WO2025054897A1 - 离合装置 - Google Patents

离合装置 Download PDF

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Publication number
WO2025054897A1
WO2025054897A1 PCT/CN2023/118799 CN2023118799W WO2025054897A1 WO 2025054897 A1 WO2025054897 A1 WO 2025054897A1 CN 2023118799 W CN2023118799 W CN 2023118799W WO 2025054897 A1 WO2025054897 A1 WO 2025054897A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch device
actuator
disk member
pin
actuating pin
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/CN2023/118799
Other languages
English (en)
French (fr)
Inventor
吴少雄
徐志力
付兰平
韦亚军
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to CN202380101446.0A priority Critical patent/CN121752828A/zh
Priority to PCT/CN2023/118799 priority patent/WO2025054897A1/zh
Publication of WO2025054897A1 publication Critical patent/WO2025054897A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16D25/12—Details not specific to one of the before-mentioned types
    • 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
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/12—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like

Definitions

  • the present application relates to the field of vehicle technology and specifically to a clutch device.
  • the clutch is an important component in the vehicle transmission system.
  • the torque transmission path in the transmission system can be connected or disconnected with the help of the clutch.
  • the clutch includes friction clutch and dog clutch.
  • a wet-running friction clutch is disclosed in patent document WO2020064400A1, in which the clutch has large axial and radial dimensions, and the manufacturing cost of the clutch is relatively high.
  • a tooth clutch is disclosed in patent document US007975796B2, in which the clutch is suitable for the case where the speed difference between the two ends of the clutch is small enough; once the speed difference is large, there is a risk of clutch engagement failure.
  • an object of the present application is to provide a clutch device which has a compact structure and is applicable to situations where the rotational speed difference is relatively high.
  • the clutch device has a relatively low manufacturing cost.
  • the clutch device comprises: a first disk member and a second disk member, a coupling mechanism and an operating mechanism.
  • the first disk member and the second disk member are coaxially arranged and can rotate relative to each other.
  • the coupling mechanism comprises a plurality of ratchets and at least two pawls, wherein the plurality of ratchets are distributed on the outer periphery of the first disk member along the circumferential direction; and the at least two pawls are respectively mounted on the second disk member in a manner that they can rotate relative to the second disk member and can respectively engage with or disengage from the ratchets.
  • the operating mechanism comprises an actuating pin, a pin spring, a diaphragm spring and an actuator, wherein the actuating pin can move axially relative to the second disk member and is configured with an actuating portion at a longitudinal end portion facing the second disk member, wherein when the actuating pin approaches the second disk member in the axial direction, the actuating portion can act on the pawl and make the pawl engage with the ratchet teeth, and when the actuating pin moves away from the second disk member in the axial direction, the pawl is disengaged from the ratchet teeth; the pin spring abuts against the actuating pin at one end in an elastic action direction and against the second disk member or a component fixed relative to the second disk member at the other end; the diaphragm spring and the actuator, wherein, The diaphragm spring abuts against the actuating pin at one end in the elastic action direction and is actuated by the actuator at the other end.
  • the clutch device also includes a hub cover, wherein the hub cover is fixedly connected to the second disk member and is constructed with a section located on the axial side facing away from the second disk member relative to the first disk member, wherein the diaphragm spring is supported at the section with its support portion, abuts against the actuating pin with its outer end located radially outside the support portion and abuts against the actuator with its inner end located radially inside the support portion.
  • the second disk and/or the hub shell are produced by a stamping process.
  • the actuator is designed as a hydraulic actuator.
  • the actuator comprises a hydraulic chamber formed by an 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.
  • a radial bearing is arranged 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.
  • the pin spring surrounds the actuating pin, wherein the pin spring in the elastic action direction abuts at one end against a stop formed on the actuating pin and at the other end against the hub cap.
  • the pin spring is designed as a wave spring.
  • each pawl is constructed with a first engagement portion and a second engagement portion
  • 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.
  • the clutch device provided by the present application has a compact structure and light weight, can be arranged in a small accommodation space of a vehicle and meets the requirements of current lightweight design.
  • the clutch device of the present application can realize bidirectional torque transmission and support engagement applications under conditions of large speed difference.
  • the clutch device of the present application can be manufactured at low cost.
  • FIG1 is an axial half-sectional view of a clutch device in an engaged state according to an embodiment
  • FIG2 is an axial half-sectional view of the clutch device in a disconnected state according to the embodiment shown in FIG1 ;
  • FIG. 3 is a radial cross-sectional view of the clutch device at the engagement mechanism according to the embodiment shown in FIG. 1 ;
  • FIG. 4 is a perspective view of a pawl of the engagement mechanism of the clutch device according to the embodiment shown in FIG. 1 ;
  • FIG. 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 ;
  • FIG. 6 is a schematic diagram of the cooperation between the pawl shown in FIG. 4 and the actuating pin shown in FIG. 5 ;
  • FIG. 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;
  • FIG. 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;
  • FIG9 is a schematic diagram of the engagement mechanism of the clutch device according to the embodiment shown in FIG1 during the engagement or separation process;
  • FIG. 10 is a schematic diagram of the engagement mechanism of the clutch device according to the embodiment shown in FIG. 1 in a disengaged state.
