WO2023206064A1 - 换挡组件及变速箱 - Google Patents

换挡组件及变速箱 Download PDF

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Publication number
WO2023206064A1
WO2023206064A1 PCT/CN2022/089251 CN2022089251W WO2023206064A1 WO 2023206064 A1 WO2023206064 A1 WO 2023206064A1 CN 2022089251 W CN2022089251 W CN 2022089251W WO 2023206064 A1 WO2023206064 A1 WO 2023206064A1
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WO
WIPO (PCT)
Prior art keywords
shift
fork
shift fork
finger
gear
Prior art date
Application number
PCT/CN2022/089251
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English (en)
French (fr)
Inventor
戚超乾
Original Assignee
舍弗勒技术股份两合公司
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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 PCT/CN2022/089251 priority Critical patent/WO2023206064A1/zh
Publication of WO2023206064A1 publication Critical patent/WO2023206064A1/zh

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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
    • F16H—GEARING
    • F16H53/00—Cams ; Non-rotary cams; or cam-followers, e.g. rollers for gearing mechanisms
    • 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
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/02—Selector apparatus
    • 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
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/02—Selector apparatus
    • F16H59/04—Ratio selector apparatus
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/32—Electric motors actuators or related electrical control means therefor
    • 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
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
    • F16H63/16—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism
    • F16H63/18—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism the final actuating mechanism comprising cams
    • 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
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • 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
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/32—Gear shift yokes, e.g. shift forks

Definitions

  • the present invention relates to the technical field of gearboxes, and in particular, to a shifting assembly and a gearbox.
  • the fork fingers 32 on the fork 30 are usually in a symmetrical shape, such as a rhombus or a circle.
  • the shift fork finger 32 is in contact with the shift profile.
  • the contact area between the inner walls of the groove 11 is too small, causing the position where the shift fork finger 32 and the shift wire groove 11 are in contact with a strong pressure, resulting in a large degree of wear and tear, resulting in damage to the shift fork finger 32 and the shift hub 10 Short service life.
  • the width of the shift type wire trough 11 is narrow, so the space for accommodating the shift fork fingers 32 is limited.
  • the symmetrical shift fork fingers 32 further limit the space for the shift fork fingers 32.
  • the size of the finger 32 results in a reduction in the volume of the shift fork finger 32, which affects the overall strength and stiffness of the shift fork 30.
  • the present invention provides a shifting assembly and a gearbox.
  • the present invention provides a shift assembly, which includes: a shift hub, the outer wall of which is provided with a shift-type wire groove; and a shift fork, including a shift fork finger, and the shift fork shifts
  • the finger is located in the shift wire groove of the shift hub and slides along the shift wire groove, thereby driving the shift fork to move in the axial direction, wherein the shift fork finger is a non-axisymmetric block shape structure.
  • the fork fingers have a centrally symmetrical block structure.
  • the side wall of the shift fork finger includes a vertical portion and an inclined portion arranged at an included angle
  • the shift type wire groove includes a straight section and an inclined section arranged at an included angle in the unfolded state.
  • the vertical portion includes a first vertical portion and a second vertical portion that are parallel to each other and centrally symmetrical;
  • the inclined portion includes a first inclined portion and a second inclined portion that are parallel to each other and centrally symmetrical.
  • a first curved portion is formed between the first vertical portion and the first inclined portion and between the second vertical portion and the second inclined portion.
  • a second curved portion is provided between the first vertical portion and the second inclined portion, and/or between the first inclined portion and the second vertical portion.
  • the second curved portion is composed of one or more arc segments.
  • a first included angle is formed between the vertical portion and the inclined portion, and a second included angle is formed between the straight section and the inclined section; wherein, the first included angle and The second included angles are equal.
  • the shift fork further includes a shift fork sleeve and a shift fork shaft.
  • the shift fork sleeve is sleeved on the shift fork shaft.
  • the shift fork sleeve can be moved axially on the shift fork shaft. Reciprocating movement, the axial direction of the shift fork sleeve is parallel to the rotation axis of the shift hub; wherein, the shift fork finger is provided at the end of the shift fork sleeve, and the vertical portion is in line with the rotation axis of the shift hub.
  • the end surface of the shift fork sleeve is flush.
  • the shift fork further includes a shift fork foot.
  • the shift fork foot is provided on a side of the shift fork sleeve away from the shift fork finger.
  • the shift fork foot is used to drive with the synchronizer. connect.
  • the present invention provides a gearbox, which is characterized by including the shifting assembly as described in the first aspect.
  • the technical solutions provided by the embodiments of the present invention can include the following beneficial effects: through the asymmetric structure of the shift fork fingers, the contact area between the shift fork fingers and the shift type wire groove can be increased, local wear is small, and extended The service life of the shift fork fingers.
  • the non-axisymmetric structure of the fork fingers can also increase the volume of the fork fingers, increase the strength and stiffness of the fork fingers, and further extend the service life of the fork fingers.
