Clutch operation reaction force generating device

Abstract

To provide a clutch operation reaction force generation device capable of eliminating backlashes of a cam follower and a cam surface by using a biasing force of a bias member which generates an operation reaction force in a clutch pedal and suppressing generation of an abnormal sound.SOLUTION: A clutch operation reaction force generation device 5 comprises: a cam body 10; a cam plate 14 having a cam surface 14C and provided in the cam body 10 so as to be movable when a clutch pedal is operated; a cam follower 21 having a roller 21B brought into contact with the cam surface 14C; and a coil spring 17 installed between the cam follower 21 and the cam body 10 and elongated / contracted in response to the movement of the cam plate 14 to generate an operation reaction force in the clutch pedal and generate a load for pressing the cam follower 21 on the cam surface 14C.SELECTED DRAWING: Figure 5

Description

Technical Field

[0001] The present invention relates to a clutch operation reaction force generating device.

Background Art

[0002] Conventionally, vehicles that engage and disengage a clutch using an actuator, such as an MT (Manual Transmission) employing a clutch by wire system, are known.

[0003] When engaging and disengaging a clutch using an actuator, when a driver operates the clutch pedal, the driver cannot feel the operating reaction force corresponding to the operation amount of the clutch pedal. Therefore, it is necessary to generate an operating reaction force corresponding to the operation amount of the clutch pedal.

[0004] Conventionally, an electronic vehicle clutch pedal that pseudo-generates a pedal reaction force (operating reaction force) corresponding to the operation amount of the clutch pedal is known (see Patent Document 1).

[0005] This electronic vehicle clutch pedal includes a housing, and a distal drum that is coupled to the housing and rotatable with respect to the housing, and a pedal arm that defines a contact surface including a plurality of surface portions with different gradients.

[0006] Further, the electronic vehicle clutch pedal includes a force lever that is pivotable around the housing and has a first end that abuts against the contact surface on the distal drum of the pedal arm, and a compressible member that has a first end that abuts against the pedal arm and a second end that abuts against the second end of the force lever. The rotation of the pedal arm is configured to cause the pivoting of the force lever and the action of large and small forces on the pedal arm by the compressible member.

Prior Art Documents

Patent Documents

[0007]

Patent Document 1

SUMMARY OF THE INVENTION

PROBLEMS TO BE SOLVED BY THE INVENTION

[0008] In such a conventional electronic vehicle clutch pedal, when the clutch pedal is in the released state (the state where the clutch device is fully engaged), the compressible member is in a state where it is fully extended and not compressed. As a result, the biasing force of the compressible member does not act on each component such as the clutch pedal and the force lever.

[0009] Therefore, if attention is not paid to component accuracy, play may occur between components, and abnormal noise may be generated due to contact between components caused by vibrations during vehicle running or engine vibrations. Since the compressible member is not compressed at all when the clutch pedal is released, abnormal noise may occur in most of the vehicle running range, which is likely to give discomfort to passengers.

[0010] The present invention has been made paying attention to the above circumstances, and an object of the present invention is to provide a clutch operation reaction force generating device that can eliminate play between a cam follower and a cam surface by utilizing the biasing force of a biasing member that generates an operation reaction force on the clutch pedal and can suppress the generation of abnormal noise.

MEANS FOR SOLVING THE PROBLEMS

[0011] The present invention is a clutch operation reaction force generating device that generates an operation reaction force corresponding to the operation amount of a clutch pedal by a driver, comprising a cam body, a cam plate having a cam surface and movably provided on the cam body so as to be interlocked with the operation of the clutch pedal, a cam follower having a contact portion that contacts the cam surface, and a biasing member installed between the cam follower and the cam body 、which is provided at the end of the cam body on the side opposite to the clutch pedal side, and is a cylindrical support portion that accommodates the end side of the cam plate on the side opposite to the cam follower and the clutch pedal and is characterized in that a load direction conversion portion is provided in the cylindrical support portion, the biasing member expands and contracts according to the movement of the cam plate to generate an operation reaction force on the clutch pedal and generate a load that presses the cam follower against the cam surface. when the direction of the load received by the cam follower from the biasing member is defined as the first direction, and the direction of the load pressing the cam follower against the cam surface is defined as the second direction, the load direction conversion portion converts the load in the first direction applied to the cam follower into a load in the second direction different from the first direction ​

Advantages of the Invention

[0012] According to the present invention as described above, it is possible to eliminate the play between the cam follower and the cam surface by utilizing the biasing force of the biasing member that generates an operating reaction force on the clutch pedal, and the generation of abnormal noise can be suppressed.

Brief Description of the Drawings

[0013]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Modes for Carrying Out the Invention

[0014] The clutch operation reaction force generating device according to an embodiment of the present invention is a clutch operation reaction force generating device that generates an operation reaction force corresponding to the operation amount of a clutch pedal by a driver, and includes a cam body, a cam plate having a cam surface and movably provided on the cam body so as to be interlocked with the operation of the clutch pedal, a cam follower having a contact portion that contacts the cam surface, and a biasing member provided between the cam follower and the cam body. The biasing member expands and contracts according to the movement of the cam plate to generate an operation reaction force on the clutch pedal and generate a load that presses the cam follower against the cam surface.

[0015] Thereby, the clutch operation reaction force generating device according to an embodiment of the present invention can eliminate the play between the cam follower and the cam surface by utilizing the biasing force of the biasing member that generates the operation reaction force on the clutch pedal, and can suppress the generation of abnormal noise.

Example

[0016] Hereinafter, the clutch operation reaction force generating device according to an embodiment of the present invention will be described with reference to the drawings. FIGS. 1 to 10 are views showing the clutch operation reaction force generating device according to an embodiment of the present invention.

[0017] In FIGS. 1 to 9, the up-down, front-back, left-right directions used for the description are based on the state where the clutch operation reaction force generating device according to an embodiment is installed in a vehicle. The front-back direction of the vehicle is the front-back direction, the left-right direction (vehicle width direction) of the vehicle is the left-right direction, and the up-down direction (vehicle height direction) of the vehicle is the up-down direction. However, the mounting state of the clutch operation reaction force generating device on the vehicle is not limited to this.

[0018] Each of the up-down, front-back, left-right directions used for the description can be readjusted according to the mounting state. Note that, based on the biasing member described later in part of the description, one end side of the biasing member that receives the movement from the clutch pedal is referred to as the "clutch pedal side", and the other end side of the biasing member that presses the cam follower described later is referred to as the "cam follower side" for the description. In this embodiment, they indicate the same directions as the rear side and the front side, respectively.

[0019] First, the configuration will be described. In FIG. 1, a vehicle 1 is provided with a dash panel 2. An engine room 2A for installing an engine, a transmission, etc. (not shown) is provided on the front side of the dash panel 2, and a passenger compartment 2B for passengers including the driver is provided on the rear side of the dash panel 2.

[0020] A pedal bracket 3 is attached to the dash panel 2, and a clutch pedal 4 is connected to the pedal bracket 3 via a swing shaft 3a. The clutch pedal 4 swings back and forth about the swing shaft 3a as the center by the operation of the driver.

[0021] Specifically, the clutch pedal 4 has a lever portion 4A whose upper part is connected to the pedal bracket 3 via the swing shaft 3a and extends in the vertical direction, and a pedal portion 4B provided at the lower part of the lever portion 4A and stepped on by the driver.

[0022] The transmission of this embodiment is composed of an MT (Manual Transmission), and the transmission disconnects and connects a clutch device (not shown) using an actuator.

[0023] The actuator disconnects and connects the clutch device according to the depression amount of the clutch pedal 4 operated by the driver. Therefore, the clutch pedal 4 and the clutch device are not mechanically connected. When the clutch device is mechanically disconnected, the power from the engine to the transmission is cut off, and when the clutch device is mechanically connected, the power is transmitted from the engine to the transmission.

[0024] The vehicle 1 is provided with a clutch operation reaction force generating device 5, and the clutch operation reaction force generating device 5 is provided separately from the clutch pedal 4. When the driver operates the clutch pedal 4, the clutch operation reaction force generating device 5 pseudo-generates an operation reaction force (operation load) corresponding to the operation amount of the clutch pedal 4 as if operating a clutch that is mechanically connected.