  • FIGS. 1 to 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, so as to connect or disconnect the transmission of torque.
  • the vehicle can be an electric vehicle, a hybrid vehicle or a traditional fuel vehicle.
  • the driving device can be a driving motor and/or an internal combustion engine;
  • the driven device can be a vehicle driving wheel.
  • the structure and working mode of the clutch device are exemplarily described by taking the torque transmission direction of the vehicle driving wheel driven by the driving motor and/or the internal combustion engine as an example. Therefore, in this embodiment, the terms related to the "input" and "output" of torque are based on the torque transmission direction of the above example, for example, the end of the clutch device that receives torque from the driving motor and/or the internal combustion engine is called the input end, and the end of the clutch device that transmits torque to the vehicle driving wheel is called the output end.
  • this embodiment does not limit the application scenario of the clutch device according to the present application.
  • the clutch device can also be applied to energy recovery, internal combustion engine starting, motor operation in generator mode and other working conditions opposite to the above torque transmission direction.
  • FIG1 shows an axial half-section view of a clutch device according to an embodiment.
  • the invention comprises: a first plate member 50 and a second plate member 130, a coupling mechanism and an operating mechanism.
  • the first disc 50 and the second disc 130 are arranged coaxially and can rotate relative to each other.
  • the first disc 50 is mounted on the first shaft 140 in a rotationally fixed manner.
  • the first shaft 140 is used as the input end of the clutch device, and the first shaft 140 can be connected to the drive device of the vehicle.
  • the first shaft 140 can be a torque output shaft of the drive device of the vehicle.
  • the second disc 130 can be directly or indirectly connected to the second shaft 150 in a rotationally fixed manner.
  • the second disc 130 is fixedly connected to the housing 170, and the housing 170 is connected to the second shaft 150 in a rotationally fixed manner, for example, by a spline, so that the second disc 130 is indirectly connected to the second shaft 150 in a rotationally fixed manner.
  • the second disc 130 can also be directly connected to the second shaft 150 in a rotationally fixed manner.
  • the second shaft can be the output end of the clutch device, and can also be the input shaft of a downstream device on the torque transmission path.
  • axial direction refers to the direction of the above-mentioned rotation axis or a direction parallel to the above-mentioned rotation axis.
  • dial direction refers to a direction perpendicular to the above-mentioned rotation axis and intersecting the above-mentioned rotation axis.
  • Cirumferential direction refers to a direction around the above-mentioned rotation axis.
  • rotation-proof connection refers to a connection that prevents two components from rotating relative to each other, thereby enabling torque to be transmitted.
  • rotation-proof connection refers to a connection that prevents two components from rotating relative to each other, thereby enabling torque to be transmitted.
  • the two components can transmit torque and can rotate together.
  • a spline connection can achieve an anti-rotation connection.
  • a fixed connection can also achieve an anti-rotation connection.
  • 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 on 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 they can rotate relative to the second disk member 130 and can respectively engage with or disengage from the ratchets.
  • the ratchet teeth are integrally constructed with the first disk member 50, and the first disk member 50 is constructed as a ratchet.
  • the ratchet teeth are evenly distributed on the outer periphery of the first disk member 50 in the circumferential direction.
  • FIG. 4 shows a perspective view of the pawl 80 according to the present embodiment.
  • the pawl 80 includes a rotating portion 81 and engaging portions 83 and 84 disposed away from the rotating portion 81.
  • the pawl 80 is mounted on the second disk 130 so that each pawl 80 can pivot around the rotating portion 81 relative to the second disk 130, and the pawl 80, in particular the engaging portions 83 and 84, swings around respective fixed axes relative to the second disk 130.
  • the axes of pivoting of each pawl 80 are parallel to the rotation axis of the clutch device.
  • the pawl 80 is mounted on the second disk 130 so that each pawl 80 can rotate around respective non-fixed axes relative to the second disk 130.
  • the engaging portions 83 and 84 of the pawl 80 can engage with the ratchet teeth at the first disk 50, so that the first disk 50 and the second disk 130 can rotate together, that is, the torque transmission path is connected.
  • the engagement portions 83, 84 of the pawl 80 are decoupled from the ratchet teeth at the first disk 50, thereby disconnecting the torque transmission path.
  • the number of pawls depends on the torque to be transmitted.
  • at least two pawls 80 are evenly distributed on the second disk 130 in the circumferential direction.
  • the clutch device further comprises a hub cover 120.
  • the hub cover 120 is fixedly connected to the second disc 130, for example, by interference fit.
  • the second disc 130 and/or the hub cover 120 are made by a stamping process.
  • the connection section where the second disc 130 and the hub cover 120 are fixedly connected to each other is arranged radially outside the first disc 50.
  • the hub cover 120 is configured with a section located on the axial side facing away from the second disc 130 relative to the first disc 50.
