 30 that can be at least partially extended into or out of the hydraulic chamber using hydraulic pressure. The actuator includes a dynamic seal 20 to prevent leakage of hydraulic fluid. Preferably, the actuator housing 10 and the piston 30 are made of plastic. The piston 30 rests against the fingers of a diaphragm spring 90 via an axial bearing 40.

[0044] In this embodiment, a radial bearing is provided radially inside the actuator, and the first shaft 140 can be supported in a relatively rotatable manner on the housing 160 via the radial bearing, thereby achieving a compact structure of the clutch device.

[0045] Figures 1 and 2 show axial half-section views of the clutch device of this embodiment in the engaged and disengaged states, respectively. Figure 3 shows a radial cross-section view of the clutch device of this embodiment at the engagement mechanism. The clutch device of this embodiment employs a normally engaged design. When the vehicle is moving, the clutch device is normally engaged and disengages only when the actuator is operated.

[0046] Referring to Figures 1 and 3 , when the clutch device is engaged, the actuator is inactive. At this time, the piston 30 is at least partially retracted into the hydraulic chamber and exerts no force or only minimal force against the fingers of the diaphragm spring 90. Because the fingers are not subject to force or only minimal force, the diaphragm spring 90, acting as a lever spring, abuts against the respective actuating pins 110 at their annular edge sections, causing each actuating pin 110 to axially move toward the second disk 130 or remain in a position adjacent to the second disk, overcoming the elastic force of the pin spring 100. Each actuating pin 110, through its actuating portion 112, applies an axial force to the corresponding actuating counterpart 82 of the pawl 80, thereby causing the pawl 80 to rotate to or remain in the engaged position, overcoming the elastic force of the return spring. In the engaged position, the engagement portions 83 and 84 of each pawl 80 engage with the ratchet teeth of the first disk 50.

[0047] Referring to Figure 2, when the clutch device needs to be disconnected, the actuator begins to work. At this time, the piston 30 extends at least partially out of the hydraulic chamber under the action of hydraulic pressure and applies a force to the finger of the diaphragm spring 90. Due to the force on the finger, the diaphragm spring 90, which acts as a lever spring, moves and / or deforms in the axial direction in the direction away from the second disk member at the edge section of the circular ring. At this time, the axial force applied by the diaphragm spring 90 to each actuating pin 110 is reduced or completely eliminated, causing each actuating pin 110 to move axially away from the second disk member 130 under the elastic force of the pin spring 100. The force applied by each actuating pin 110 to the corresponding pawl 80 is reduced or eliminated, and the return spring prompts the pawl 80 to rotate to the disconnected position. At the disconnected position, the engaging portions 83 and 84 of each pawl 80 are disengaged from the ratchet teeth of the first disk member 50.

[0048] According to a design of this embodiment, each pawl 80 is constructed with a first engaging portion 83 and a second engaging portion 84, and each ratchet tooth is constructed with a first engaging mating portion 51 and a second engaging mating portion 52, wherein the first engaging portion 83 and the second engaging portion 84 are used to engage with the first engaging mating portion 51 and the second engaging mating portion 52 respectively in two opposite rotational directions.

[0049] FIG7 is a schematic diagram illustrating the engagement mechanism of the clutch device according to this embodiment in an engaged state and transmitting torque in a first rotational direction. As shown in FIG7 , the first engaging mating portion 51 of the ratchet tooth of the first disk member 50 abuts against the first engaging portion 83 of the pawl 80, thereby transmitting the rotational motion of the first disk member 50 in the first rotational direction to the second disk member 130, thereby transmitting torque.

[0050] FIG8 is a schematic diagram illustrating the engagement mechanism of the clutch device according to this embodiment in an engaged state and transmitting torque in a second rotational direction. As shown in FIG8 , the second engaging mating portion 52 of the ratchet tooth of the second disc 50 abuts against the second engaging portion 84 of the pawl 80, thereby transmitting the rotational motion of the first disc 50 to the second disc 130 in a second rotational direction opposite to the first rotational direction, thereby transmitting torque.

[0051] Figure 9 is a schematic diagram of the clutch mechanism of the present embodiment during engagement or disengagement. Figure 10 is a schematic diagram of the clutch mechanism of the present embodiment in a disengaged state. As shown in Figure 10 , the engagement portions 83 and 84 of each pawl 80 are now disengaged from the ratchet teeth of the first disc 50.