[0025] As shown in FIGS. 2 to 4, the clutch operation reaction force generating device 5 has a cam body 10. The cam body 10 is disposed in the vicinity of the dash panel 2. Specifically, a through hole (not shown) is formed in the dash panel 2, and the cam body 10 is disposed in a state of being inserted through this through hole. That is, the front portion of the cam body 10 is disposed in the engine room 2A on the front side of the dash panel 2, and the rear portion is disposed in the passenger compartment 2B on the rear side of the dash panel 2.

[0026] The cam body 10 has a cam body main body 11 and a cylindrical support portion 12. The cam body main body 11 has a panel fixing plate 11A, a front side bottom wall 11B, a front side left side wall 11C, a front side right side wall 11D, a rear side left side wall 11E, and a rear side right side wall 11F.

[0027] The cam body 10 is attached to the dash panel 2 by fixing the panel fixing plate 11A to the dash panel 2. As shown in FIG. 2, a through hole 11a is formed in the panel fixing plate 11A, and a cam plate 14 and a coil spring 17, which will be described later, are inserted through the through hole 11a.

[0028] As shown in FIG. 1, the rear surface 11r of the panel fixing plate 11A is in contact with the front surface 2f of the dash panel 2. As shown in FIG. 8, bolt holes 11b and 11c are formed on the left and right sides of the panel fixing plate 11A, and a pair of bolts (not shown) are inserted through the bolt holes 11b and 11c.

[0029] The panel fixing plate 11A is overlapped on the front surface 2f of the dash panel 2, and is fastened to the dash panel 2 by a pair of bolts in a state where the rear surface 11r is in contact with the front surface 2f.

[0030] As shown in FIGS. 4 and 5, the rear end portion of the front side bottom wall 11B is connected to the panel fixing plate 11A, and the front side bottom wall 11B extends forward from the panel fixing plate 11A.

[0031] As shown in FIGS. 3 and 6, the rear end portion of the front left side wall 11C is connected to the panel fixing plate 11A. The front left side wall 11C extends forward from the panel fixing plate 11A and extends upward from the left end portion of the front bottom wall 11B.

[0032] As shown in FIG. 6, the rear end portion of the front right side wall 11D is connected to the panel fixing plate 11A. The front right side wall 11D extends forward from the panel fixing plate 11A and extends upward from the right end portion of the front bottom wall 11B.

[0033] The front left side wall 11C and the front right side wall 11D face each other in the vehicle width direction (left - right direction) and are formed in a symmetrical shape.

[0034] As shown in FIGS. 3 and 6, the front end portion of the rear left side wall 11E is connected to the panel fixing plate 11A. The rear left side wall 11E extends rearward from the panel fixing plate 11A. Also, the front end portion of the rear left side wall 11E is connected to the rear end portion of the front left side wall 11C, and the rear left side wall 11E and the front left side wall 11C are continuous.

[0035] As shown in FIGS. 4 and 6, the front end portion of the rear right side wall 11F is connected to the panel fixing plate 11A. The rear right side wall 11F extends rearward from the panel fixing plate 11A. Also, the front end portion of the rear right side wall 11F is connected to the rear end portion of the front right side wall 11D, and the rear right side wall 11F and the front right side wall 11D are continuous.

[0036] The rear left side wall 11E and the rear right side wall 11F face each other in the vehicle width direction and are formed in a symmetrical shape.

[0037] As shown in FIGS. 2 and 3, the cylindrical support portion 12 is provided so as to extend forward from the front end portion 11f of the cam body main body 11 and is continuous with the cam body main body 11. The front end portion 11f of the cam body main body 11 in this embodiment constitutes the end portion of the cam body on the side opposite to the clutch pedal side (front side, cam follower side).

[0038] As shown in FIGS. 3, 5, and 8, the cylindrical support portion 12 has a bottom wall 12A, a left side wall 12B, a right side wall 12C, and an inclined wall 12D.

[0039] The bottom wall 12A is connected to the front end portion of the front bottom wall 11B and extends forward from the front bottom wall 11B.

[0040] As shown in FIGS. 2, 3, and 8, the left side wall 12B extends upward from the left end portion of the bottom wall 12A, and the lower portion of the left side wall 12B is connected to the front left side wall 11C.

[0041] As shown in FIGS. 5 and 8, the right side wall 12C extends upward from the right end portion of the bottom wall 12A, and the lower portion of the right side wall 12C is connected to the front right side wall 11D.

[0042] As shown in FIG. 8, the inclined wall 12D connects the upper end portion of the left side wall 12B and the upper end portion of the right side wall 12C. As shown in FIGS. 2 and 3, the inclined wall 12D linearly inclines upward from the front end portion 12a toward the rear end portion 12b such that the rear end portion 12b is located obliquely upward rearward with respect to the front end portion 12a. That is, in relation to the bottom wall 12A, the inclined wall 12D inclines so that the distance between the rear end portion 12b and the bottom wall 12A is greater than the distance between the front end portion 12a and the bottom wall 12A.

[0043] As shown in FIGS. 5 and 6, a cam plate 14 is disposed within the cam body 10, and the cam plate 14 is movable back and forth with respect to the cam body 10.

[0044] As shown in FIG. 5, the cam plate 14 has a cam plate portion 14A and a spring receiving portion 14B.

[0045] The cam plate portion 14A extends in the front-rear direction, and the spring receiving portion 14B rises upward from the rear end portion of the cam plate portion 14A.

[0046] An engaging groove 14a is formed at the rear end portion 14c of the cam plate 14, that is, at the rear end portion 14c of the spring receiving portion 14B, and the front end portion of the rod member 15 is fitted into the engaging groove 14a.

[0047] A cylindrical cam plate connecting portion 15A having a central axis in a direction (vehicle width direction) perpendicular to the extending direction of the rod member 15 is provided at the front end portion of the rod member 15 (see FIG. 4), and the cam plate connecting portion 15A is fitted into the engaging groove 14a.

[0048] Specifically, the intersection portion of the axial center of the rod member 15 and the central axis of the cam plate connecting portion 15A is connected so as to be located inside the engaging groove 14a. Thereby, the rod member 15 is connected to the rear end portion 14c of the cam plate 14.

[0049] The engaging groove 14a has an inner peripheral surface formed of a curved surface along the outer peripheral surface of the cam plate connecting portion 15A, and is formed so as to surround the cylindrical cam plate connecting portion 15A in a range of 180 degrees or more with respect to its central axis, and the cam plate connecting portion 15A cannot be detached except in the direction of the central axis.

[0050] Note that the engaging groove 14a allows the rod member 15 to swing about the central axis of the cam plate connecting portion 15A, and the rod member 15 is slidable in the vertical direction along the engaging groove 14a. The rear end portion 14c of the cam plate 14 in the present embodiment constitutes the end portion of the cam plate on the clutch pedal side.

[0051] As shown in FIGS. 2 and 3, a ball-shaped pedal connecting portion 15B is provided at the rear end portion of the rod member 15.

[0052] As shown in FIGS. 1 and 6, a rod support member 7 is attached to the pedal connecting portion 15B, and the pedal connecting portion 15B is swingably connected to the rod support member 7. The rod support member 7 is attached to the clutch pedal 4. That is, the rear end portion of the rod member 15 is connected to the clutch pedal 4 via the rod support member 7.

[0053] Thus, when the clutch pedal 4 swings back and forth with respect to the pedal bracket 3 about the swing axis 3a, the movement is transmitted to the cam plate 14 via the rod member 15, causing the cam plate 14 to move back and forth.

[0054] Specifically, when the clutch pedal 4 is depressed, the clutch pedal 4 rotates (in the clockwise direction in FIG. 1) about the swing axis 3a, and the rod support member 7 moves forward. At this time, the cam plate 14 is pushed by the rod member 15 and moves forward with respect to the cam body 10.

[0055] On the other hand, when returning from the state where the clutch pedal 4 is depressed to the state where the depression is released, the cam plate 14 moves backward with respect to the cam body 10 by the biasing force of a coil spring 17 (biasing member) described later.

[0056] At this time, the clutch pedal 4 is pushed by the rod member 15 and rotates about the swing axis 3a (in the counterclockwise direction in FIG. 1).

[0057] The rod support member 7 is attached to the upper part of the lever portion 4A, and the distance from the rod support member 7 to the swing axis 3a is shorter than the distance from the pedal portion 4B to the swing axis 3a. Therefore, regarding the swing of the clutch pedal 4, the vertical movement distance of the rod support member 7 can be kept small, and the swing movement of the clutch pedal 4 can be easily converted into a linear movement of the cam plate 14 via the rod member 15.