  • the hub cover 120 and the second disc can protect the engagement mechanism, such as the ratchet area and the pawl 80 of the first disc 50, and are conducive to the compact arrangement of the components to be described in detail later.
  • the rotational movement of the pawl 80 between the engagement position and the disconnection position is realized in a rotation direction by an operating mechanism and in another direction by a return spring not shown in detail.
  • the return spring is tensioned between the pawl 80 and the second disk 130 along its elastic action direction.
  • the actuating mechanism includes an actuating pin 110 , a pin spring 100 , a diaphragm spring 90 and an actuator.
  • FIG. 5 shows a perspective view of the actuating pin 110 according to the present embodiment.
  • the actuating pin 110 is specifically a body 111 that is substantially cylindrical.
  • the actuating pin 110 can move axially relative to the second disk 130.
  • the actuating pin 110 can at least partially extend into or extend out of the accommodation cavity formed by the second disk 130 in the axial direction.
  • the actuating pin 110 is configured with an actuating portion 112 at the longitudinal end facing the second disk 130.
  • the pawl 80 is moved away from the rotating portion 112.
  • An actuating counterpart 82 is also configured at the position of the pawl 81.
  • the actuating counterpart 82 of the pawl 80 and the actuating portion 112 of the actuating pin 110 are configured as cooperative action surfaces, so that when the actuating pin 110 moves along the longitudinal direction of the actuating pin 110, that is, in this embodiment, the axial direction of the clutch device, the pawl 80 can be caused to rotate, see the schematic diagram of the cooperation between the pawl 80 and the actuating pin 110 shown in FIG6.
  • the actuating counterpart 82 of the pawl 80 and the actuating portion 112 of the actuating pin 110 are configured as paired inclined surfaces.
  • the actuating portion 112 of the actuating pin 110 is realized by chamfering.
  • the movement of the actuating pin 110 along its longitudinal direction is achieved in one direction by the pin spring 100.
  • the pin spring 100 is configured as a wave spring, and the pin spring 100 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 an elastic action direction.
  • a diaphragm spring 90 is further arranged on the torque transmission path between the actuator and each actuating pin 110.
  • the diaphragm spring 90 is in the shape of an annular disk and comprises a plurality of fingers distributed in the circumferential direction of an annular edge section, wherein the fingers extend from the edge section in a zigzag manner toward the radial inner side.
  • the diaphragm spring 90 is mounted on the section of the hub cover 120 located on the axial side facing away from the second disk member 130 relative to the first disk member 50 via a centering bolt 70 so as to be relatively movable and deformable in the axial direction.
  • the diaphragm spring 90 is used as a lever spring here, which acts like a lever between the actuator and the actuating pin 110.
  • the diaphragm spring 90 is supported at the above-mentioned section of the hub cover 120 via a support ring 60 with its support portion, and the support point forms a lever fulcrum.
  • the diaphragm spring 90 abuts against the actuating pin 110 with its outer end located radially outside the support, here, 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, here, the free end of the finger.
  • the actuator is configured as a hydraulic actuator.
  • the actuator comprises a hydraulic chamber formed by the 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.
  • the actuator comprises a dynamic seal 20 to prevent leakage of hydraulic fluid.
  • the actuator housing 10 and the piston 30 are made of plastic.
  • the piston 30 rests on the finger of the diaphragm spring 90 via an axial bearing 40.
  • a radial bearing is provided in the radial interior of the actuator, and the first shaft 140 can be supported on the housing 160 so as to be relatively rotatable by means of the radial bearing.
  • FIG1 and FIG2 show axial half-section views of the clutch device of this embodiment in the engaged state and the disengaged state, respectively.
  • FIG3 shows a radial section view of the clutch device of this embodiment at the engagement mechanism.
  • the clutch device according to this embodiment adopts a normally engaged scheme. When the vehicle is running, the clutch device is usually in the engaged state and is only disengaged when the actuator is operated.
  • the actuator when the clutch device is engaged, the actuator is not working, and the piston 30 at least partially extends into the hydraulic chamber and does not apply force to the finger of the diaphragm spring 90 or only presses against the finger of the diaphragm spring 90 with a small force. Since the finger is not subjected to force or only subjected to a small force, the diaphragm spring 90 acting as a lever spring abuts against each actuating pin 110 at the edge section of the circular ring, so that each actuating pin 110 moves toward the second disk member 130 in the axial direction against the elastic force of the pin spring 100 or remains at a position close to the second disk member.
  • Each actuating pin 110 applies an axial force to the actuating counterpart 82 of the corresponding pawl 80 through the actuating portion 112, thereby causing the pawl 80 to rotate to or remain in the engaged position against the elastic force of the return spring.
  • the engaging portions 83 and 84 of each pawl 80 engage with the ratchet teeth of the first disk member 50.
  • the actuator starts to work.
  • the piston 30 at least partially extends out of the hydraulic chamber under the action of the hydraulic pressure and applies a force to the finger of the diaphragm spring 90.
  • 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.
  • the axial force applied by the diaphragm spring 90 to each actuating pin 110 is reduced or completely eliminated, so that each actuating pin 110 moves axially away from the second disk member 130 under the elastic force of the pin spring 100.