  • Figure 1 is a three-dimensional structural diagram of a shift assembly in the related art
  • Figure 2 is an expanded schematic diagram of a shift type wire trough in the related art
  • Figure 3 is a three-dimensional structural diagram of a shift fork in the related art
  • Figure 4 is a top view outline view of the shift fork fingers in the related art
  • Figure 5 is a schematic diagram of the cooperation between the shift fork finger and the shift type cable trough in the related art
  • Figure 6 is a three-dimensional structural view of a shift fork according to an exemplary embodiment
  • Figure 7 is a top profile view of a fork finger according to an exemplary embodiment
  • FIG. 8 is a schematic diagram showing the cooperation between the shift fork finger and the shift type wire groove according to an exemplary embodiment.
  • the present invention provides a shifting assembly 100.
  • the shifting assembly 100 can be applied in a dual-clutch transmission or a hybrid transmission.
  • the shift assembly 100 may be drivingly connected with a shift motor (not shown in the figure), and the shift motor provides driving force to the shift assembly 100 .
  • the shift assembly 100 includes a shift hub 10 , a shift fork shaft 20 and a shift fork 30 .
  • the shift hub 10 is generally in a cylindrical structure, and the outer wall of the shift hub 10 is provided with a shift wire slot 11 .
  • the shift wire groove 11 is spiral-shaped and extends along the axial direction of the shift hub 10 .
  • the shift hub 10 is usually drivingly connected to the shift motor.
  • a reduction gear assembly (not shown in the figure) is provided between the shift motor and the shift hub 10.
  • the shift hub 10 is provided with a synchronously rotating shift hub gear (Fig. (not shown in ), the reduction gear assembly meshes with the shift hub gear.
  • the shift motor transmits the rotational driving force to the reduction gear assembly, and the reduction gear assembly reduces the rotational driving force and increases the torque before transmitting it to the shift hub gear, thereby driving the shift hub gear to rotate, and then driving the shift hub 10 around the rotation axis X2 Rotate.
  • the shift-type wire trough 11 includes a plurality of straight sections 111 and an inclined section 112.
  • the straight sections 111 and the inclined sections 112 are arranged at intervals and are staggered, and the plurality of straight sections 111 are parallel to each other.
  • the straight line segment 111 extends along the circumferential direction of the shift hub 10 and is parallel to the cross section of the shift hub 10.
  • the multiple straight line segments 111 are located in different and different positions of the shift hub 10. on parallel cross sections.
  • the straight line segment 111 represents the gear position (such as the first gear position, the second gear position or the neutral position) and the parking position.
  • the straight line segment S1 represents the first gear position
  • the straight line segment S2 represents the neutral position
  • the straight line segment S3 represents the second gear position
  • the straight line segment S4 represents the parking position.
  • the inclined section 112 is arranged at an angle with the straight section 111.
  • the inclined section 112 is shifted from the second gear position to the parking position.
  • Inclined sections 112 arranged at an included angle are arranged between the straight sections 111, which can make the first gear position transition to the neutral position (others are similar and will not be described again). This way, the multiple straight sections 111 can also be kept along the direction of the shift hub 10. It extends circumferentially and is parallel to the cross section of the shift hub 10 .
  • the included angle between the inclined segment 112 and the straight segment 111 forms a second included angle ⁇ 2.
  • the value of the second included angle ⁇ 2 can be set according to the actual design situation and is not specifically limited here.
  • the second included angle ⁇ 2 is an obtuse angle less than 180°.
  • the shift fork shaft 20 can be supported or fixed on the casing of the gearbox (not shown in the figure).
  • the central axis of the shift fork shaft 20 coincides with the axial direction X1 of the shift fork sleeve 31 and is aligned with the rotation axis of the shift hub 10 X2 is parallel, and the shift fork shaft 20 can be used as a guide rail for the linear reciprocation motion of the shift fork 30 .
  • the shift fork 30 includes a shift fork sleeve 31 , a shift fork finger 32 and a shift fork foot 33 , wherein the shift fork finger 32 and the shift fork foot 33 are both arranged on the shift fork sleeve 31 .
  • the shift fork sleeve 31 is sleeved on the shift fork shaft 20 and can reciprocate along the axial direction X1 of the shift fork shaft 20; in the following embodiments of the present invention, the shift fork sleeve 31 is sleeved on the shift fork shaft 20.
  • at least one end of the shift fork sleeve 31 can be supported or fixed in a hole in the gearbox housing, and perform axial reciprocating movement in the X1 direction relative to the gearbox housing, where No specific details.
  • the shift fork finger 32 is fixed on the shift fork sleeve 31 and is located in the shift wire slot 11 of the shift hub 10 and slides along the shift wire slot 11.
  • the shift fork finger 32 and the shift wire slot 11 form a Cylindrical cam motion structure.
  • the shift fork leg 30 is arranged on the side of the shift fork sleeve 31 away from the shift fork finger 32.
  • the shift fork leg 33 is used to insert into the gear sleeve of the synchronizer to transmit the shifting action to the synchronizer.
  • a pair of meshing gears (including the driving gear and the driven gear) that allow the synchronizer to select shifting gears.
  • the synchronizer is a component in the transmission. When the transmission shifts gears, the driving gear and the driven gear are forced to synchronize, so that the two gears are quickly combined to avoid noise and vibration.