[0052] The clutch device provided according to this embodiment has a compact structure and low weight, enabling installation in the confined space of a vehicle and meeting current lightweight design requirements. Furthermore, the clutch device of this embodiment enables bidirectional torque transmission and supports engagement applications with large speed differentials. Furthermore, the clutch device of this embodiment can be manufactured at low cost.

[0053] Obviously, the above embodiments of the present application are merely examples for the purpose of clearly illustrating the present application, and are not intended to limit the implementation methods of the present application. For those skilled in the art, other different forms of changes or modifications can be made based on the above description. It is not necessary and impossible to list all the implementation methods here. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present application should be included in the scope of protection of the claims of the present application. In the description of the present application, it should be noted that the terms "first" and "second" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance.

[0054] LIST OF REFERENCE NUMERALS 10 Actuator housing 20 Seal 30 Piston 40 Thrust bearing 50 First disk 51 First engaging partner 52 Second engaging partner 60 Support ring 70 Centering bolt 80 Pawl 81 Rotating portion 82 Actuating partner 83 First engaging portion 84 Second engaging portion 90 Diaphragm spring 100 Pin spring 110 Actuating pin 111 Main body 112 Actuating portion 113 Stopper 120 Hub cap 130 Second disk 140 First shaft 150 Second shaft 160 Housing 170 Housing

Claims

1. A clutch device, comprising: A first disk member (50) and a second disk member (130) which are coaxially arranged and rotatable relative to each other; The engaging mechanism comprises: a plurality of ratchet teeth distributed along the circumferential direction at the outer periphery of the first disk member (50), at least two ratchet pawls (80), which are respectively mounted on the second disk member (130) in a manner that allows them to rotate relative to the second disk member (130) and are respectively capable of engaging with or disengaging from the ratchet teeth; Control mechanism, including: an actuating pin (110) which is axially movable relative to the second disk member (130) and is provided with an actuating portion (112) at a longitudinal end portion thereof facing the second disk member (130), wherein when the actuating pin (110) is axially close to the second disk member (130), the actuating portion (112) is capable of acting on the pawl (80) and causing the pawl (80) to engage with the ratchet teeth, and when the actuating pin (110) is axially away from the second disk member (130), the pawl (80) is disengaged from the ratchet teeth, a pin spring (100) which, in an elastic action direction, abuts against the actuating pin (110) at one end and abuts against the second disk member (130) or a member fixed relative to the second disk member (130) at the other end, A diaphragm spring (90) and an actuator, wherein the diaphragm spring (90) abuts against the actuating pin (110) at one end along the elastic action direction and is operated by the actuator at the other end.

2. The clutch device according to claim 1, wherein: The clutch device further comprises a hub cover (120), wherein the hub cover (120) is fixedly connected to the second disc member (130) and is configured with a section located on an axial side facing away from the second disc member (130) relative to the first disc member (50). The diaphragm spring (90) is supported at the section with its support portion, with its outer end located radially outside the support portion abutting against the actuating pin (110), and with its inner end located radially inside the support portion abutting against the actuator.

3. The clutch device according to claim 2, wherein: The second disk (130) and / or the hub cover (120) are made by a stamping process.

4. The clutch device according to claim 2, wherein: The actuator is designed as a hydraulic actuator.

5. The clutch device according to claim 4, wherein: The actuator comprises a hydraulic chamber formed by an actuator housing (10) and a piston (30) which can be at least partially extended into or out of the hydraulic chamber by means of hydraulic pressure, wherein the actuator housing (10) and the piston (30) are made of plastic.

6. The clutch device according to claim 4, wherein: The piston (30) abuts against the inner end of the diaphragm spring (90) via an axial bearing (40).

7. The clutch device according to claim 4, wherein: A radial bearing is arranged radially inside the actuator, and a shaft component (140) connected to the first disk component (50) in a rotationally fixed manner can be supported on the housing in a relatively rotatable manner by means of the radial bearing.

8. The clutch device according to claim 2, wherein: The pin spring (100) surrounds the actuating pin (110), wherein the pin spring (100) abuts against a stopper (113) configured on the actuating pin (110) at one end and against the hub cover (120) at the other end in an elastic action direction.

9. The clutch device according to claim 8, wherein: The pin spring (100) is configured as a wave spring.

10. The clutch device according to claim 1, wherein: Each of the pawls (80) is constructed with a first engaging portion (83) and a second engaging portion (84), and each of the ratchet teeth is constructed with a first engaging mating portion (51) and a second engaging mating portion (52), wherein the first engaging portion (83) and the second engaging portion (84) are used to respectively engage with the first engaging mating portion (51) and the second engaging mating portion (52) in two opposite rotational directions.

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