  • each actuating pin 110 to the corresponding pawl 80 is reduced or eliminated, and the reset spring prompts the pawl 80 to rotate to 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.
  • each pawl 80 is constructed with a first engaging portion 83 and a second engaging portion 84
  • 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.
  • FIG. 7 is a schematic diagram showing the engagement mechanism of the clutch device according to the present embodiment in an engaged state and transmitting torque in a first rotational direction.
  • the engagement counterpart 51 abuts against the first engagement portion 83 of the pawl 80 , thereby transmitting the rotational movement of the first disk member 50 to the second disk member 130 in the first rotational direction, that is, transmitting the torque.
  • Fig. 8 is a schematic diagram showing the engagement mechanism of the clutch device according to the present embodiment in an engagement state and transmitting torque in the second rotational direction.
  • the second engagement counterpart 52 of the ratchet teeth of the second disk member 50 abuts against the second engagement portion 84 of the pawl 80, thereby transmitting the rotational motion of the first disk member 50 to the second disk member 130 in the second rotational direction opposite to the first rotational direction, i.e., transmitting torque.
  • Fig. 9 is a schematic diagram showing the engagement mechanism of the clutch device according to the present embodiment in the engagement or disengagement process.
  • Fig. 10 is a schematic diagram showing the engagement mechanism of the clutch device according to the present embodiment in the disengagement state. As shown in Fig. 10, at this time, the engagement portions 83, 84 of each pawl 80 are disengaged from the ratchet teeth of the first disc 50.
  • the clutch device provided according to this embodiment has a compact structure and light weight, can be arranged in a small accommodation space of a vehicle and meets the requirements of current lightweight design.
  • the clutch device of this embodiment can realize bidirectional torque transmission and support engagement applications under the condition of large speed difference.
  • the clutch device of this embodiment can be manufactured in a low-cost manner.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