  • the fork fingers 32 have a non-axisymmetric block structure. Furthermore, in some embodiments, the fork fingers 32 may have a centrally symmetrical block structure.
  • the non-axially symmetrical structure of the shift fork finger 32 can increase the contact between the shift fork finger 32 and the inner wall of the straight section 111 area, under the same pressure, the pressure of the inner wall of the straight section 111 on the fork fingers 32 can be reduced, thereby reducing the contact stress, reducing local wear, and extending the service life of the fork fingers 32.
  • the area of the fork finger 32 is increased as shown in Figure 7.
  • the fork finger 32 can be enlarged. 32 in volume, thereby increasing the strength and rigidity of the shift fork finger 32 and further extending the service life of the shift fork finger 32.
  • the fork finger 32 includes a sliding surface 320 and a side wall, where the sliding surface 320 is in contact with the bottom wall of the shift wire groove 11 , and the sliding surface 320 may be a flat surface. It can also be an arcuate surface matching the outer wall of the shift hub 10 .
  • the side is located between the sliding surface 320 and the outer wall of the shift fork sleeve 31, and the side wall is vertically arranged.
  • the direction in which the side walls are vertically arranged refers to the direction perpendicular to the paper surface as shown in Figure 7 .
  • the side wall of the shift fork finger 32 includes a vertical portion and an inclined portion arranged at an included angle.
  • the shift wire groove 11 includes a straight section 111 and an inclined section 112 arranged at an included angle in the unfolded state.
  • the vertical part and the inclined part are not absolute straight lines, but may be approximately straight-line vertical parts and inclined parts composed of a plurality of short curves.
  • the vertical part includes a first vertical part 321 and a second vertical part 322 that are parallel to each other and centrally symmetrical;
  • the inclined part includes a first inclined part 323 and a second inclined part 324 that are parallel to each other and centrally symmetrical.
  • a first curved portion 325 is formed between the first vertical portion 321 and the first inclined portion 323 and between the second vertical portion 322 and the second inclined portion 324.
  • the first bending portion 325 can prevent the shift fork finger 32 from being too sharp, causing mutual wear between the side walls of the shift fork finger 32 and the inner wall of the shift groove 11 , thereby extending the service life of the shift fork 30 and the shift hub 10 .
  • a second curved portion 326 is provided between the first vertical portion 321 and the second inclined portion 324, and/or between the first inclined portion 323 and the second vertical portion 322.
  • the second curved portion 326 may be composed of an arc and/or a straight line.
  • the second curved portion 326 is composed of an arc segment, and the two second curved portions 326 may be centrally symmetrical. Non-centrosymmetric settings are also possible.
  • the arrangement of the second curved portion 326 can create a gap between the first vertical portion 321 and the second inclined portion 324 (upper left corner as shown in Figure 7) and between the second vertical portion 322 and the first inclined portion 323 (as shown in Figure 7). 7), becomes more rounded, so that when the shift fork finger 32 slides in the shift wire groove 11 of the shift hub 10, it can avoid being too sharp and damaging the inner wall of the shift wire groove 11, and This makes the movement of the shift fork finger 32 in the shifting wire slot 11 smoother.
  • the second curved portion 326 is composed of one or more arcuate segments.
  • the second curved portion 326 is composed of multiple arc-shaped segments, and the multiple arc-shaped segments refer to different curvatures.
  • the second bending portion 326 is located at the upper left corner and the lower right corner shown in FIG. 7 , and the two second bending portions 326 are arranged symmetrically about the central axis.
  • the number of arc-shaped segments and the curvature of the arc-shaped segments of the second bending portion 326 can be set according to actual design requirements, and are not specifically limited here.
  • the second bending portion 326 composed of multiple arc-shaped segments can increase the strength of the side wall at the second bending portion 326 .
  • the curved portion composed of multiple arc-shaped segments can increase the area of the sliding surface 320 to increase the strength and stiffness of the entire shift fork finger 32 and extend the service life of the shift fork finger 32 and even the shift fork 30 .
  • a first included angle ⁇ 1 is formed between the vertical part and the inclined part.
  • a second included angle ⁇ 2 is formed between the straight segment 111 and the inclined segment 112; the first included angle ⁇ 1 and the second included angle ⁇ 2 are formed between the straight segment 111 and the inclined segment 112.
  • the angle ⁇ 2 is equal.
  • the first included angle ⁇ 1 can also be understood as an obtuse angle less than 180°.
  • the first included angle ⁇ 1 and the second included angle ⁇ 2 may be equal and set at opposite angles. As shown in FIG. 8 , when the fork finger 32 is located at the corner of the straight segment 111 and the inclined segment 112 , the fork finger 32 Before entering the inclined section 112, the vertical part can be in contact with the inner wall of the straight section 111. When the fork finger 32 turns into the inclined section 112, the inclined part of the fork finger 32 is in contact with the inner wall of the inclined section 112. .
  • part of the side wall of the shift fork finger 32 is in contact with the inner wall of the shift type wire slot 11, thereby increasing the size of the shift fork finger.
  • the contact area between 32 and the shift wire groove 11 reduces the mutual wear between the two and prolongs the life of the shift fork finger 32 and the shift hub 10.