[0058] As shown in FIG. 1, a spring member 6 is provided on the pedal bracket 3. An engaging portion 4C that engages with the spring member 6 is provided on the upper part of the lever portion 4A, and the clutch pedal 4 is biased in the return direction by the spring member 6.

[0059] Note that the pedal bracket 3 is provided with a stopper for restricting the swing range of the clutch pedal 4. Specifically, there is a return side stopper (not shown) that restricts the movement of the clutch pedal 4 in the return direction beyond the return position of the clutch pedal 4 and adjusts the position of the pedal part 4B in the state where it is not depressed, and a depression side stopper (not shown) that restricts the movement of the clutch pedal 4 in the depression direction.

[0060] As shown in FIG. 5, a long hole 14d extending in the front-rear direction is formed in the cam plate portion 14A, and pins 16A and 16B are inserted into the long hole 14d. The left end portions and the right end portions of the pins 16A and 16B are respectively connected to the rear left side wall 11E and the rear right side wall 11F, and the cam plate 14 is movably attached to the cam body main body 11 in the front-rear direction. In addition, due to the relationship between the long hole 14d and the pins 16A and 16B, movement in directions other than the front-rear direction is restricted.

[0061] The vertical width of the long hole 14d is formed slightly larger than the diameters of the pins 16A and 16B. Thereby, when the cam plate 14 moves in the front-rear direction, the vertical movement of the cam plate 14 is restricted and it can move in the direction of the long hole 14d without wobbling. That is, it moves smoothly and stably in a straight line in the front-rear direction with respect to the cam body 10.

[0062] When the cam plate 14 moves forward and the pin 16B abuts against the rear end portion of the long hole 14d, the excessive forward movement of the cam plate 14 is restricted, and when the cam plate 14 moves backward and the pin 16A abuts against the front end portion of the long hole 14d, the excessive backward movement of the cam plate 14 is restricted.

[0063] As shown in FIG. 5, the cylindrical support portion 12 houses the cam follower 21 and the front end portion 14f side of the cam plate portion 14A, that is, the front end portion 14f side (cam follower side) of the cam plate 14.

[0064] The cam follower 21 includes a cam follower body 21A, a roller shaft 21a fixed to the cam follower body 21A, a roller 21B, and a ball bearing 21C disposed between the roller 21B and the roller shaft 21a for rotatably supporting the roller 21B on the roller shaft 21a. In this embodiment, the roller 21B constitutes a contact portion, and the roller shaft 21a constitutes a support shaft. The ball bearing 21C constitutes a bearing.

[0065] Specifically, as shown in FIGS. 8 and 9, the cam follower body 21A has a groove formed from the lower surface upward, and this groove forms a vertically inverted U-shape with a downwardly open cross-section when viewed from the front-rear direction. The roller 21B and the ball bearing 21C are disposed in the groove of the cam follower body 21A with their rotation axes oriented in the left-right direction, and the roller shaft 21a penetrates the roller 21B and the ball bearing 21C, and both ends thereof are fixed to the left and right walls of the groove.

[0066] On the upper surface of the cam plate 14 facing the cam follower 21, a cam surface 14C is formed. The roller 21B is in contact with the cam surface 14C, and the roller 21B is pressed against the cam surface 14C by the biasing force of the biasing member.

[0067] The cam surface 14C is formed in an uneven shape in the range from the front end portion 14f to the rear end portion 14r of the cam surface 14C along the moving direction A of the cam plate 14. Here, the moving direction A of the cam plate 14 is the front-rear direction, and the cam surface 14C is formed from the front end portion 14f of the cam plate 14 to a position immediately before the long hole 14d.

[0068] The cam surface 14C has a convex cam surface 14e that gradually protrudes in a direction orthogonal to the moving direction A of the cam plate 14 from the front end portion 14f toward the rear end portion 14r in the moving direction A. That is, the cam surface 14C is formed with a convex cam surface 14e whose height of protruding toward the cam follower 21 increases from the front end portion 14f to the rear end portion 14r.

[0069] The cam surface 14C has a concave cam surface 14g that gradually depresses in a direction orthogonal to the moving direction A of the cam plate 14, from the apex 14t of the convex cam surface 14e toward the rear end portion 14r of the cam plate 14. That is, the cam surface 14C is formed with a concave cam surface 14g whose height protruding toward the cam follower 21 decreases from the apex 14t toward the rear end portion 14r. The cam surface 14C has a convex cam surface 14h that gradually protrudes in a direction orthogonal to the moving direction A of the cam plate 14, from the deepest part 14p of the concave cam surface 14g toward the rear end portion 14r of the cam plate 14.

[0070] That is, the cam surface 14C is formed with a convex cam surface 14h whose height protruding toward the cam follower 21 increases from the deepest part 14p toward the rear end portion 14r. That is, the convex cam surfaces 14e and 14h are formed apart from each other in the front-rear direction.

[0071] When in the initial position where the clutch pedal 4 is not depressed (the full connection position of the clutch device), the roller 21B that abuts against the cam surface 14C is located at a position lower than the apex 14t of the convex cam surface 14e and at a height position approximately equal to the deepest part 14p of the concave cam surface 14g.

[0072] The apex 14t is the highest part of the convex cam surface 14e, and the deepest part 14p is the deepest part of the concave cam surface 14g. That is, the apex 14t and the deepest part 14p are the highest part and the lowest part of the cam surface 14C.

[0073] When the cam plate 14 moves in the front-rear direction by the operation of the clutch pedal 4, the contact position between the roller 21B and the cam surface 14C changes, and the position of the cam follower 21 is changed.

[0074] A coil spring 17 is provided between the cam follower 21 and the cam plate 14 such that its axis 17a extends along the direction in which the cam plate 14 extends. The front end portion of the coil spring 17 abuts against the spring receiving surface 21b of the cam follower body 21A so as to apply its elastic force (biasing force), and the rear end portion of the coil spring 17 abuts against the spring receiving portion 14B of the cam plate 14 so as to apply its elastic force (biasing force).

[0075] Specifically, a spring receiving surface 14s is provided on the front surface of the spring receiving portion 14B, and the rear end portion of the coil spring 17 abuts against the spring receiving surface 14s.

[0076] A protrusion 14u is provided on the spring receiving surface 14s. The protrusion 14u protrudes from the spring receiving surface 14s toward the cam follower 21 side, and the protrusion 14u is inserted inside the inner diameter of the coil spring 17.

[0077] A spring receiving surface 21b is provided on the rear surface of the cam follower body 21A, and the front end portion of the coil spring 17 abuts against the spring receiving surface 21b.

[0078] A cylindrical fitting protrusion 21c is provided on the spring receiving surface 21b. The fitting protrusion 21c protrudes from the spring receiving surface 21b toward the spring receiving portion 14B side, and the inner circumference of the coil spring 17 is fitted to the outer circumference of the fitting protrusion 21c.

[0079] That is, the front end portion of the coil spring 17 is fitted to the fitting protrusion 21c while abutting against the spring receiving surface 21b, and the rear end portion of the coil spring 17 has the protrusion 14u inserted inside its inner diameter while abutting against the spring receiving surface 14s.

[0080] Thus, when the cam plate 14 moves, the coil spring 17 does not come off from the cam follower 21 and the spring receiving portion 14B, and expands and contracts following the movements of the cam follower 21 and the spring receiving portion 14B. The expansion and contraction direction of the coil spring 17 is the front-rear direction, which is the same as the movement direction A of the cam plate 14.

[0081] The coil spring 17 applies a biasing force in the direction in which the cam follower 21 and the cam plate 14 separate from each other in the movement direction A of the cam plate 14 to the cam follower 21 and the cam plate 14. The coil spring 17 in this embodiment constitutes a biasing member.

[0082] The clutch operation reaction force generating device 5 causes the cam plate 14 to move in the front-rear direction by stepping on or returning the clutch pedal 4, thereby expanding and contracting the coil spring 17, and applies the elastic force from the coil spring 17 as an operation reaction force to the clutch pedal 4.

[0083] Furthermore, the clutch operation reaction force generating device 5 adjusts the operation reaction force applied to the clutch pedal 4 by changing the compression amount of the coil spring 17 according to the moving position of the cam follower 21 accompanying the front-rear movement of the cam plate 14, generates a reaction force as if operating a mechanically connected clutch, and applies a pseudo operation reaction force to the clutch pedal 4.