一种离合装置，包括：第一盘件（50）、第二盘件（130）、接合机构、操纵机构。第一盘件（50）和第二盘件（130）同轴线布置并且能够相对彼此转动；接合机构包括多个棘齿和至少两个棘爪（80），其中，多个棘齿沿圆周方向分布在第一盘件（50）的外周处，至少两个棘爪（80）分别以能相对第二盘件（130）转动的方式安装于第二盘件（130）并且分别能够与棘齿接合或脱离于棘齿；操纵机构包括致动销（110）、销弹簧（100）、膜片弹簧（90）和执行器，其中，致动销（110）能够相对于第二盘件（130）沿轴向移动并且在朝向第二盘件（130）的纵向端部处构造有致动部（112），销弹簧（100）沿弹性作用方向在一端抵靠致动销（110）并且在另一端抵靠第二盘件（130）或者抵靠相对第二盘件（130）固定的构件，膜片弹簧（90）沿弹性作用方向在一端抵靠致动销（110）并且在另一端由执行器致动。

Description

离合装置 技术领域
本申请涉及车辆技术领域。本申请具体地涉及一种离合装置。
背景技术
离合器是车辆传动系中的重要部件。传动系中的扭矩传递路径可以借助离合器连通或断开。在当前的湿式离合器技术中，离合器包括摩擦式离合器和牙嵌式离合器等多种类型。
湿式运行的摩擦式离合器例如参考专利文献WO2020064400A1，其中公开的离合器具有很大的轴向尺寸和径向尺寸，并且该离合器的制造成本较高。牙嵌式离合器例如参考专利文献US007975796B2，其中公开的离合器适用于离合器两端的转速差足够小的情况；一旦转速差较大，则会存在离合器接合失败的风险。
发明内容
因此，本申请的目的在于提供一种结构紧凑并且能够适用于转速差较高情况的离合装置，有利地该离合装置具有较低的制造成本。
根据本申请，上述目的在此通过一种离合装置实现。所述离合装置包括：第一盘件和第二盘件、接合机构以及操纵机构。第一盘件和第二盘件同轴线布置并且能够相对彼此转动。接合机构包括多个棘齿和至少两个棘爪，其中，多个棘齿沿圆周方向分布在第一盘件的外周处；至少两个棘爪分别以能相对第二盘件转动的方式安装于第二盘件并且分别能够与棘齿接合或脱离于棘齿。操纵机构包括致动销、销弹簧、膜片弹簧和执行器，其中，致动销能够相对于第二盘件沿轴向移动并且在朝向第二盘件的纵向端部处构造有致动部，其中，在致动销沿轴向靠近第二盘件时，致动部能够作用于棘爪并使得棘爪与棘齿接合，在致动销沿轴向远离第二盘件时，棘爪脱离于棘齿；销弹簧沿弹性作用方向在一端抵靠致动销并且在另一端抵靠第二盘件或者抵靠相对第二盘件固定的构件；膜片弹簧和执行器，其中， 膜片弹簧沿弹性作用方向在一端抵靠致动销并且在另一端由执行器操纵。
在一种有利的实施方式中，离合装置还包括毂罩，其中，毂罩固定连接于第二盘件并且构造有相对于第一盘件位于背向第二盘件的轴向侧的区段，其中，膜片弹簧以其支撑部支承在区段处、以位于支撑部的径向外侧的外端部抵靠致动销并且以位于支撑部的径向内侧的内端部抵靠执行器。
有利地，第二盘件和/或毂罩由冲压工艺制成。
有利地，执行器构造为液压式执行器。
在此，特别有利地，执行器包括由执行器壳体形成的液压腔和能够借助液压至少部分地伸入或伸出液压腔的活塞，其中，执行器壳体和活塞由塑料制成。
在此，特别有利地，活塞通过轴向轴承抵靠在膜片弹簧的内端部处。
在此，特别有利地，在执行器的径向内部设置有径向轴承，与第一盘件抗旋转连接的轴件能够借助径向轴承能相对转动地支承于壳体。
有利地，销弹簧环绕致动销，其中，销弹簧沿弹性作用方向在一端抵靠构造在致动销处的止挡部并且在另一端抵靠毂罩。
在此，特别有利地，销弹簧构造为波形弹簧。
在一种有利的实施方式中，每个棘爪均构造有第一接合部和第二接合部，每个棘齿均构造有第一接合配对部和的第二接合配对部，其中，第一接合部和第二接合部用于在两个相反的旋转方向上分别与第一接合配对部和第二接合配对部接合。
根据本申请提供的离合装置具有紧凑的结构和较轻的重量，能够布置在车辆狭小的容纳空间并且符合当前轻量化设计的要求。此外，本申请的离合装置能够实现双向的扭矩传递并且支持转速差较大情况下的接合应用。同时，本申请的离合装置能够低成本地制造。
附图说明
下面将参考附图来描述本申请的实施例的特征、优点和技术效果。
图1是根据一个实施例的离合装置在接合状态下的轴向半剖视图；
图2是根据图1所示实施例的离合装置在断开状态下的轴向半剖视图；
图3是根据图1所示实施例的离合装置在的接合机构处的径向剖视图；
图4是根据图1所示实施例的离合装置的接合机构的棘爪的立体图；
图5是根据图1所示实施例的离合装置的操纵机构的致动销的立体图；
图6是根据图4所示的棘爪和根据图5所示的致动销配合作用的示意图；
图7是根据图1所示实施例的离合装置的接合机构在接合状态并且在第一旋转方向上传递扭矩的示意图；
图8是根据图1所示实施例的离合装置的接合机构在接合状态并且在第二旋转方向上传递扭矩的示意图；
图9是根据图1所示实施例的离合装置的接合机构在接合或分离过程中的示意图；
图10是根据图1所示实施例的离合装置的接合机构在分离状态下的示意图。
具体实施方式
图1至图3提供的实施例提供一种离合装置，其能够布置在位于车辆驱动系中的、在驱动装置和从动装置之间的扭矩传递路径上的任意位置处，从而连通或者断开扭矩的传递。