  • the vertical portion and the inclined portion are not absolute straight lines, but can be approximately straight-line vertical portions and inclined portions composed of a plurality of short curves. Therefore, when the vertical part and the inclined part are not absolutely straight lines, the first included angle ⁇ 1 formed between the vertical part and the inclined part may be the angle formed by the plane where the vertical part and the inclined part are generally located.
  • first included angle ⁇ 1 and the second included angle ⁇ 2 may not be equal in an absolute sense, but may be substantially or approximately equal.
  • the fork finger 32 is disposed at the end of the fork sleeve 31 , and the vertical portion is flush with the end surface of the fork sleeve 31 .
  • the vertical portion may not be flush with the end surface of the fork sleeve 31 , which is not specifically limited here.
  • the fork finger 32 can be arranged at any position in the middle of the fork sleeve 31 according to actual use requirements, which is not specifically limited here.
  • the present invention also provides a gearbox including the above-mentioned shifting assembly 100 .
  • the shift assembly 100 can be applied in any position where shifting is required, including but not limited to gearboxes.
  • the transmission can be a dual-clutch transmission or a hybrid transmission.
  • first, second, etc. are used to describe various structures, but these structures should not be limited to these terms. These terms are used only to distinguish structures of the same type from each other and do not imply a specific order or importance. In fact, expressions such as “first” and “second” can be used interchangeably.
  • a first structure may also be referred to as a second structure, and similarly, the second structure may also be referred to as a first structure.
  • connection includes a direct connection without other components between the two, and also includes an indirect connection with other elements between the two.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear-Shifting Mechanisms (AREA)
  • Structure Of Transmissions (AREA)

Abstract