[0084] The coil spring 17 expands and contracts in response to the front-rear movement of the cam plate 14, thereby generating an operation reaction force on the clutch pedal 4 and generating a pressing load that presses the cam follower 21 against the inclined wall 12D and the cam surface 14C.

[0085] The position of the cam follower 21 is changed according to the shape of the cam surface 14C as the cam plate 14 moves. The cam follower 21 moves along the inclined wall 12D (specifically, the first sliding surface 18b), thereby changing the operation reaction force on the clutch pedal 4 and allowing the cam plate 14 to move in the front-rear direction.

[0086] As shown in FIG. 5, the inclined wall 12D of the cylindrical support portion 12 faces the resultant force direction F3 of the load F1 received by the cam follower 21 from the coil spring 17 and the load F2 received by the cam follower 21 from the cam surface 14C, and is inclined in the direction D orthogonal to the resultant force direction F3.

[0087] The inclined wall 12D of the present embodiment is inclined at an angle of approximately 45° with respect to the moving direction A of the cam plate 14. However, the inclination angle of the inclined wall 12D with respect to the moving direction A of the cam plate 14 is not limited to this angle.

[0088] In the clutch operation reaction force generating device 5 of the present embodiment, when the direction of the load F1 received by the cam follower 21 from the coil spring 17 is defined as the first direction A1, and the direction of the load F4 (the direction opposite to the load F2) pressing the cam follower 21 against the cam surface 14C is defined as the second direction A2, the inclined wall 12D converts the load F1 in the first direction A1 applied to the cam follower 21 into the load F4 in the second direction A2.

[0089] Specifically, when the cam plate 14 moves forward, the coil spring 17 is compressed between the cam follower 21 and the spring receiving portion 14B of the cam plate 14, and the cam follower 21 receives the load F1 in the first direction A1 by the coil spring 17.

[0090] When the cam plate 14 moves forward, the contact position between the roller 21B and the cam surface 14C is changed, and as the height of the contacting cam surface 14C changes, the cam follower 21 moves along the inclined wall 12D while being pressed against the inclined wall 12D.

[0091] At this time, since the cam follower 21 receives a reaction force from the inclined wall 12D, a load F4 in the second direction A2 is applied to the cam surface 14C. In this way, the inclined wall 12D converts the load in the first direction A1 applied to the cam follower 21 into the load in the second direction A2. The inclined wall 12D of the present embodiment constitutes a load direction conversion portion.

[0092] The inclined wall 12D is installed in the normal direction H of the contact portion between the cam surface 14C and the roller 21B. Specifically, in the range from the front end portion 14f of the cam surface 14C to the apex 14t of the cam surface 14C, the inclined wall 12D is installed in the normal direction H of the contact portion between the cam surface 14C and the roller 21B. In FIG. 7, one of the normal directions H is shown.

[0093] As shown in FIGS. 5 and 7, the cam surface 14C is formed along the plate thickness direction (left - right direction) of the cam plate 14 from the front end portion 14f of the cam plate 14 as a starting point to the rear end portion 14r that is slightly in front of the front end portion of the long hole 14d from the front end portion 14f.

[0094] The height of the cam surface 14C increases from the front end portion 14f toward the rear, and the apex 14t is formed to be the highest. And between the front end portion 14f and the apex 14t, the inclined wall 12D is installed in the normal direction H of the contact portion between the cam surface 14C and the roller 21B.

[0095] The front end portion 14f of the cam surface 14C of this embodiment constitutes the end portion of the cam surface on the cam follower side, and the apex 14t of the cam surface 14C constitutes a predetermined part of the cam surface on the clutch pedal side.

[0096] As shown in FIG. 5, a part of the coil spring 17 and the inclined wall 12D are installed side by side in the direction of the axis 17a of the coil spring 17.

[0097] In other words, when the clutch operation reaction force generating device 5 is viewed from the direction of the axis 17a of the coil spring 17, the coil spring 17 is installed so as to overlap with the inclined wall 12D. Note that the direction of the axis 17a of the coil spring 17 is also referred to as the axial direction of the coil spring 17.

[0098] The coil spring 17 and the roller shaft 21a are installed side by side in the axial direction of the coil spring 17. In other words, when the clutch operation reaction force generating device 5 is viewed from the axial direction of the coil spring 17, the coil spring 17 is installed so as to overlap with the roller shaft 21a.

[0099] The roller shaft 21a is disposed at a position between the front end portion 12a and the rear end portion 12b of the inclined wall 12D at the position in the moving direction A of the cam plate 14.

[0100] The inclined wall 12D of the present embodiment constitutes a guide wall portion and a first guide wall portion, and the bottom wall 12A constitutes a second guide wall portion. The front end portion 12a of the inclined wall 12D constitutes the other end portion in the inclined direction of the guide wall portion, and the rear end portion 12b of the inclined wall 12D constitutes one end portion in the inclined direction of the guide wall portion.

[0101] The front end portion 12a of the inclined wall 12D is located below (inside) the upper end portion 17b of the coil spring 17, and the rear end portion 12b of the inclined wall 12D is located above (outside) the upper end portion 17b of the coil spring 17.

[0102] That is, the lower portion of the inclined wall 12D faces the coil spring 17 in the axial direction of the coil spring 17, and the upper portion of the inclined wall 12D is located above the coil spring 17 in the axial direction of the coil spring 17. The upper end portion 17b of the coil spring 17 of the present embodiment constitutes the outer peripheral end portion of the coil spring.

[0103] The cam body 10 is provided with a resin-made first friction member 18 and a second friction member 19. As shown in FIGS. 5 and 7, the first friction member 18 is installed between the inclined wall 12D of the cylindrical support portion 12 and the cam follower 21, and reduces the sliding resistance when the cam follower 21 moves.

[0104] The first friction member 18 extends along the inclined wall 12D and is inclined in the same direction as the inclined wall 12D with respect to the moving direction A of the cam plate 14.

[0105] Fitting protrusions 18a are formed on the surface of the first friction member 18 facing the inclined wall 12D. As shown in FIGS. 5 and 8, fitting holes 12d are formed in the inclined wall 12D, and the fitting protrusions 18a are fitted into the fitting holes 12d.

[0106] As a result, the first friction member 18 is attached to the inclined wall 12D so as not to be movable in the inclined direction of the inclined wall 12D. As shown in FIGS. 5 and 7, the first friction member 18 has a first sliding surface 18b that contacts the cam follower 21, and the cam follower 21 moves along the first sliding surface 18b.

[0107] Note that a plurality of fitting protrusions 18a and fitting holes 12d are formed side by side in the inclined direction of the inclined wall 12D, and the first friction member 18 is positioned and attached to the inclined wall 12D by these fittings.

[0108] As shown in FIGS. 5 and 7, the second friction member 19 is provided between the front bottom wall 11B of the cam body main body 11 and the cam plate portion 14A, and reduces the sliding resistance when the cam plate 14 moves. Further, the second friction member 19 extends to the cam body main body 11 and enters between the front bottom wall 11B and the cam plate portion 14A.

[0109] As shown in FIGS. 8 and 9, the second friction member 19 has a bottom wall 19A, a left side wall 19B, and a right side wall 19C. The bottom wall 19A extends in the front-rear direction along the cam plate portion 14A, and the bottom wall 19A is in frictional contact with the lower surface of the cam plate portion 14A.

[0110] The left side wall 19B and the right side wall 19C extend upward from the left end portion and the right end portion of the bottom wall 19A, and the left side wall 19B and the right side wall 19C are in frictional contact with the left and right surfaces of the lower portion of the cam plate portion 14A. That is, the second friction member 19 has a groove (second sliding surface 19b) formed along the moving direction A of the cam plate 14 into which the cam plate 14 enters on its upper surface, and is installed between the cam plate portion 14A and the front bottom wall 11B of the cam body main body 11 and the bottom wall 12A of the cylindrical support portion 12 so as to sandwich the lower portion of the cam plate portion 14A.

[0111] Further, as shown in FIG. 8, the left side wall 19B of the second friction member 19 is disposed between the cam plate portion 14A, the front left side wall 11C of the cam body main body 11, and the left side wall 12B of the cylindrical support portion 12. The right side wall 19C of the second friction member 19 is disposed between the cam plate portion 14A, the front right side wall 11D of the cam body main body 11, and the right side wall 12C of the cylindrical support portion 12.

