JP5795786B2 - Multi-disc transmission - Google Patents

Description

  The present invention relates to a multi-disc transmission.

  Conventionally, there is provided a disk overlapping area where a part of the input disk and a part of the output disk overlap each other, and the input disk and the output disk are held in contact with each other by a pair of pressing rollers in the disk overlapping area, and the input disk is changed to the output disk A transmission for transmitting rotation is disclosed in Patent Document 1.

JP 2010-53995 A

  In the above transmission, when the shift position of the shift lever is in the P range, the input disk and the output disk are prevented from rotating relative to each other by increasing the pressing force between the input disk and the output disk by the pressing roller. Thus, the vehicle is prevented from moving after stopping.

  In such a transmission, when the shift position is in the P range, in addition to the above state, the input shaft and the output shaft are directly connected by a gear or the like, and the vehicle is moved after stopping by interlocking the transmission. It is also possible to prevent this.

  In such a transmission, when the shift position is in the P range, the clutch must be released to protect the transmission by preventing rotation from being transmitted from the power source.

  When the shift position is changed from the P range to the travel range, for example, the R range, the interlock is released, the clutch is engaged, and the transmission of rotation from the power source to the transmission is started, but the interlock is released. If the clutch is engaged before rotation and rotation is transmitted from the power source to the transmission, the transmission, particularly the clutch, is damaged.

  The present invention has been invented to solve such a problem, in which the shift position is changed from the P range, and the rotation is transmitted from the power source to the transmission before the interlock is released. Also aims to reduce the above damage.

A multi-disc transmission according to an aspect of the present invention includes an input shaft connected to a power source, an output shaft disposed in parallel to the input shaft, a circle provided on the input shaft, and an outer peripheral end disposed close to the output shaft. According to the target gear ratio in a disk-shaped input disk, a disk-shaped output disk provided on the output shaft and having an outer peripheral end disposed close to the input shaft, and a disk overlapping region where the input disk and the output disk overlap each other A pair of pressing means that sandwich and press both discs at a position and form a torque transmission contact portion by elastic deformation of both discs, and a pair of arms that sandwich the pair of pressing means with a pivot shaft as a fulcrum An axis that rotates about an axis provided at one arm end opposite to the shaft and adjusts the clamping pressure according to the rotation angle, and an actuator that rotates the clamping pressure adjustment mechanism. Between the over data, when connected to a power source, and a reverse gear for rotating the output shaft and in the reverse direction rotation direction of the output shaft when the clamping pressing the discs by pressing means, a power source and the input shaft When the shift lever is in a parking range that prevents the vehicle from moving, the input shaft and reverse gear are connected, and both discs are clamped and pressed by the pressing means to transmit torque. When the shift lever is in the parking range and the brake pedal is depressed, the larger the amount of depression of the brake pedal , the smaller the clamping pressure by the clamping pressure adjustment mechanism. a pressing setting means for, when the position of the shift lever is parking range, clutch Ru is released.

  According to this aspect, by setting the clamping pressure based on the depression amount of the brake pedal, the shift position is changed from the P range to, for example, the R range, and before the interlock is released, the power source rotates to the transmission. Even when this is transmitted, it is possible to reduce damage to the multi-disc transmission.

It is the whole vehicle schematic of this embodiment. It is the figure which looked at the transmission from the engine side. FIG. 3 is a bottom view of FIG. 2. It is IV-IV sectional drawing of FIG. It is VV sectional drawing of FIG. It is a figure which shows the position or possible range of the 2nd roller follower in a shift position. It is a flowchart explaining rotation angle setting control. It is a map which shows the relationship between the depression amount of a brake pedal, and a 2nd roller follower.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  FIG. 1 is an overall schematic diagram of a vehicle 1 provided with a multi-disc transmission 3 according to an embodiment of the present invention.

  The vehicle 1 includes an engine 2 as a power source, a multi-disc transmission (hereinafter referred to as a transmission) 3, left and right drive shafts 4 and 5, left and right drive wheels 6 and 7, and a control unit (hereinafter referred to as a drive unit). , Called ATCU).