一种换挡组件及变速箱，换挡组件包括：换挡毂（10），其外壁设置有换挡型线槽（11）；以及拨叉（30），包括拨叉拨指（32），拨叉拨指（32）位于换挡毂（10）的换挡型线槽（11）内并沿换挡型线槽（11）滑动从而带动拨叉沿轴向移动，其中，拨叉拨指（32）为非轴对称型块状结构。通过非轴对称型块状结构的拨叉拨指（32），不仅可以增大拨叉拨指（32）与换挡型线槽（11）之间的接触面积，局部磨损小；另外还可以增大拨叉拨指（32）的体积，从而提高拨叉拨指（32）的强度与刚度，总体上可以延长拨叉拨指（32）的使用寿命。

Description

换挡组件及变速箱 技术领域
本发明涉及变速箱技术领域，尤其涉及一种换挡组件及变速箱。
背景技术
相关技术中，如图3至图5所示，拨叉30上的拨叉拨指32通常为对称形状，例如菱形或圆形。然而当拨叉拨指32位于换挡毂10的换挡型线槽11的空档或在档保持(一档、二挡或驻车挡)位置时，拨叉拨指32与换挡型线槽11的内壁之间的接触面积太小，导致拨叉拨指32与换挡型线槽11接触的位置受到的压强大，因此磨损程度大，导致拨叉拨指32及换挡毂10的使用寿命短。
另外，换挡型线槽11的宽度较窄，因此容纳拨叉拨指32的空间有限，当拨叉拨指32为对称性形状时，对称型的拨叉拨指32进一步限制了拨叉拨指32的尺寸大小，导致拨叉拨指32的体积减少，影响拨叉30整体的强度和刚度。
发明内容
为克服相关技术中存在的问题，本发明提供一种换挡组件及变速箱。
根据本发明实施例的第一方面，本发明提供一种换挡组件，包括：换挡毂，其外壁设置有换挡型线槽；以及拨叉，包括拨叉拨指，所述拨叉拨指位于所述换挡毂的所述换挡型线槽内并沿所述换挡型线槽滑动，从而带动拨叉沿轴向移动，其中，所述拨叉拨指为非轴对称型块状结构。
在一些实施例中，所述拨叉拨指为中心对称型的块状结构。
在一些实施例中，所述拨叉拨指的侧壁包括呈夹角设置的竖直部和倾斜部，所述换挡型线槽在展开状态下包括呈夹角设置的直线段和倾斜段；其中，当所述拨叉拨指位于所述换挡型线槽的所述直线段时，所述拨叉拨 指的所述竖直部与所述直线段处的内壁抵接并贴合；当所述拨叉拨指位于所述换挡型线槽的所述倾斜部时，所述拨叉拨指的所述倾斜部与所述倾斜段处的内壁抵接并贴合。
在一些实施例中，所述竖直部包括相互平行且中心对称的第一竖直部和第二竖直部；所述倾斜部包括相互平行且中心对称的第一倾斜部和第二倾斜部；其中，所述第一竖直部和所述第一倾斜部之间以及所述第二竖直部和所述第二倾斜部之间形成第一弯曲部。
在一些实施例中，所述第一竖直部和所述第二倾斜部之间，和/或所述第一倾斜部和所述第二竖直部之间设置有第二弯曲部。
在一些实施例中，所述第二弯曲部由一个或多个弧形段组成。
在一些实施例中，所述竖直部和所述倾斜部之间形成第一夹角，所述直线段和所述倾斜段之间形成第二夹角；其中，所述第一夹角和所述第二夹角相等。
在一些实施例中，所述拨叉还包括拨叉套筒和拨叉轴，所述拨叉套筒套设在拨叉轴上，所述拨叉套筒可在拨叉轴上沿轴向往复移动，所述拨叉套筒的轴向与所述换挡毂的转动轴平行；其中，所述拨叉拨指设置在所述拨叉套筒的端部，且所述竖直部与所述拨叉套筒的端面平齐。
在一些实施例中，所述拨叉还包括拨叉脚，所述拨叉脚设置在所述拨叉套筒远离所述拨叉拨指的一面，所述拨叉脚用于与同步器传动连接。
根据本发明实施例的第二方面，本发明提供一种变速箱，其特征在于，包括如第一方面所述的换挡组件。
本发明的实施例提供的技术方案可以包括以下有益效果：通过拨叉拨指的非对称性结构，可以增大拨叉拨指与换挡型线槽之间的接触面积，局部磨损小，延长拨叉拨指的使用寿命。通过拨叉拨指的非轴对称结构，还可以增大拨叉拨指的体积，增大拨叉拨指的强度与刚度，进一步延长拨叉拨指的使用寿命。
附图说明
此处的附图被并入说明书中并构成本说明书的一部分，示出了符合本 发明的实施例，并与说明书一起用于解释本发明的原理。
图1是相关技术中换挡组件的立体结构图；
图2是相关技术中换挡型线槽的展开示意图；
图3是相关技术中拨叉的立体结构图；
图4是相关技术中拨叉拨指的俯视轮廓图；
图5是相关技术中拨叉拨指与换挡型线槽的配合示意图；
图6是根据一示例性实施例示出的拨叉的立体结构图；
图7是根据一示例性实施例示出的拨叉拨指的俯视轮廓图；
图8是根据一示例性实施例示出的拨叉拨指与换挡型线槽的配合示意图。
具体实施方式
这里将详细地对示例性实施例进行说明，其示例表示在附图中。下面的描述涉及附图时，除非另有表示，不同附图中的相同数字表示相同或相似的要素。以下示例性实施例中所描述的实施方式并不代表与本发明相一致的所有实施方式。相反，它们仅是与如所附权利要求书中所详述的、本发明的一些方面相一致的装置和方法的例子。
为解决上述技术问题，本发明提供一种换挡组件100。换挡组件100可以应用于双离合变速箱或混动动力变速箱中。
换挡组件100可以与换挡电机(图中未显示)传动连接，换挡电机向换挡组件100提供驱动力。
如图1所示，换挡组件100包括换挡毂10、拨叉轴20以及拨叉30。
换挡毂10大体呈圆柱形结构，换挡毂10的外壁设置有换挡型线槽11。换挡型线槽11呈螺旋形，且沿换挡毂10的轴向延伸。
换挡毂10通常与换挡电机传动连接，换挡电机与换挡毂10之间设置有减速齿轮组件(图中未示出)，换挡毂10设置有同步旋转的换挡毂齿轮(图中未示出)，减速齿轮组件与换挡毂齿轮啮合。换挡电机将旋转驱动力传递给减速齿轮组件，减速齿轮组件将旋转驱动力降速增扭后传递给换挡毂齿轮，从而驱动换挡毂齿轮旋转，进而驱动换挡毂10绕转动轴X2 旋转。