[0112] As shown in FIGS. 5 and 9, a fitting projection 19a is formed on the bottom wall 19A of the second friction member 19 facing the bottom wall 12A and the front bottom wall 11B. Fitting grooves 11d and 12e are formed in the front bottom wall 11B and the bottom wall 12A, and the fitting projection 19a is fitted into the fitting grooves 11d and 12e. The fitting grooves 11d and 12e are holes that are long in the left-right direction. Regarding the gap (play) between the fitting projection 19a and the fitting grooves 11d and 12e, the gap in the moving direction A of the cam plate 14 is small, and the gap in the left-right direction is set to be relatively large.

[0113] As a result, the second friction member 19 is unable to move in the moving direction A of the cam plate 14 due to the relationship between the fitting projection 19a and the fitting grooves 11d and 12e. Further, the second friction member 19 is positioned in contact with the left side wall 12B or the right side wall 12C in the left-right direction.

[0114] As shown in FIGS. 5 and 8, the inner peripheral surfaces of the bottom wall 19A, the left side wall 19B, and the right side wall 19C of the second friction member 19 constitute a groove-shaped second sliding surface 19b that contacts the cam plate 14. When the cam plate 14 moves in the front-rear direction, the second sliding surface 19b frictionally contacts the cam plate 14 to guide the movement of the cam plate 14 and receive the load acting from the cam follower 21 on the cam surface 14C.

[0115] The cam follower 21 is urged by the coil spring 17 and is pressed against the first friction member 18, and this pressing force is received by the inclined wall 12D of the cylindrical support portion 12 via the first friction member 18.

[0116] Further, the cam follower 21 is urged by the coil spring 17 and pressed against the cam plate 14, and this pressing force is received by the bottom wall 12A of the cylindrical support portion 12 via the cam plate 14 and the second friction member 19.

[0117] The positional relationship between the first sliding surface 18b (the inclined wall 12D or the first friction member 18) and the second sliding surface 19b (the bottom wall 12A or the second friction member 19) is formed such that the interval becomes narrower as it goes forward.

[0118] Thereby, a cam follower 21 urged forward is disposed between the first sliding surface 18b (the inclined wall 12D or the first friction member 18) and the second sliding surface 19b (the bottom wall 12A or the second friction member 19), and a wedge-shaped space that gradually becomes narrower as it goes forward is formed.

[0119] The coil spring 17 presses the cam follower 21 in a direction in which the interval between the inclined wall 12D and the bottom wall 12A, or the interval between the first friction member 18 and the second friction member 19 becomes narrower, and pushes the cam follower 21 into the cylindrical support portion 12.

[0120] Thereby, the cam follower 21 is stably pressed against the first friction member 18, and at the same time, the cam follower 21 is stably pressed against the cam plate 14.

[0121] The inclined wall 12D and the first friction member 18 of the present embodiment constitute a first wall portion, and the bottom wall 12A and the second friction member 19 constitute a second wall portion. That is, the first wall portion is composed of the first guide wall portion and the first friction member 18, and the second wall portion is composed of the second guide wall portion and the second friction member 19.

[0122] The first friction member 18 of this embodiment constitutes the first guide member, and the second friction member 19 constitutes the second guide member. The fitting hole 12d constitutes the first fitted portion, and the fitting grooves 12e and 11d constitute the second fitted portion. The fitting protrusion 18a constitutes the first fitting portion, and the fitting protrusion 19a constitutes the second fitting portion.

[0123] As shown in FIG. 2, hook portions 11g and 11h are provided at the end of the cam body main body 11 on the clutch pedal 4 side, that is, at the rear end portions of the rear left side wall 11E and the rear right side wall 11F of the cam body main body 11.

[0124] The hook portions 11g and 11h extend upward from the rear end portions of the rear left side wall 11E and the rear right side wall 11F, and then bend toward the cam follower 21 side.

[0125] Engagement grooves 11i and 11j are provided in the hook portions 11g and 11h, and the left and right end portions of the cam plate connecting portion 15A of the rod member 15 are detachably engaged with the engagement grooves 11i and 11j.

[0126] As shown in FIGS. 4 and 6, the hook portions 11g and 11h are arranged on the left and right sides of the rod member 15. When viewed in the vertical direction, the rod member 15 and the cam plate 14 are arranged in a straight line, and the cam plate 14 is installed between the rear left side wall 11E including the hook portion 11g and the front left side wall 11C and the rear right side wall 11F including the hook portion 11h and the front right side wall 11D in the vehicle width direction.

[0127] And the spring receiving portion 14B provided at the rear end portion of the cam plate 14 is provided between the hook portions 11g and 11h in the vehicle width direction.

[0128] In a state where the cam plate connecting portion 15A is engaged with the engagement grooves 11i and 11j, the coil spring 17 is installed in a compressed state between the cam follower 21 and the spring receiving portion 14B of the cam plate 14, and while pushing the cam follower 21 into the internal space of the cylindrical support portion 12, the cam plate connecting portion 15A is pressed against the engagement grooves 11i and 11j. At this time, the coil spring 17 is in a state of being maximally extended while being incorporated into the clutch operation reaction force generating device 5 according to an embodiment of the present invention.

[0129] When the cam plate connecting portion 15A is engaged with the engagement grooves 11i and 11j, the clutch device is in a completely connected state, and the clutch pedal 4 is released without being depressed. Even in the completely connected state of this clutch device, the coil spring 17 is compressed, and the coil spring 17 has sufficient biasing force to push the cam follower 21 into the cylindrical support portion 12.

[0130] In a state where the cam plate connecting portion 15A is pressed against the engagement grooves 11i and 11j by the coil spring 17, as shown in FIG. 3, when viewed from the left - right direction, the spring receiving portion 14B overlaps with the hook portions 11g and 11h in the front - rear direction.

[0131] When the cam plate connecting portion 15A attached to the spring receiving portion 14B is locked to the engagement grooves 11i and 11j, the movement of the spring receiving portion 14B backward from the hook portions 11g and 11h is restricted, and the movement of the cam plate 14 toward the clutch pedal 4 side is restricted. The hook portions 11g and 11h of the present embodiment constitute stopper portions.

[0132] Also, in a state where the cam plate connecting portion 15A is pressed against the engagement grooves 11i and 11j by the coil spring 17 and engaged with the engagement grooves 11i and 11j, it is possible to prevent the cam plate 14 from coming off the cam body main body 11. Also, it is possible to prevent the coil spring 17 from falling off.

[0133] In addition, since the movement of the cam plate 14 toward the clutch pedal 4 side is restricted, when the clutch pedal 4 is not depressed, the clutch pedal 4 is pressed by the biasing force of the coil spring 17, and it is possible to prevent the clutch pedal 4 from being excessively swung toward the passenger compartment 2B side (the occupant side) about the swing shaft 3a. Therefore, it is possible to prevent giving a sense of discomfort to the driver.

[0134] On the other hand, when the clutch pedal 4 is depressed and the cam plate 14 moves forward, the cam plate connecting portion 15A is disengaged from the engaging grooves 11i and 11j. The coil spring 17 is gradually compressed as the cam plate 14 moves forward. Thereby, the biasing force (spring force) of the coil spring 17 increases.

[0135] As shown in FIGS. 3 and 4, ribs 15C and 15D are provided on the left and right sides of the rod member 15. The ribs 15C and 15D project in the left - right direction in the same manner as the cam plate connecting portion 15A. That is, the ribs 15C and 15D project from the rod member 15 toward the hook portions 11g and 11h and extend in the front - rear direction along the rod member 15.

[0136] A clearance s in the vehicle width direction is formed between the ribs 15C and 15D and the hook portions 11g and 11h, and the clearance s is formed smaller than the protruding height in the vehicle width direction of each of the ribs 15C and 15D.

[0137] That is, the rod member 15 is connected to the cam plate 14 and the clutch pedal 4 such that a clearance s is formed between the hook portions 11g and 11h and the ribs 15C and 15D. Therefore, normally, the rod member 15 does not contact the hook portions 11g and 11h, but when the position of the rod member 15 is displaced left and right, the ribs 15C and 15D contact the hook portions 11g and 11h to suppress further displacement, and it is possible to prevent the cam plate connecting portion 15A from coming off the spring receiving portion 14B.