  The transmission 3 includes a transmission case 9, an input shaft 10, a primary disk 11, a secondary disk 12, a pressing mechanism 13, an output shaft 14, a dry start clutch 15, a reverse gear 16, and a reverse idler gear. 17, an output gear 18, a synchronization mechanism 19, a final gear 20, and a differential gear unit 21.

  The input shaft 10 and the output shaft 14 are arranged in parallel and are rotatably supported by the transmission case 9.

  FIG. 2 is a view of the transmission 3 as viewed from the engine 2 side. FIG. 3 is a bottom view of FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG. 5 is a cross-sectional view taken along the line VV in FIG. In addition, about drawing after FIG. 2, a part of member is abbreviate | omitted for description.

  The primary disk 11 is configured as an input shaft 10 in which two circular disks 11 a are arranged in the axial direction of the input shaft 10, and rotates integrally with the input shaft 10. A spacer 22 is provided between the two disks 11 a, and the two disks 11 a are arranged at a predetermined interval in the axial direction of the input shaft 10 by the spacer 22. The primary disk 11 is arranged so that the outer peripheral end of the disk 11 a is close to the output shaft 14. The primary disk 11 rotates with the input shaft 10 in the direction of the arrow in FIG.

  The secondary disk 12 includes a center disk 12a and two side disks 12b provided facing both sides of the center disk 12a. The secondary disk 12 is configured by arranging a center disk 12 a and a side disk 12 b in the axial direction of the output shaft 14 and attaching to the output shaft 14, and rotates integrally with the output shaft 14. A spacer 23 is provided between the center disk 12a and the side disk 12b, and the center disk 12a and the side disk 12b are arranged with a predetermined distance in the axial direction of the output shaft 14 by the spacer 23. The secondary disk 12 is arranged so that the outer peripheral end of the center disk 12 a and the outer peripheral end of the side disk 12 b are close to the input shaft 10.

  The disk 11a of the primary disk 11 is disposed between the center disk 12a of the secondary disk 12 and the side disk 12b. The primary disk 11 and the secondary disk 12 form a disk overlapping region where a part of the disks 11 and 12 overlap between the input shaft 10 and the output shaft 14.

  In the disk overlapping region, a gap is formed between the primary disk 11 and the secondary disk 12 in a state where the pressing force by the pressing mechanism 13 described in detail below does not act or in a state where the pressing force is small.

  On the other hand, when the pressing force by the pressing mechanism 13 is applied and the pressing force is large, the primary disk 11 and the secondary disk 12 are elastically deformed to contact each other, and a torque transmission contact portion is formed. In the transmission 3, the transmission of rotation from the input shaft 10 to the output shaft 14 is realized by forming a torque transmission contact portion between the primary disk 11 and the secondary disk 12.

  The pressing mechanism 13 includes a pair of pressing roller mechanisms 30, a disk clamp mechanism 31, a pressing force adjusting mechanism 32, a first actuator 33, and a second actuator 90.

  The first actuator 33 moves the pressing roller mechanism 30 along the axis connection line O. The axis connection line O is a line that connects the axis of the input shaft 10 and the axis of the output shaft 14 and is orthogonal to the input shaft 10 and the output shaft 14.

  The first actuator 33 includes a first electric motor 34, a ball screw mechanism 35, and a bracket 37.

  One end of the ball screw mechanism 35 is coupled to the rotation shaft of the first electric motor 34 and rotates in the forward direction or the reverse direction depending on the rotation direction of the rotation shaft of the first electric motor 34. The ball screw mechanism 35 is extended in the direction of the axis connection line O.

  When the ball screw mechanism 35 rotates, the bracket 37 moves along the axial direction of the ball screw mechanism 35, that is, the direction of the axial center connection line O according to the rotation of the ball screw mechanism 35. The bracket 37 is formed with a tapered surface 37a on the surface on the engine 2 side, the distance from the ball screw mechanism 35 becomes shorter toward the first electric motor 34 side. When the bracket 37 is reciprocated by the first electric motor 34, a push rod (not shown) that follows a tapered surface 37a like a so-called cam follower is reciprocated, and the release lever of the dry start clutch 15 is driven by the push rod. Then, the dry start clutch 15 is engaged and released. When the pressing roller mechanism 30 is closer to the input shaft 10 than the lowest position, the dry start clutch 15 is released.