如图2所示，为换挡型线槽11的展开图。换挡型线槽11在展开状态下，包括多段直线段111和倾斜段112，直线段111与倾斜段112间隔交错设置，且多段直线段111相互平行。而直线段111在实际的圆柱形换挡毂10中，直线段111是沿换挡毂10的周向延伸且与换挡毂10的横切面平行，多段直线段111位于换挡毂10不同且平行的横切面上。
直线段111表示在档位置(例如一档位置、二挡位置或空档位置)以及驻车位置。在本发明的实施例中，直线段S1表示一档位置，直线段S2表示空档位置，直线段S3表示二挡位置，直线段S4表示驻车位置。
倾斜段112与直线段111呈夹角设置，当需要换挡时，例如从一档位置换到空档位置或空档位置换到二挡位置或二挡位置换到驻车位置，通过在两段直线段111之间设置呈夹角设置的倾斜段112，可以使一档位置过渡到空档位置(其他类似，不再赘述)，如此还可以保持多段直线段111均沿换挡毂10的周向延伸且与换挡毂10的横切面平行。
进一步地，倾斜段112与直线段111之间的夹角形成第二夹角θ2。第二夹角θ2的数值可以根据实际设计情况设置，在此不作具体限定。另外，可以理解的是，第二夹角θ2为小于180°的钝角。
拨叉轴20可以支撑或固定在变速箱的壳体(图中未示出)，拨叉轴20的中心轴与拨叉套筒31的轴向X1重合，且与换挡毂10的转动轴X2平行，拨叉轴20可以作为拨叉30直线往复运动的导轨。
拨叉30包括拨叉套筒31、拨叉拨指32和拨叉脚33，其中，拨叉拨指32和拨叉脚33均设置在拨叉套筒31。
拨叉套筒31套设在拨叉轴20且可沿拨叉轴20的轴向X1往复移动；在本发明的以下实施例中，均以拨叉套筒31套设在拨叉轴20为例进行详细说明。当然，在其他一些实施例中，拨叉套筒31的至少一端可以支撑或固定在变速箱的壳体中的孔中，并相对变速箱的壳体进行轴向X1方向的往复运动，在此不具体详细说明。
拨叉拨指32固定在拨叉套筒31，且位于换挡毂10的换挡型线槽11内并沿换挡型线槽11滑动，拨叉拨指32与换挡型线槽11形成圆柱凸轮运 动结构。
当换挡电机驱动换挡毂10旋转时，由于换挡毂10和拨叉轴20无法轴向运动，迫使拨叉拨指32沿换挡型线槽11滑动，从而带动拨叉套筒31沿拨叉轴20的轴向作直线往复运动，如此，将换挡毂10的旋转运动转化为的拨叉30的直线往复运动，从而实现换挡组件100的换挡。
拨叉脚30设置在拨叉套筒31远离拨叉拨指32的一面，拨叉脚33用于插入同步器的齿套，以将换挡动作传递给同步器，通过拨叉30的直线运动使同步器选择换挡的一对啮合齿轮(包括主动齿轮和从动齿轮)。其中，同步器是变速箱中的零部件,在变速器换档时，主动齿轮和从动齿轮强制同步，使两个齿轮迅速结合在一起，避免噪音和振动。
进一步地，如图6至图8所示，拨叉拨指32为非轴对称型块状结构。进一步地，在一些实施例中，拨叉拨指32可以为中心对称型的块状结构。
当拨叉拨指32位于换挡型线槽11的直线段111时，通过拨叉拨指32的非轴对称性结构，可以增大拨叉拨指32与直线段111的内壁之间的接触面积，在同样的压力左右下，可以减小直线段111的内壁对拨叉拨指32的压强，从而使接触应力变小，局部磨损小，延长拨叉拨指32的使用寿命。
另外，通过拨叉拨指32的非轴对称结构，如图7所示的拨叉拨指32的面积增大，在拨叉拨指32高度不变的情况下，可以增大拨叉拨指32的体积，以此增大拨叉拨指32的强度与刚度，进一步延长拨叉拨指32的使用寿命。
在一些实施例中，再如图7所示，拨叉拨指32包括滑动面320和侧壁，其中滑动面320与换挡型线槽11的底壁抵接，滑动面320可以为平面，也可以为与换挡毂10的外壁相匹配的弧形面。侧面位于滑动面320和拨叉套筒31的外壁之间，且侧壁垂直设置。其中，侧壁垂直设置的方向是指图7中所示的垂直于纸面的方向。
拨叉拨指32的侧壁包括呈夹角设置的竖直部和倾斜部，由上述内容可知，换挡型线槽11在展开状态下包括呈夹角设置的直线段111和倾斜 段112。
如图8所示，当拨叉拨指32位于换挡型线槽11的直线段111时，拨叉拨指32的竖直部与直线段111处的内壁抵接并贴合；当拨叉拨指32位于换挡型线槽11的倾斜部时，拨叉拨指32的倾斜部与倾斜段112处的内壁抵接并贴合。
换而言之，无论拨叉拨指32是位于换挡型线槽11的直线段111还是倾斜段112，均有部分侧壁与换挡型线槽11的内壁贴合，从而增大接触面积，减小对拨叉拨指32的磨损，延长拨叉拨指32的使用寿命。
需要说明的是，竖直部和倾斜部并非绝对的直线，可以是由多条短小的曲线组成的近似直线的竖直部和倾斜部。
在一些实施例中，竖直部包括相互平行且中心对称的第一竖直部321和第二竖直部322；倾斜部包括相互平行且中心对称的第一倾斜部323和第二倾斜部324；其中，第一竖直部321和第一倾斜部323之间以及第二竖直部322和第二倾斜部324之间形成第一弯曲部325。
第一弯曲部325可以避免拨叉拨指32过于尖锐，而使得拨叉拨指32的侧壁与换挡型线槽11内壁的相互磨损，从而延长拨叉30及换挡毂10的使用寿命。
在一些实施例中，第一竖直部321和第二倾斜部324之间，和/或第一倾斜部323和第二竖直部322之间设置有第二弯曲部326。
其中，第二弯曲部326可以由弧形和/或直线组成，在本发明的实施例中，第二弯曲部326由弧形段组成，两个第二弯曲部326之间可是中心对称设置，也可以非中心对称设置。
第二弯曲部326的设置，可以使第一竖直部321与第二倾斜部324之间(如图7所示的左上角)以及第二竖直部322与第一倾斜部323(如图7所述的右下角)，变得更加圆滑，使拨叉拨指32在换挡毂10的换挡型线槽11滑动时，避免太过尖锐而损害换挡型线槽11的内壁，且使拨叉拨指32在换挡型线槽11内运动更加流畅。