[0138] As shown in FIGS. 8 and 9, the first sliding surface 18b of the first friction member 18 facing the cam follower 21 is formed with a curved surface portion protruding in a semi-cylindrical shape, and the first sliding surface 18b is formed along the inclined wall 12D from the front end portion 12a to the rear end portion 12b of the inclined wall 12D. The curved surface portion with a semi-circular cross-section extends along the extending direction (inclined direction) of the first friction member 18 while maintaining the curved surface of its cross-sectional shape.

[0139] That is, the curved surface portion is formed so as to protrude in a semi-circular cross-section from the front end portion (the lower end portion in the inclined direction) to the rear end portion (the upper end portion in the inclined direction) of the first friction member 18, and extends linearly so as to overlap the cam plate 14 or the second sliding surface 19b when viewed from the vertical direction.

[0140] On the upper surface of the cam follower body 21A facing the first sliding surface 18b of the first friction member 18, a groove-shaped sliding surface 21d formed of a curved surface recessed in a semi-cylindrical shape in cross-section is formed. The sliding surface 21d extends linearly in the inclined direction along the first sliding surface 18b, and the curved surface portion protruding linearly from the first sliding surface 18b enters the groove of the sliding surface 21d.

[0141] That is, the first sliding surface 18b of the first friction member 18 and the sliding surface 21d of the cam follower body 21A are in contact with each other by the curved surface portion and the curved surface of the groove, and when the cam follower body 21A slides in the vertical direction along the first friction member 18, they slide in a state where the curved surfaces are in contact with each other.

[0142] That is, the cam follower 21 moves (slides) along the curved surface portion of the first sliding surface 18b. The curved surface has a semi-circular cross-section, and the curved surface is composed of a curved surface portion protruding in a semi-cylindrical shape and a groove recessed in a semi-cylindrical shape, and these semi-cylindrical shape and semi-cylindrical shape have a common central axis. And with this central axis as the rotation center, the cam follower 21 can tilt in the left-right direction with respect to the first friction member 18.

[0143] The vehicle is provided with a sensor (not shown) that detects the operation amount of the clutch pedal 4. The sensor detects the depression amount of the clutch pedal 4 or the movement amount of the cam plate 14 and transmits a detection signal to a controller (not shown).

[0144] Based on the detection information of the sensor, the controller controls the actuator to disengage / engage the clutch device.

[0145] Next, the operation of the clutch operation reaction force generating device 5 of this embodiment will be described. When the driver does not depress the clutch pedal 4, the clutch device is fully engaged. In this state, the cam plate 14 is located at the maximum position on the clutch side. And the roller 21B of the cam follower 21 is in contact with the cam surface 14C on the front end portion 14f side of the cam plate 14 (see FIG. 5).

[0146] When the driver depresses the clutch pedal 4 to disengage the clutch device from this state, the movement is transmitted to the cam plate 14 via the rod member 15. At this time, the cam plate 14 moves forward while in frictional contact with the second friction member 19, the cam plate connecting portion 15A disengages from the engagement grooves 11i, 11j and moves forward, and the coil spring 17 is compressed.

[0147] When the cam plate 14 moves forward, the cam follower 21 is pushed up by the convex cam surface 14e of the cam surface 14C. At this time, since the roller 21B rotates while in contact with the convex cam surface 14e of the cam surface 14C, the cam plate 14 can move forward smoothly.

[0148] Note that the movement direction of the cam follower 21 pushed up by the convex cam surface 14e of the cam surface 14C is restricted by the presence of the inclined wall 12D (the first friction member 18) and moves obliquely upward to the rear side along the first sliding surface 18b (see FIG. 7).

[0149] That is, the cam follower 21 is not only pushed up by the convex cam surface 14e of the cam plate 14 and moves upward, but also moves obliquely upward to the rear side while the cam follower body 21A is in frictional contact with the first friction member 18. Therefore, the cam follower 21 also moves in the moving direction A of the cam plate 14 toward the clutch pedal side (rod member 15 side). For this reason, the coil spring 17 is not only compressed by the movement of the cam plate 14, but also further compressed by the cam follower 21 moving toward the clutch pedal side.

[0150] Due to the elastic force of the coil spring 17 and the inclination of the inclined wall 12D, the cam follower 21 is pressed against the cam surface 14C. The pressing load from the cam follower 21 is received by the second friction member 19 via the cam plate 14. Further, since the roller 21B is rotatably supported on the roller shaft 21a by the ball bearing 21C, the sliding resistance between the roller 21B and the cam surface 14C is reduced. By these, the cam plate 14 can slide smoothly.

[0151] When the cam plate 14 moves further forward and the roller 21B is positioned at the apex 14t of the convex cam surface 14e as shown in FIG. 7, the cam follower 21 moving along the inclined wall 12D is located at the rearmost side (clutch pedal side) in the moving direction A of the cam plate 14 and is closest to the rod member 15.

[0152] As a result, until the roller 21B reaches the apex 14t of the convex cam surface 14e from the cam surface 14C at the front end portion 14f of the cam plate 14, the compression amount of the coil spring 17 further increases by the amount that the cam follower 21 moves toward the rod member 15 side along the inclined wall 12D.

[0153] When the roller 21B moves along the convex cam surface 14e (between the front end portion 14f and the apex 14t), as shown by W1 in FIG. 10, a reaction force of the coil spring 17 that gradually increases according to the depression amount of the clutch pedal 4 is applied to the clutch pedal 4 as an operating reaction force.

[0154] In FIG. 10, the horizontal axis represents the clutch pedal stroke, indicating the amount of depression (depression length) of the clutch pedal by the driver, and the vertical axis represents the operating reaction force, indicating the depression force of the clutch pedal by the driver (the force required to maintain the depression position).

[0155] While the cam plate 14 further moves forward and the roller 21B contacts the deepest part 14p of the concave cam surface 14g while contacting the concave cam surface 14g from the apex 14t of the convex cam surface 14e, the cam follower 21 moves downward.

[0156] When the cam follower 21 moves downward, since the cam follower 21 receives the biasing force of the coil spring 17 and is pressed toward the inclined wall 12D, the cam follower 21 moves obliquely downward forward along the first sliding surface 18b while frictionally sliding on the first friction member 18, and moves away from the rod member 15 in the moving direction A of the cam plate 14. As a result, the compression amount of the coil spring 17 decreases.

[0157] Thus, when the cam follower 21 moves according to the shape between the apex 14t and the deepest part 14p of the cam surface 14C, as shown by W2 in FIG. 10, even if the depression amount of the clutch pedal 4 increases, the reaction force (operating reaction force) applied to the clutch pedal 4 generated from the elastic force of the coil spring 17 becomes smaller.

[0158] Since this load characteristic is similar to the operating feeling (load characteristic accompanying the deformation of the diaphragm spring) that the driver feels when operating a mechanically connected clutch, the driver can operate the clutch pedal of the clutch-by-wire system without discomfort.

[0159] When the cam plate 14 moves further forward, the roller 21B moves upward while contacting the convex cam surface 14h from the deepest part 14p of the concave cam surface 14g. The cam follower 21 moves obliquely upward to the rear side along the first sliding surface 18b while frictionally sliding on the first friction member 18, and moves toward the side approaching the rod member 15 in the moving direction A of the cam plate 14. As a result, the amount of compression of the coil spring 17 can be further increased by the amount that the cam follower 21 moves in the moving direction A of the cam plate 14.

[0160] At this time, as shown by W3 in FIG. 10, a reaction force of the coil spring 17 that gradually increases according to the depression amount of the clutch pedal 4 is applied to the clutch pedal 4.

[0161] As shown in FIG. 10, the depressing force of the clutch pedal 4 by the driver is smaller when releasing the depression of the clutch pedal 4 from the state where the clutch pedal 4 is depressed until the clutch device is in the disconnection control state than when depressing the clutch pedal 4 (when increasing the depression amount).

[0162] When releasing the depression of the clutch pedal 4, the elastic force (spring force) biased by the coil spring 17 exceeds the operating force of the driver input to the cam plate 14 via the rod member 15, so that the cam plate 14 moves to the rear side.

[0163] When the cam plate 14 moves toward the clutch pedal 4 side by the coil spring 17, the roller 21B sequentially contacts the convex cam surface 14e from the concave cam surface 14g, and the cam follower 21 moves in the moving direction A of the cam plate 14 along the inclined wall 12D according to the height of the cam surface 14C including the concave cam surface 14g and the convex cam surface 14e.