在此，车辆能够是电动车、混合动力车辆或者传统的燃油车。在这种情况下，驱动装置能够是驱动电机和/或内燃机；从动装置能够是车辆驱动轮。在本实施例中，以由驱动电机和/或内燃机驱动车辆驱动轮的扭矩传递方向为例对离合装置的结构和作用方式进行示例性的说明。因此，在本实施例中，与扭矩的“输入”和“输出”相关的术语均基于上述示例的扭矩传递方向，例如将离合装置中从驱动电机和/或内燃机接收扭矩的一端称为输入端，将离合装置中向车辆驱动轮传递扭矩的一端称为输出端。但是本实施例不限定根据本申请的离合装置的应用场景，例如，离合装置也能够应用于能量回收、内燃机起动、电机以发电机模式运行等与上述扭矩传递方向相反的工况。
图1示出了根据一种实施例的离合装置的轴向半剖视图。离合装置包 括：第一盘件50和第二盘件130、接合机构以及操纵机构。
第一盘件50和第二盘件130同轴线布置并且能够相对彼此转动。第一盘件50抗旋转地安装于第一轴件140。在本实施例中，第一轴件140用作离合装置的输入端，第一轴件140能够与车辆的驱动装置连接。在一些其他实施例中，第一轴件140能够是车辆的驱动装置的扭矩输出轴。第二盘件130能够直接或者间接地与第二轴件150抗旋转连接。在本实施例中，第二盘件130与壳体170固定连接，壳体170与第二轴件150例如通过花键抗旋转连接，由此第二盘件130间接地与第二轴件150抗旋转连接。在另外的实施例中，第二盘件130也能够直接地与第二轴件150抗旋转连接。在此，第二轴件能够是离合装置的输出端，也能够是扭矩传递路径上的下游装置的输入轴。
在此，需要说明的是，在本文范围内，除非另有说明，否则术语“轴向”、“径向”和“圆周方向”均参考第一盘件50和第二盘件130的共同的旋转轴线、也即参考离合装置的旋转轴线。具体地，“轴向”为上述旋转轴线的方向或平行于上述旋转轴线的方向。“径向”为垂直于上述旋转轴线并且与上述旋转轴线相交的方向。“圆周方向”为围绕上述旋转轴线的方向。
此外，在本文范围内，术语“抗旋转连接”是指：使得两个部件之间不能够相对彼此旋转、从而能够传递扭矩的连接。例如，当两个部件彼此抗旋转地连接或者一个部件抗旋转地安装于另一个部件时，两个部件能够传递扭矩且能够一起旋转。例如，花键连接可以实现抗旋转连接。又例如，固定连接也可以实现抗旋转连接。在此，不限定抗旋转连接的两个部件是否能够相对彼此轴向运动。
接合机构包括多个棘齿和至少两个棘爪80，其中，多个棘齿沿圆周方向分布在第一盘件50的外周处，至少两个棘爪80分别以能相对第二盘件130转动的方式安装于第二盘件130并且分别能够与棘齿接合或脱离于棘齿。
优选地，棘齿与第一盘件50一体式构造，第一盘件50构造为棘轮。优选地，各个棘齿在圆周方向上均匀地分布在第一盘件50的外周处。
图4示出了根据本实施例的棘爪80的立体图。棘爪80包括转动部81和远离转动部81设置的接合部83、84。优选地，如此将棘爪80安装于第二盘件130，使得各个棘爪80能够分别相对第二盘件130围绕转动部81枢转，在此棘爪80、尤其接合部83、84相对第二盘件130围绕各自固定的轴线摆动。在此，优选地，各个棘爪80枢转的轴线分别平行于离合装置的旋转轴线。备选地，如此将棘爪80安装于第二盘件130，使得各个棘爪80能够分别相对第二盘件130围绕各自非固定的轴线转动。在棘爪80转动到接合位置时，棘爪80的接合部83、84能够与第一盘件50处的棘齿接合，从而第一盘件50和第二盘件130能够共同旋转，也即连通扭矩传递路径。在棘爪80转动到断开位置时，棘爪80的接合部83、84与第一盘件50处的棘齿脱耦，由此断开扭矩传递路径。在此，棘爪的数量取决于传递的扭矩。优选地，至少两个棘爪80在圆周方向上均匀分布在第二盘件130处。
在本实施例中，离合装置还包括毂罩120。毂罩120例如通过过盈配合固定连接于第二盘件130。优选地，第二盘件130和/或毂罩120由冲压工艺制成。在此，有利地，第二盘件130和毂罩120彼此固定连接的连接区段设置在第一盘件50的径向外侧。优选地，毂罩120构造有相对于第一盘件50位于背向第二盘件130的轴向侧的区段。由此，毂罩120以及第二盘件能够保护接合机构、如第一盘件50的棘齿区域以及棘爪80并且有利于后面将详细阐述的零部件的紧凑布置。
棘爪80在接合位置和断开位置之间的旋转运动在一个转动方向上通过操纵机构实现并且在另一方向上通过未详细示出的复位弹簧实现。在此，复位弹簧沿其弹性作用方向张紧在棘爪80和第二盘件130之间。
在此，操纵机构包括致动销110、销弹簧100、膜片弹簧90和执行器。
图5示出了根据本实施例的致动销110的立体图。致动销110具体基本呈圆柱体的主体111。致动销110能够相对于第二盘件130沿轴向移动。为此，优选地，致动销110在轴向上能够至少部分地伸入或伸出于由第二盘件130形成的容纳腔中。如图5所示，致动销110在朝向第二盘件130的纵向端部处构造有致动部112。再如图4所示，棘爪80在远离转动部 81的位置处还构造有致动配对部82。棘爪80的致动配对部82和致动销110的致动部112构造为能够配合作用的作用面，使得在致动销110沿着致动销110的纵向、在本实施例中也即离合装置的轴向移动时能够促使棘爪80转动，参见由图6示出的棘爪80和致动销110配合作用的示意图。有利地，棘爪80的致动配对部82和致动销110的致动部112构造为配对的斜面。有利地，致动销110的致动部112由倒角实现。
致动销110沿其纵向的移动在一个方向上由销弹簧100实现。如图1所示，销弹簧100构造为波形弹簧，并且销弹簧100环绕致动销110。销弹簧100沿弹性作用方向张紧在构造在致动销110处的止挡部113和毂罩120之间。