在一些实施例中，第二弯曲部326由一个或多个弧形段组成。在本实施例中，如图7所示，第二弯曲部326由多个弧形段组成，多个弧形段是 指曲率不同。第二弯曲部326位于图7中所示的左上角和右下角，且两个第二弯曲部326呈中心轴对称设置。
其中，第二弯曲部326的多个弧形段的组成数量及多个弧形段的曲率可以根据实际设计需求进行设置，在此不作具体限定。多段弧形段组成的第二弯曲部326可以增加第二弯曲部326处侧壁的强度。且多段弧形段组成的弯曲部可以增大滑动面320的面积，以增加整个拨叉拨指32的强度和刚度，延长拨叉拨指32乃至拨叉30的使用寿命。
在一些实施例中，竖直部和倾斜部之间形成第一夹角θ1，由上述内容可知，直线段111和倾斜段112之间形成第二夹角θ2；第一夹角θ1和第二夹角θ2相等。同理，第一夹角θ1也可以理解为小于180°的钝角。
第一夹角θ1与第二夹角θ2可以相等且呈对顶角设置，如图8所示，在拨叉拨指32位于直线段111和倾斜段112的拐角时，在拨叉拨指32未进入倾斜段112时，可以使竖直部与直线段111的内壁抵接，当拨叉拨指32拐入倾斜段112后，拨叉拨指32的倾斜部与倾斜段112的内壁抵接。
如此可以使拨叉拨指32无论是在换挡型线槽11的直线段111还是倾斜段112，都有部分侧壁与换挡型线槽11的内壁贴合，从而增大拨叉拨指32与换挡型线槽11的接触面积，减小两者之间的相互磨损，延长拨叉拨指32以及换挡毂10的寿命。
需要说明的是，由上述内容可知，竖直部和倾斜部并非绝对的直线，可以是由多条短小的曲线组成的近似直线的竖直部和倾斜部。因此当竖直部和倾斜部并非绝对直线时，竖直部与倾斜部之间形成的第一夹角θ1可以是竖直部和倾斜部大体所在的面所形成的角度。
另外，第一夹角θ1和第二夹角θ2也可以并非绝对意义上的相等，可以是大致或近似相等。
在一些实施例中，如图7所示，拨叉拨指32设置在拨叉套筒31的端部，且竖直部与拨叉套筒31的端面平齐。在另一些实施例中，竖直部也可以与拨叉套筒31的端面不平齐，在此不作具体限定。另外，在其他的一些实施例中，拨叉拨指32可以根据实际使用的需求，设置在拨叉套筒31的中部的任意位置，在此也不作具体限定。
基于相同的发明构思，本发明还提供一种变速箱，包括上述的换挡组件100。除此之外，换挡组件100可以应用在任何需要换挡的位置，包括但不限于变速箱。另外，变速箱可以为双离合变速箱，也可以为混合动力变速箱。
关于上述实施例中的变速箱中实现的功能的具体方式已经在有关该换挡组件100的实施例中进行了详细描述，此处将不做详细阐述说明。
可以理解的是，本公开中“多个”是指两个或两个以上，其它量词与之类似。“和/或”，描述关联对象的关联关系，表示可以存在三种关系，例如，A和/或B，可以表示：单独存在A，同时存在A和B，单独存在B这三种情况。字符“/”一般表示前后关联对象是一种“或”的关系。单数形式的“一种”、“所述”和“该”也旨在包括多数形式，除非上下文清楚地表示其他含义。
进一步可以理解的是，术语“第一”、“第二”等用于描述各种结构，但这些结构不应限于这些术语。这些术语仅用来将同一类型的结构彼此区分开，并不表示特定的顺序或者重要程度。实际上，“第一”、“第二”等表述完全可以互换使用。例如，在不脱离本公开范围的情况下，第一结构也可以被称为第二结构，类似地，第二结构也可以被称为第一结构。
进一步可以理解的是，术语“中心”、“纵向”、“横向”、“前”、“后”、“上”、“下”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本实施例和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作。
进一步可以理解的是，除非有特殊说明，“连接”包括两者之间不存在其他构件的直接连接，也包括两者之间存在其他元件的间接连接。
进一步可以理解的是，本公开实施例中尽管在附图中以特定的顺序描述操作，但是不应将其理解为要求按照所示的特定顺序或是串行顺序来执 行这些操作，或是要求执行全部所示的操作以得到期望的结果。在特定环境中，多任务和并行处理可能是有利的。
本领域技术人员在考虑说明书及实践这里公开的发明后，将容易想到本公开的其它实施方案。本申请旨在涵盖本公开的任何变型、用途或者适应性变化，这些变型、用途或者适应性变化遵循本公开的一般性原理并包括本公开未公开的本技术领域中的公知常识或惯用技术手段。说明书和实施例仅被视为示例性的，本公开的真正范围和精神由下面的权利范围指出。
应当理解的是，本公开并不局限于上面已经描述并在附图中示出的精确结构，并且可以在不脱离其范围进行各种修改和改变。本公开的范围仅由所附的权利范围来限制。

Claims (10)

  1. 一种换挡组件，其特征在于，包括：
    换挡毂(10)，其外壁设置有换挡型线槽(11)；以及
    拨叉(30)，包括拨叉拨指(32)，所述拨叉拨指(32)位于所述换挡毂(10)的所述换挡型线槽(11)内并沿所述换挡型线槽(11)滑动，从而带动拨叉(30)沿轴向(X1)移动，其中，所述拨叉拨指(32)为非轴对称型块状结构。
  2. 根据权利要求1所述的换挡组件，其特征在于，
    所述拨叉拨指(32)为中心对称型的块状结构。
  3. 根据权利要求1所述的换挡组件，其特征在于，