[0164] Thereby, the amount of compression of the coil spring 17 is adjusted, and a reaction force corresponding to the amount of compression of the coil spring 17 is applied to the clutch pedal 4 as an operating reaction force.

[0165] As shown in FIG. 10, on the return side of the clutch pedal 4, an operating reaction force smaller than that on the depression side of the clutch pedal 4 is applied to the clutch pedal 4.

[0166] Specifically, when the clutch pedal 4 is depressed, frictional forces that resist the depression direction of the clutch pedal 4 are generated between the first friction member 18 and the cam follower 21 and between the second friction member 19 and the cam plate 14, and the frictional forces increase as the compression amount of the coil spring 17 increases.

[0167] On the other hand, when the depression of the clutch pedal 4 is released and the clutch pedal 4 is returned, frictional forces that resist the return direction opposite to the depression direction of the clutch pedal 4 are generated between the first friction member 18 and the cam follower 21 and between the second friction member 19 and the cam plate 14, and the frictional forces decrease as the compression amount of the coil spring 17 decreases.

[0168] Since the depression force of the clutch pedal 4 by the driver is smaller on the return side than on the depression side, as shown in FIG. 10, a hysteresis load is generated in the operating reaction force of the clutch pedal 4.

[0169] As a result, a large operating reaction force can be obtained by the clutch operating reaction force generating device 5 on the depression side of the clutch pedal 4, and an operating reaction force smaller than that on the depression side can be obtained by the clutch operating reaction force generating device 5 on the return side of the clutch pedal 4.

[0170] In this way, the first friction member 18 and the second friction member 19 of the present embodiment function as hysteresis generating members.

[0171] Further, since the first friction member 18 and the second friction member 19 are made of resin, wear when the cam follower 21 or the cam plate 14 comes into contact with the first friction member 18 and the second friction member 19 can be suppressed, and the durability of the cam follower 21 and the cam plate 14 can be improved.

[0172] Thus, when the clutch pedal 4 is operated, the clutch operation reaction force generating device 5 of this embodiment can change the compression amount of the coil spring 17 according to the movement amounts of the cam plate 14 and the cam follower 21, and apply an operation reaction force corresponding to the compression amount of the coil spring 17 to the clutch pedal 4.

[0173] Further, by changing the shape of the cam surface 14C of the cam plate 14, the movement amount of the cam follower 21 with respect to the movement direction A of the cam plate 14 can be adjusted to set the reaction force of the coil spring 17, and an operation reaction force with a desired pseudo characteristic can be generated.

[0174] As a result, the clutch operation reaction force generating device 5 can pseudo-generate an operation reaction force corresponding to the operation amount of the clutch pedal 4 by the driver, and can give the driver an operation feeling of the clutch pedal 4 without discomfort.

[0175] Also, when the cam plate 14 moves forward, the pin 16B abuts against the rear end portion of the long hole 14d, thereby restricting the cam plate 14 from moving excessively forward.

[0176] Thereby, it is possible to prevent the coil spring 17 from being excessively compressed and prevent the durability of the coil spring 17 from deteriorating. As a result, the durability of the clutch operation reaction force generating device 5 can be improved.

[0177] Next, the effects of the clutch operation reaction force generating device 5 of this embodiment will be described. The clutch operation reaction force generating device 5 of this embodiment includes a cam body 10, a cam plate 14 having a cam surface 14C and movably provided on the cam body 10 so as to be interlocked with the operation of the clutch pedal 4, and a cam follower 21 having a roller 21B that contacts the cam surface 14C.

[0178] In addition, the clutch operation reaction force generating device 5 includes a coil spring 17 installed between the cam follower 21 and the cam body 10. The coil spring 17 expands and contracts according to the movement of the cam plate 14, thereby generating an operation reaction force on the clutch pedal 4 and generating a load for pressing the cam follower 21 against the cam surface 14C.

[0179] Thus, the coil spring 17 that expands and contracts according to the movement of the cam plate 14 to generate an operation reaction force on the clutch pedal 4 can generate a load for pressing the cam follower 21 against the cam surface 14C, and the play between the cam follower 21 and the cam surface 14C can be eliminated.

[0180] Therefore, it is possible to suppress the collision between the cam follower 21 and the cam surface 14C due to vibrations during the running of the vehicle 1 or engine vibrations. Accordingly, it is possible to suppress the generation of abnormal noises from the clutch operation reaction force generating device 5 and suppress giving discomfort to the passengers.

[0181] Further, according to the clutch operation reaction force generating device 5 of the present embodiment, a cylindrical support portion 12 for accommodating the front end portion 11f side of the cam body main body 11 and the front end portion 14f side of the cam plate 14 is provided on the front end portion 11f side of the cam body main body 11.

[0182] An inclined wall 12D is provided on the cylindrical support portion 12. When the direction of the load F1 that the cam follower 21 receives from the coil spring 17 is defined as the first direction A1, and the direction of the load F4 for pressing the cam follower 21 against the cam surface 14C (the direction opposite to the load F2) is defined as the second direction A2, the inclined wall 12D converts the load F1 in the first direction A1 applied to the cam follower 21 into the load F4 in the second direction A2.

[0183] Thereby, by adjusting the inclination angle of the inclined wall 12D with respect to the moving direction of the cam plate 14, the pressing load of the cam follower 21 against the cam surface 14C with respect to the biasing force of the coil spring 17 (the operation reaction force of the clutch pedal 4) can be appropriately adjusted.

[0184] Therefore, it is possible to eliminate the play between the cam follower 21 and the cam surface 14C with an appropriate load corresponding to the operating reaction force of the clutch pedal 4, and it is possible to suppress the collision between the cam follower 21 and the cam surface 14C due to vibrations associated with the running of the vehicle 1 or vibrations of the engine. For this reason, it is possible to effectively suppress the generation of abnormal noises from the clutch operating reaction force generating device 5.

[0185] Note that, although the clutch operating reaction force generating device 5 of the present embodiment converts the direction of the load by the inclined wall 12D, it is not limited thereto.

[0186] For example, when the cam follower 21 receives a load F1 from the coil spring 17, a rotating shaft that rotatably supports the cam follower main body 21A is attached to the left side wall 12B and the right side wall 12C of the cylindrical support portion 12, and the cam follower main body 21A is rotated about the rotating shaft, thereby converting the load F1 in the first direction A1 applied to the cam follower 21 into a load F4 in the second direction A2.

[0187] Further, according to the clutch operating reaction force generating device 5 of the present embodiment, the inclined wall 12D faces the resultant force direction of the load F1 received by the cam follower 21 from the coil spring 17 and the load F2 received from the cam surface 14C, and extends in a direction D orthogonal to the resultant force direction F3.

[0188] Thereby, the load F1 in the first direction A1 applied to the cam follower 21 by the inclined wall 12D can be easily converted into a load F4 in the second direction A2.

[0189] In addition, since the inclined wall 12D extends in the direction D orthogonal to the resultant force direction F3, the cam follower 21 can be brought into surface contact with the first friction member 18 attached to the inclined wall 12D, and the play between the first friction member 18 and the cam follower 21 can be eliminated.

[0190] For this reason, it is possible to suppress the generation of abnormal noises from the clutch operating reaction force generating device 5 due to the collision between the cam follower 21 and the first friction member 18.

[0191] In addition, since the cam follower 21 can be brought into surface contact with the first friction member 18, wear due to sliding between the first friction member 18 and the cam follower 21 can be suppressed, and the durability of the cam follower 21 and the first friction member 18 can be improved. As a result, the durability of the clutch operation reaction force generating device 5 can be improved.

[0192] Further, according to the clutch operation reaction force generating device 5 of the present embodiment, the first friction member 18 attached to the inclined wall 12D has a first sliding surface 18b on which the cam follower 21 slides, and the inclined wall 12D and the first friction member 18 are inclined with respect to the moving direction A of the cam plate 14.

[0193] The cylindrical support portion 12 has a second sliding surface 19b on which the cam plate 14 slides, and has a bottom wall 12A extending along the moving direction A of the cam plate 14 and a second friction member 19.

[0194] In addition to this, the inclined wall 14D and the first friction member 18 and the bottom wall 12A and the second friction member 19 are formed such that the distance between the inclined wall 14D and the first friction member 18 and the bottom wall 12A and the second friction member 19 becomes narrower as the cam follower 21 moves in the direction away from the clutch pedal 4 (front side), and the coil spring 17 pushes the cam follower 21 in the direction in which the distance between the inclined wall 14D and the first friction member 18 and the bottom wall 12A and the second friction member 19 becomes narrower.