  The bracket 37 is connected to the second support portion 44 and the roller follower support block 48 of the pressing roller mechanism 30 via a first shaft 38 that extends in the direction of the axis connection line O. When the ball screw mechanism 35 is rotated by the first electric motor 34, the bracket 37 moves back and forth along the direction of the axis connection line O according to the rotation direction of the ball screw mechanism 35, and the pressing roller mechanism 30 The first shaft 38 and the first shaft 38 move forward and backward along the direction of the axis connection line O.

  The pressing roller mechanism 30 includes a pressing roller 40, a holding portion 41, a pressing roller shaft 42, a first support portion 43, a second support portion 44, a support block 46, and a first roller follower 47.

  The pair of pressing roller mechanisms 30 are disposed on both sides of the primary disk 11 and the secondary disk 12 and are attached to the guide block 49. The guide block 49 is slidably supported by two guide shafts 51 provided between the two guide shaft blocks 50 attached to the transmission case 9 and extending in the direction of the axis connection line O. In other words, the pressing roller mechanism 30 is slidably supported by the guide shaft 51 via the guide block 49, moves in the direction of the axis connection line O by the first actuator 33, and transmits torque to a position corresponding to the target gear ratio. A contact portion is formed.

  The pressing roller shaft 42 extends in a direction intersecting with the direction of the axis connection line O, one end portion 42 a is supported by the first support portion 43, and the other end portion 42 b is supported by the second support portion 44. Is done. The pressing roller shaft 42 has a spherical end portion 42 b supported by the second support portion 44. A holding portion 41 that supports the pressing roller 40 is attached to the pressing roller shaft 42 between the first support portion 43 and the second supporting portion 44, and the pressing roller shaft 42 supports the pressing roller 40 via the holding portion 41. It is rotatably supported.

  The first support portion 43 is rotatably supported by the guide block 49 via a rotation shaft 52 provided in parallel with the guide shaft 51. The first support portion 43 supports one end portion 42 a of the pressing roller shaft 42 via the needle bearing 53.

  The second support portion 44 supports the other end portion 42 b of the pressing roller shaft 42 via the support block 46 and the needle bearing 54. A bush 55 having a spherical tip 55a is provided between the second support portion 44 and the support block 46 in the axial direction of the input shaft 10, and a gap is provided between the second support portion 44 and the support block 46. Is formed. The gap in the axial direction of the input shaft 10 is positioned closer to the primary disk 11 than the bush 55, and the tip 55 a of the bush 55 contacts the support block 46. The second support portion 44 is connected to the end portion of the second shaft 56 that extends in the direction of the axis connection line O and the direction orthogonal to the axial direction of the input shaft 10 and to which the first roller follower 47 is attached. The second support portion 44 moves in the axial direction of the input shaft 10 by the pressing force applied to the first roller follower 47, and the first support portion 43 and the holding portion 41 that supports the pressing roller 40 according to this movement are: It rotates around the rotation shaft 52.

  The first support portion 43 is provided so as to form a gap between the needle bearing 53 and the pressing roller shaft 42 in the direction of the axis connection line O. The end portion 42 b of the pressing roller shaft 42 supported by the second support portion 44 has a spherical shape, and the end portion 42 b is in contact with the needle bearing 54. Accordingly, the pressing roller shaft 42 is supported by the first support portion 43 and the second support portion 44 so as to be rotatable and tiltable with respect to the direction of the axis connection line O.

  The holding portion 41 is provided between the first support portion 43 and the second support portion 44 and is attached to the pressing roller shaft 42. The holding portion 41 rotates and tilts integrally with the pressing roller shaft 42.

  A first shaft portion 57 is fixed to the holding portion 41. When the pressing roller shaft 42 is in a direction perpendicular to the axial center connection line O when viewed from the axial direction of the input shaft 10, the first shaft portion 57 coincides with the axial center connection line O. Further, the first shaft portion 57 is provided so that the first shaft portion 57 inclines with respect to the disk surface in FIG.

  The pressing roller 40 is rotatably supported by the first shaft portion 57.

  The pressing roller 40 contacts the side disk 12b in the disk overlapping region, and rotates around the first shaft portion 57. When the pressing force transmitted through the first roller follower 47 increases, the pressing roller 40 elastically deforms the disks 11 and 12 to form a torque transmission contact portion.