致动销110沿其纵向的移动在另一个方向上由执行器实现。在本实施例中，在执行器和各个致动销110之间的扭矩传递路径上还设置有膜片弹簧90。在本实施例中，参考图1，膜片弹簧90呈环形盘状并且包括圆环形的边缘区段多个沿圆周方向分布的指部，其中，指部从边缘区段曲折地朝向径向内侧延伸。膜片弹簧90在此通过定心螺栓70可沿轴向相对运动及变形地安装于毂罩120的相对于第一盘件50位于背向第二盘件130的轴向侧的区段。膜片弹簧90在此用作杠杆弹簧，其类似杠杆地作用在执行器和致动销110之间。膜片弹簧90以其支撑部经由支撑环60支承在毂罩120的上述区段处，该支承点形成杠杆支点。膜片弹簧90以位于支撑部的径向外侧的外端部、在此即环形的边缘区段抵靠致动销110；膜片弹簧90以位于支撑部的径向内侧的内端部、在此即指部的自由端抵靠执行器的执行构件30。
在本实施例中，执行器构造为液压式执行器。特别有利地，执行器包括由执行器壳体10形成的液压腔和能够借助液压至少部分地伸入或伸出液压腔的活塞30。执行器包括动态密封件20以防止液压液泄漏。优选地，执行器壳体10和活塞30由塑料制成。在此，活塞30通过轴向轴承40抵靠在膜片弹簧90的指部处。
在本实施例中，在执行器的径向内部设置有径向轴承，第一轴件140能够借助径向轴承能相对转动地支承于壳体160。由此可以实现离合装置 的紧凑结构。
图1和图2分别示出本实施例的离合装置在接合状态和断开状态下的轴向半剖视图。图3示出本实施例的离合装置在的接合机构处的径向剖视图。根据本实施例的离合装置采用常接合的方案。在车辆行驶时，离合装置通常为接合状态，只有在操纵执行器时才断开。
参考图1和图3，在离合装置接合时，执行器不工作，此时活塞30至少部分地伸入在液压腔中并且不会向膜片弹簧90的指部施加作用力或者仅以很小的力压靠膜片弹簧90的指部。由于指部不受力或者仅受到很小的力，导致以杠杆弹簧作用的膜片弹簧90在圆环形的边缘区段抵靠各个致动销110，使得各个致动销110沿轴向克服销弹簧100的弹性力朝向第二盘件130移动或者保持在靠近第二盘件的位置处。各个致动销110通过致动部112将轴向力施加到对应的棘爪80的致动配对部82处，从而促使棘爪80克服复位弹簧的弹性力转动到或者保持在接合位置。在接合位置处，各个棘爪80的接合部83、84与第一盘件50的棘齿接合。
参考图2，在离合装置需要断开时，执行器开始工作。此时活塞30在液压的作用下至少部分地伸出液压腔并且向膜片弹簧90的指部施加作用力。由于指部受力，导致以杠杆弹簧作用的膜片弹簧90在圆环形的边缘区段在轴向上沿远离第二盘件的方向移动和/变形。此时膜片弹簧90向各个致动销110施加的轴向力减少或完全消失，使得各个致动销110沿轴向在销弹簧100的弹性作用力下远离第二盘件130地移动。各个致动销110施加到对应的棘爪80的作用力减小或消失，此时复位弹簧促使棘爪80转动到断开位置。在断开位置处，各个棘爪80的接合部83、84脱离于第一盘件50的棘齿。
根据本实施的一种设计，每个棘爪80均构造有第一接合部83和第二接合部84，每个棘齿均构造有第一接合配对部51和的第二接合配对部52，其中，第一接合部83和第二接合部84用于在两个相反的旋转方向上分别与第一接合配对部51和第二接合配对部52接合。
图7示出根据本实施例的离合装置的接合机构在接合状态并且在第一旋转方向上传递扭矩的示意图。如图7所示，第一盘件50的棘齿的第一 接合配对部51抵靠棘爪80的第一接合部83，由此在第一旋转方向上将第一盘件50的旋转运动传递到第二盘件130，也即传递扭矩。
图8示出根据本实施例的离合装置的接合机构在接合状态并且在第二旋转方向上传递扭矩的示意图。如图8所示，第二盘件50的棘齿的第二接合配对部52抵靠棘爪80的第二接合部84，由此在与第一旋转方向相反的第二旋转方向上将第一盘件50的旋转运动传递到第二盘件130，也即传递扭矩。
图9示出根据本实施例的离合装置的接合机构在接合或分离过程中的示意图。图10示出根据本实施例的离合装置的接合机构在分离状态下的示意图。如图10所示，此时各个棘爪80的接合部83、84脱离于第一盘件50的棘齿。
根据本实施例提供的离合装置具有紧凑的结构和较轻的重量，能够布置在车辆狭小的容纳空间并且符合当前轻量化设计的要求。此外，本实施例的离合装置能够实现双向的扭矩传递并且支持转速差较大情况下的接合应用。同时，本实施例的离合装置能够以低成本的方式制造。
显然，本申请的上述实施例仅仅是为了清楚说明本申请所作的举例，而并非是对本申请的实施方式的限定。对于所属领域的普通技术人员来说，在上述说明的基础上还可以做出其它不同形式的变化或变动。这里无需也无法对所有的实施方式予以穷举。凡在本申请的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本申请权利要求的保护范围之内。在本申请的描述中，需要说明的是，术语“第一”、“第二”、仅用于描述目的，而不能理解为指示或暗示相对重要性。
附图标记列表
10    执行器壳体
20    密封件
30    活塞
40    推力轴承
50    第一盘件
51    第一接合配对部
52    第二接合配对部
60    支撑环
70    定心螺栓
80    棘爪
81    转动部
82    致动配对部
83    第一接合部
84    第二接合部
90    膜片弹簧
100   销弹簧
110   致动销
111   主体
112   致动部
113   止挡部
120   毂罩
130   第二盘件
140   第一轴件
150   第二轴件