[0195] Thereby, a wedge-shaped space that gradually becomes smaller as the cam follower 21 moves forward can be formed between the inclined wall 12D and the first friction member 18 and the bottom wall 12A and the second friction member 19. And the coil spring 17 biases the cam follower 21 so as to push the cam follower 21 into this wedge-shaped space.

[0196] Therefore, the play between the cam follower 21 and the cam surface 14C can be eliminated, and the play between the cam follower 21 and the first friction member 18 can be eliminated.

[0197] As a result, it is possible to suppress the generation of abnormal noise from the clutch operation reaction force generating device 5 due to the collision between the cam follower 21 and the cam surface 14C, and it is also possible to suppress the generation of abnormal noise from the clutch operation reaction force generating device 5 due to the collision between the cam follower 21 and the first friction member 18.

[0198] Further, according to the clutch operation reaction force generating device 5 of the present embodiment, a rod member 15 having a pedal connecting portion 15B connected to the clutch pedal 4 at the rear end portion and a cylindrical cam plate connecting portion 15A connected to the rear end portion 14c of the cam plate 14 at the front end portion is provided.

[0199] Engagement grooves 11i and 11j that are detachably engaged with the cam plate connecting portion 15A are provided at the rear end portion of the cam body 10 (the rear end portions of the rear left side wall 11E and the rear right side wall 11F), and hook portions 11g and 11h that restrict the movement of the cam plate 14 toward the clutch pedal 4 are provided.

[0200] The coil spring 17 is installed in a compressed state between the cam follower 21 and the spring receiving portion 14B of the cam plate 14, and by urging the cam plate 14 toward the clutch pedal 4, the cam plate connecting portion 15A is pressed against the engagement grooves 11i and 11j.

[0201] Thereby, in a state where the clutch pedal 4 is not depressed (a state where the clutch device is completely engaged), the coil spring 17 urges the cam plate 14 toward the clutch pedal 4, so that the cam plate connecting portion 15A can be pressed against the engagement grooves 11i and 11j.

[0202] Therefore, the cam follower 21 can be pressed against the cam surface 14C by the urging force of the coil spring 17, and the play between the cam follower 21 and the cam surface 14C can be eliminated.

[0203] Therefore, it is possible to more effectively suppress the collision between the cam follower 21 and the cam surface 14C due to the vibration associated with the running of the vehicle 1 or the vibration of the engine. As a result, it is possible to more effectively suppress the generation of abnormal noise from the clutch operation reaction force generator 5, and it is possible to more effectively suppress giving discomfort to the passengers.

[0204] Note that in the clutch operation reaction force generator 5 of the present embodiment, the clutch pedal 4 is connected to the cam plate 14 via the rod member 15, but the cam plate 14 may be directly connected to the clutch pedal 4.

[0205] Also, although the transmission of the present embodiment is configured as a MT, the transmission may be an AMT (Automated Manual Transmission).

[0206] Further, in the clutch operation reaction force generator 5 of the present embodiment, the inclined wall 12D of the cylindrical support portion 12 is on the upper side, and the front bottom wall 11B of the cam body 10 and the bottom wall of the cylindrical support portion 12 are on the lower side. However, the inclined wall 12D of the cylindrical support portion 12 may be on the lower side, and the front bottom wall 11B of the cam body 10 and the bottom wall of the cylindrical support portion 12 may be on the upper side.

[0207] Although embodiments of the present invention have been disclosed, it is obvious that those skilled in the art can make changes without departing from the scope of the present invention. It is intended that all such modifications and equivalents be included in the following claims.

Description of Reference Numerals

[0208] 4... Clutch pedal, 5... Clutch operation reaction force generating device, 10... Cam body, 11f... Front end (end of the cam body on the side opposite to the clutch pedal side), 11g, 11h... Hook portion (stopper portion), 11i, 11j... Engagement groove, 12... Cylindrical support portion, 12A... Bottom wall (second wall portion), 12D... Inclined wall (load direction conversion portion, first wall portion), 14... Cam plate, 14C... Cam surface, 14c... Rear end (end of the cam plate on the clutch pedal side), 14f... Front end (end side of the cam plate on the side opposite to the clutch pedal), 15... Rod member, 15A... Cam plate connection portion, 15B... Pedal connection portion, 17... Coil spring (biasing member), 18... First friction member (first wall portion), 18b... First sliding surface, 19... Second friction member (second wall portion), 19b... Second sliding surface, 21... Cam follower, 21B... Roller (contact portion), A1... First direction, A2... Second direction, F1... Load received by the cam follower from the biasing member, F2... Load received by the cam follower from the cam surface, F3... Resultant force direction of the load received by the cam follower from the biasing member and the load received by the cam follower from the cam surface

Claims

1. A clutch operation reaction force generator that generates an operation reaction force according to the amount of operation of a clutch pedal by a driver, comprising: a cam body; a cam plate having a cam surface and movably provided on the cam body so as to be interlocked with the operation of the clutch pedal; a cam follower having a contact portion that contacts the cam surface; a biasing member installed between the cam follower and the cam body; a cylindrical support portion provided at an end of the cam body on the side opposite to the clutch pedal side, and accommodating an end side of the cam follower and an end side of the cam plate on the side opposite to the clutch pedal; a load direction conversion portion is provided on the cylindrical support portion; The biasing member expands and contracts according to the movement of the cam plate to generate an operation reaction force on the clutch pedal and generate a load for pressing the cam follower against the cam surface; When the direction of the load received by the cam follower from the biasing member is defined as the first direction and the direction of the load for pressing the cam follower against the cam surface is defined as the second direction, the load direction conversion portion converts the load in the first direction applied to the cam follower into a load in the second direction different from the first direction. A clutch operation reaction force generator characterized by this.

2. The clutch operation reaction force generator according to claim 1, wherein the load direction conversion portion faces the resultant force direction of the load received by the cam follower from the biasing member and the load received by the cam follower from the cam surface, and extends in a direction perpendicular to the resultant force direction.

3. The load direction conversion portion has a first sliding surface on which the cam follower slides and is composed of a first wall portion inclined with respect to the moving direction of the cam plate; The cylindrical support portion has a second sliding surface on which the cam plate slides and has a second wall portion extending along the moving direction of the cam plate; The first wall portion and the second wall portion are formed such that the distance between the first wall portion and the second wall portion becomes narrower as the cam follower moves in a direction away from the clutch pedal; The clutch operation reaction force generator according to claim 1 or claim 2, wherein the biasing member pushes the cam follower in a direction in which the distance between the first wall portion and the second wall portion becomes narrower. Claim 4: A rod member having a pedal connecting portion connected to the clutch pedal at one end and a cylindrical cam plate connecting portion connected to the end of the cam plate on the clutch pedal side at the other end, wherein a stopper portion is provided at the end of the cam body on the clutch pedal side, the stopper portion having an engagement groove that detachably engages with the cam plate connecting portion to restrict movement of the cam plate toward the clutch pedal side. The biasing member is installed in a compressed state between the cam follower and the cam plate, and biases the cam plate toward the clutch pedal side, thereby pressing the cam plate connecting portion against the engagement groove. The clutch operation reaction force generating device according to any one of claims 1 to 3. Claim 5: A clutch operation reaction force generating device that generates an operation reaction force corresponding to an operation amount of a clutch pedal by a driver, comprising a cam body, a cam plate having a cam surface and movably provided on the cam body so as to be interlocked with an operation of the clutch pedal, a cam follower having a contact portion that contacts the cam surface, a biasing member installed between the cam follower and the cam body, and a rod member having a pedal connecting portion connected to the clutch pedal at one end and a cylindrical cam plate connecting portion connected to the end of the cam plate on the clutch pedal side at the other end, wherein a stopper portion is provided at the end of the cam body on the clutch pedal side, the stopper portion having an engagement groove that detachably engages with the cam plate connecting portion to restrict movement of the cam plate toward the clutch pedal side, the biasing member is installed in a compressed state between the cam follower and the cam plate, and biases the cam plate toward the clutch pedal side, thereby pressing the cam plate connecting portion against the engagement groove, and the biasing member expands and contracts in accordance with movement of the cam plate, thereby generating an operation reaction force on the clutch pedal and generating a load that presses the cam follower against the cam surface. The clutch operation reaction force generating device.

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