  The urging force of the springs of the urging portions 45 a and 45 b acts on the pressing roller 40 via the holding portion 41.

  In the first roller follower 47, as shown in FIG. 5, a second shaft 56 connected to the second support portion 44 is inserted into the inner peripheral hole 47a, and the front clamp arm 67 and the rear clamp arm 68 on the discs 11 and 12 side. Rolls in contact with the side surfaces 67a and 68a.

  The end of the second shaft 56 opposite to the end connected to the second support portion 44 is inserted into a hole 48 a formed in the roller follower support block 48. The hole 48 a is an oval-shaped hole formed along the axial direction of the input shaft 10. The roller follower support block 48 supports the second shaft 56 slidably in the axial direction of the input shaft 10 along the hole 48a. The roller follower support block 48 is connected to the bracket 37 via a first shaft 38 extending in the direction of the axis connection line O, and moves in the direction of the axis connection line O according to the movement of the bracket 37. That is, when the bracket 37 moves in the direction of the axis connection line O, the pair of pressing roller mechanisms 30 together with the roller follower support block 48 and the second shaft 56 move in the direction of the axis connection line O according to the movement.

  The disc clamp mechanism 31 includes an arm shaft 65, a front clamp arm 67, and a rear clamp arm 68.

  The arm shaft 65 is a columnar member that extends in a direction perpendicular to the shaft center connection line O and the input shaft 10. The arm shaft 65 is provided so as to be orthogonal to the input shaft 10 and to overlap the center of the primary disk 11 in the axial direction of the input shaft 10 as shown in FIG.

  The front clamp arm 67 is a plate-like member having an approximately L shape as shown in FIG. The front clamp arm 67 is rotatably supported on the arm shaft 65 on one end side. At the other end of the front clamp arm 67, an engaging portion 72 of a pressing force adjusting mechanism 32 described later is formed. As shown in FIG. 5, the side surface 67 a of the front clamp arm 67 on the side of the disks 11 and 12 contacts the first roller follower 47.

  The rear clamp arm 68 is a plate-like member having an approximately L shape as shown in FIG. The rear clamp arm 68 is rotatably supported on the arm shaft 65 on one end side. The other end of the rear clamp arm 68 is connected to a case 70 of a pressing force adjusting mechanism 32 described later. As shown in FIG. 5, the side surface 68 a of the rear clamp arm 68 on the side of the disks 11 and 12 contacts the first roller follower 47.

  The front clamp arm 67 and the rear clamp arm 68 are rotated about the arm shaft 65 by the pressing force generated by the pressing force adjusting mechanism 32, and the pressing force is applied to the holding portion 41 by sandwiching the pair of pressing roller mechanisms 30. A pressing force is applied from the pressing roller 40 to the primary disk 11 and the secondary disk 12.

  As shown in FIG. 3, the pressing force adjusting mechanism 32 includes a case 70, a second shaft portion 71, an engaging portion 72, a rotating portion 73, and a compression spring 74.

  The case 70 is connected to the end of the rear clamp arm 68. The case 70 accommodates a part of the rotating part 73, and the second shaft part 71 is attached thereto.

  The second shaft portion 71 is a columnar member parallel to the arm shaft 65, and supports the rotating portion 73 in a rotatable manner.

  The rotation unit 73 is rotated by the second actuator 90.

  The engaging portion 72 is formed at the end portion of the front clamp arm 67, and extends from the end portion toward the rear clamp arm 68, and the second shaft portion extends from the end portion of the connecting portion 75 on the rear clamp arm 68 side. And a curved surface portion 76 extending so as to surround 71. The curved surface portion 76 has an arc-shaped outer peripheral wall with the second shaft portion 71 as the center. The second roller follower 79 of the rotating portion 73 comes into contact with the outer peripheral wall of the curved surface portion 76 and rolls.

  The rotating unit 73 includes a rotating body 77, a rotation transmission block 78, and a second roller follower 79. The rotating body 77 includes a first body 80 and a second body 81.

  The first body 80 is a substantially U-shaped member extending so as to sandwich the second shaft portion 71. The first body 80 abuts on the outer peripheral wall of the second shaft portion 71 and is supported by the second shaft portion 71 so as to be rotatable and slidable. The first body 80 includes a stopper 82 that supports one end of the compression spring 74 at the end on the open side.