    所述拨叉拨指(32)的侧壁包括呈夹角设置的竖直部和倾斜部，所述换挡型线槽(11)在展开状态下包括呈夹角设置的直线段(111)和倾斜段(112)；其中，
    当所述拨叉拨指(32)位于所述换挡型线槽(11)的所述直线段(111)时，所述拨叉拨指(32)的所述竖直部与所述直线段(111)处的内壁抵接并贴合；
    当所述拨叉拨指(32)位于所述换挡型线槽(11)的所述倾斜部时，所述拨叉拨指(32)的所述倾斜部与所述倾斜段(112)处的内壁抵接并贴合。
  4. 根据权利要求3所述的换挡组件，其特征在于，
    所述竖直部包括相互平行且中心对称的第一竖直部(321)和第二竖直部(322)；
    所述倾斜部包括相互平行且中心对称的第一倾斜部(323)和第二倾斜部(324)；
    其中，所述第一竖直部(321)和所述第一倾斜部(323)之间以及所述第二竖直部(322)和所述第二倾斜部(324)之间形成第一弯曲部(325)。
  5. 根据权利要求4所述的换挡组件，其特征在于，
    所述第一竖直部(321)和所述第二倾斜部(324)之间，和/或所述第一倾斜部(323)和所述第二竖直部(322)之间设置有第二弯曲部(326)。
  6. 根据权利要求5所述的换挡组件，其特征在于，
    所述第二弯曲部(326)由一个或多个弧形段组成。
  7. 根据权利要求3所述的换挡组件，其特征在于，
    所述竖直部和所述倾斜部之间形成第一夹角(θ1)，所述直线段(111)和所述倾斜段(112)之间形成第二夹角(θ2)；
    其中，所述第一夹角(θ1)和所述第二夹角(θ2)相等。
  8. 根据权利要求1至7中任一项所述的换挡组件，其特征在于，
    所述拨叉(30)还包括拨叉套筒(31)和拨叉轴(20)，所述拨叉套筒(31)套设在拨叉轴(20)上，所述拨叉套筒(31)可在拨叉轴(20)上沿轴向(X1)往复移动，所述拨叉套筒(31)的轴向(X1)与所述换挡毂(10)的转动轴(X2)平行；
    其中，所述拨叉拨指(32)设置在所述拨叉套筒(31)的端部，且所述竖直部与所述拨叉套筒(31)的端面平齐。
  9. 根据权利要求8所述的换挡组件，其特征在于，
    所述拨叉(30)还包括拨叉脚(33)，所述拨叉脚(33)设置在所述拨叉套筒(31)远离所述拨叉拨指(32)的一面，所述拨叉脚(33)用于与同步器传动连接。
  10. 一种变速箱，其特征在于，包括如权利要求1至9中任一项所述的换挡组件。
PCT/CN2022/089251 2022-04-26 2022-04-26 换挡组件及变速箱 WO2023206064A1 (zh)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004084751A (ja) * 2002-08-26 2004-03-18 Kawasaki Heavy Ind Ltd 回転ドラム式のシフトフォーク
WO2010089224A1 (de) * 2009-02-09 2010-08-12 Zf Friedrichshafen Ag Schaltvorrichtung für ein getriebe eines kraftfahrzeugs
CN102022521A (zh) * 2009-09-17 2011-04-20 杭州依维柯汽车变速器有限公司 双离合器自动变速器电动换档执行装置
CN202301905U (zh) * 2011-10-26 2012-07-04 浙江吉利汽车研究院有限公司 一种汽车换挡拨叉的联动结构
CN106958654A (zh) * 2017-05-02 2017-07-18 苏州江南嘉捷机电技术研究院有限公司 电动车变速箱换挡操纵组件
CN211117538U (zh) * 2019-11-25 2020-07-28 蜂巢传动科技河北有限公司 用于车辆的换挡驻车系统以及具有其的车辆

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004084751A (ja) * 2002-08-26 2004-03-18 Kawasaki Heavy Ind Ltd 回転ドラム式のシフトフォーク
WO2010089224A1 (de) * 2009-02-09 2010-08-12 Zf Friedrichshafen Ag Schaltvorrichtung für ein getriebe eines kraftfahrzeugs
CN102022521A (zh) * 2009-09-17 2011-04-20 杭州依维柯汽车变速器有限公司 双离合器自动变速器电动换档执行装置
CN202301905U (zh) * 2011-10-26 2012-07-04 浙江吉利汽车研究院有限公司 一种汽车换挡拨叉的联动结构
CN106958654A (zh) * 2017-05-02 2017-07-18 苏州江南嘉捷机电技术研究院有限公司 电动车变速箱换挡操纵组件
CN211117538U (zh) * 2019-11-25 2020-07-28 蜂巢传动科技河北有限公司 用于车辆的换挡驻车系统以及具有其的车辆

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