160   壳体
170   壳体

Claims (10)

  1. 一种离合装置，包括：
    第一盘件(50)和第二盘件(130)，其同轴线布置并且能够相对彼此转动；
    接合机构，包括：
    多个棘齿，其沿圆周方向分布在所述第一盘件(50)的外周处，
    至少两个棘爪(80)，其分别以能相对所述第二盘件(130)转动的方式安装于所述第二盘件(130)并且分别能够与所述棘齿接合或脱离于所述棘齿；
    操纵机构，包括：
    致动销(110)，其能够相对于所述第二盘件(130)沿轴向移动并且在朝向所述第二盘件(130)的纵向端部处构造有致动部(112)，其中，在所述致动销(110)沿轴向靠近所述第二盘件(130)时，所述致动部(112)能够作用于所述棘爪(80)并使得所述棘爪(80)与所述棘齿接合，在所述致动销(110)沿轴向远离所述第二盘件(130)时，所述棘爪(80)脱离于所述棘齿，
    销弹簧(100)，其沿弹性作用方向在一端抵靠所述致动销(110)并且在另一端抵靠所述第二盘件(130)或者抵靠相对所述第二盘件(130)固定的构件，
    膜片弹簧(90)和执行器，其中，所述膜片弹簧(90)沿弹性作用方向在一端抵靠所述致动销(110)并且在另一端由所述执行器操纵。
  2. 根据权利要求1所述的离合装置，其中，
    所述离合装置还包括毂罩(120)，其中，所述毂罩(120)固定连接于所述第二盘件(130)并且构造有相对于所述第一盘件(50)位于背向所述第二盘件(130)的轴向侧的区段，
    其中，膜片弹簧(90)以其支撑部支承在所述区段处、以位于所述支撑部的径向外侧的外端部抵靠所述致动销(110)并且以位于所述支撑部的径向内侧的内端部抵靠所述执行器。
  3. 根据权利要求2所述的离合装置，其中，
    所述第二盘件(130)和/或所述毂罩(120)由冲压工艺制成。
  4. 根据权利要求2所述的离合装置，其中，
    所述执行器构造为液压式执行器。
  5. 根据权利要求4所述的离合装置，其中，
    所述执行器包括由执行器壳体(10)形成的液压腔和能够借助液压至少部分地伸入或伸出所述液压腔的活塞(30)，其中，所述执行器壳体(10)和所述活塞(30)由塑料制成。
  6. 根据权利要求4所述的离合装置，其中，
    所述活塞(30)通过轴向轴承(40)抵靠在所述膜片弹簧(90)的内端部处。
  7. 根据权利要求4所述的离合装置，其中，
    在所述执行器的径向内部设置有径向轴承，与所述第一盘件(50)抗旋转连接的轴件(140)能够借助所述径向轴承能相对转动地支承于壳体。
  8. 根据权利要求2所述的离合装置，其中，
    所述销弹簧(100)环绕所述致动销(110)，其中，所述销弹簧(100)沿弹性作用方向在一端抵靠构造在所述致动销(110)处的止挡部(113)并且在另一端抵靠所述毂罩(120)。
  9. 根据权利要求8所述的离合装置，其中，
    所述销弹簧(100)构造为波形弹簧。
  10. 根据权利要求1所述的离合装置，其中，
    每个所述棘爪(80)均构造有第一接合部(83)和第二接合部(84)，每个所述棘齿均构造有第一接合配对部(51)和的第二接合配对部(52)，其中，所述第一接合部(83)和所述第二接合部(84)用于在两个相反的旋转方向上分别与第一接合配对部(51)和所述第二接合配对部(52)接合。
PCT/CN2023/118799 2023-09-14 2023-09-14 离合装置 Ceased WO2025054897A1 (zh)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB806804A (en) * 1955-02-14 1958-12-31 John Telford Ratcliffe Improvements in or relating to rotational ratchet and pawl clutch mechanism
CN108591302A (zh) * 2018-05-28 2018-09-28 瀚伦贝尔通用航空器有限公司 一种旋翼传动的棘轮装置
CN114483949A (zh) * 2022-01-26 2022-05-13 向永川 自动档变速器
WO2023016584A2 (zh) * 2022-11-02 2023-02-16 舍弗勒技术股份两合公司 解耦装置及分动箱

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB806804A (en) * 1955-02-14 1958-12-31 John Telford Ratcliffe Improvements in or relating to rotational ratchet and pawl clutch mechanism
CN108591302A (zh) * 2018-05-28 2018-09-28 瀚伦贝尔通用航空器有限公司 一种旋翼传动的棘轮装置
CN114483949A (zh) * 2022-01-26 2022-05-13 向永川 自动档变速器
WO2023016584A2 (zh) * 2022-11-02 2023-02-16 舍弗勒技术股份两合公司 解耦装置及分动箱

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