  The rotation transmission block 78 is supported by the second shaft portion 71 so that the second shaft portion 71 passes therethrough and is rotatable. The rotation transmission block 78 supports the end of the compression spring 74 opposite to the end supported by the stopper 82.

  The first body 80 and the second body 81 are joined, and the second roller follower 79 is attached to the second body 81.

  The rotating body 77 is always urged in the direction from the second shaft portion 71 toward the stopper 82 by the restoring force of the compression spring 74. However, the second body 81 located on the opposite side to the compression spring 74 with respect to the second shaft portion 71 abuts on the rotation transmission block 78, and the rotation body 77 moves from the second shaft portion 71 toward the compression spring 74. Is regulated.

  The second roller follower 79 rolls in contact with the arc-shaped outer peripheral wall of the curved surface portion 76. The second roller follower 79 is rotated integrally with the rotating body 77 via the second shaft portion 71 by the second actuator 90, and is always urged toward the second shaft portion 71 by the compression spring 74.

  The pressing force adjusting mechanism 32 rotates the second roller follower 79 around the second shaft portion 71 by the second actuator 90, and directs the second roller follower 79 toward the second shaft portion 71 by the compression spring 74. Change the direction of the force applied. Thereby, the force which pushes the front clamp arm 67 to the rear clamp arm 68 side, ie, the pressing force which clamps a pair of pressing roller mechanism 30, is changed.

  Here, the relationship between the position of the second roller follower 79 and the pressing force by the pressing roller mechanism 30 will be described.

  When the second roller follower 79 is at the position shown in FIG. 3, that is, when the rotary body 77 is parallel to the direction of the axis connection line O, the pressing force by the pressing roller mechanism 30 is substantially zero. If this position is the reference position and the rotation angle of the second roller follower 79 from the reference position is the rotation angle, the pressing force by the pressing roller mechanism 30 gradually increases as the rotation angle increases. When the rotation angle reaches 90 degrees (hereinafter referred to as the maximum angle), the pressing force by the pressing roller mechanism 30 is maximized.

  Even if the pressing force is generated until the rotation angle reaches the first predetermined angle from the reference position, the torque transmission contact portion is not formed by the reaction force of the primary disk 11, and the rotation angle is the first angle. When the angle is larger than the predetermined angle, the primary disk 11 and the secondary disk 12 are elastically deformed and brought into contact with each other by the pressing force, and a torque transmission contact portion is formed.

  The second actuator 90 includes a second electric motor 91 and a coupling mechanism 92.

  The second electric motor 91 is fixed to the transmission case 9. The coupling mechanism 92 includes a slit-type coupling 92a, a third shaft 92b coupled to the rotating shaft of the second electric motor 91, and a fourth shaft 92c coupled to the rotating portion 73 via the second shaft portion 71. Is provided.

  The synchronization mechanism 19 includes a coupling sleeve 19a, and moves the coupling sleeve 19a mechanically in conjunction with the operation of the shift lever by the driver, so that the reverse gear 16 and the input shaft 10 are moved via the coupling sleeve 19a. And release. When the reverse gear 16 and the input shaft 10 are fastened via the coupling sleeve 19a, the input shaft 10 and the output shaft are rotated so that the output shaft 14 rotates in the direction opposite to the rotation direction when the torque transmission contact portion is formed. 14, the rotation generated in the engine 2 is transmitted in the order of the reverse gear 16, the reverse idler gear 17, and the output shaft 14, and the vehicle 1 can be moved backward. Thus, the synchro mechanism 19, the reverse gear 16, and the reverse idler gear 17 function as a reverse mechanism.

  The ATCU 8 includes a signal from the brake fluid pressure sensor 105 that detects the amount of depression of the brake pedal, a signal from the inhibitor switch 106 that detects the shift position of the shift lever, and an ECU (not shown) that controls the engine 2. And a signal related to the input torque.

  The ATCU 8 controls the first electric motor 34 and the second electric motor 91 based on the input signal. The ATCU 8 is configured by a CPU, a ROM, a RAM, and the like, and the functions of the ATCU 8 are exhibited when the CPU reads a program stored in the ROM.

  Next, the operating state of the transmission 3 at the shift position will be described.

(D range)
When the shift position is in the D range, the dry start clutch 15 is engaged, the reverse gear 16 and the input shaft 10 are released by the synchro mechanism 19, the torque transmission contact portion is formed by the pressing force adjusting mechanism 32, and the engine 2 The rotation is transmitted to the drive wheels 6 and 7 through the transmission 3.

  When the shift position is in the D range, as shown in FIG. 6, the second roller follower 79 (second actuator) is set so that the rotation angle is between the second predetermined angle larger than the first predetermined angle and the maximum angle. 90) is controlled. The second predetermined angle is an angle that generates a pressing force that enables the vehicle 1 to travel when rotation is transmitted from the engine 2. The position of the second roller follower 79 is set based on engine torque or the like. FIG. 6 is a schematic diagram showing the position or possible range of the second roller follower 79 for each shift position corresponding to FIG.

(N range)
When the shift position is in the N range, the dry start clutch 15 is released, and the reverse gear 16 and the input shaft 10 are released.

(R range)
When the shift position is in the R range, the dry start clutch 15 is fastened, the reverse gear 16 and the input shaft 10 are fastened by the synchro mechanism 19, and the torque contact transmission unit is not formed by the pressing force adjusting mechanism 32. 2 transmits the rotation to the drive wheels 6 and 7 through the synchro mechanism 19 and the reverse gear 16.

  The second roller follower 79 is controlled so that the rotation angle is smaller than the first predetermined angle, and in this embodiment, the second roller follower 79 is set to a reference position (rotation angle = 0) as shown in FIG.

(P range)
When the shift position is in the P range (parking range), the dry start clutch 15 is released, the reverse gear 16 and the input shaft 10 are fastened via the synchro mechanism 19, and the torque transmission contact portion is pressed by the pressing force adjusting mechanism 32. Form. Thereby, the rotation direction of the output shaft 14 permitted via the synchro mechanism 19 and the rotation direction of the output shaft 14 permitted via the primary disk 11 and the secondary disk 12 are opposite to each other. In this manner, the vehicle 1 is prevented from moving by interlocking the transmission 3.

  When the shift position is in the P range and the brake pedal is not depressed by the driver, the second roller follower 79 is controlled so that the rotation angle becomes the maximum angle as shown in FIG. . Thereby, the pressing force generated by the pressing force adjusting mechanism 32 is increased, and the interlock brake force generated by the interlock when the shift position is in the P range can be increased.

  When the shift position is in the P range and the brake pedal is stepped on by the driver, the total brake brake force generated by the brake mechanism of the vehicle 1 when the brake pedal is depressed and the interlock brake force are summed. Power is generated in the vehicle 1.

  Since the vehicle 1 does not move if the minimum braking force that balances the force for moving the vehicle 1 is generated, it is not necessary to generate a braking force larger than the minimum driving force. Therefore, when the brake pedal is depressed by the driver and the foot brake force is ensured, the pressing force generated by the pressing adjustment mechanism 32 by setting the rotation angle of the second roller follower 79 smaller than the maximum angle. Can be reduced.

  Further, when the shift position is changed from the P range to the R range, for example, the dry start clutch 15 is engaged with the rotation angle of the second roller follower 79 larger than the second predetermined angle and the interlock brake force being large. Then, the dry start clutch 15 may be damaged.

  Therefore, in this embodiment, the rotation angle setting control of the second roller follower 79 is executed. The opening angle setting control will be described with reference to the flowchart shown in FIG.

  In step S100, the ATCU 8 determines whether the shift position is in the P range based on the signal from the inhibitor switch 106. The process proceeds to step S101 if the shift position is in the P range, and ends if the shift position is not in the P range.

  In step S101, the ATCU 8 determines whether the brake pedal is depressed based on a signal from the brake fluid pressure sensor 105. The process proceeds to step S102 when the brake pedal is depressed, and ends when the brake pedal is not depressed.

  In step S102, the ATCU 8 sets the rotation angle of the second roller follower 79 using FIG. 8 based on the depression amount of the brake pedal. That is, the ATCU 8 sets the pressing force generated by the pressing adjustment mechanism 32 based on the depression amount of the brake pedal. The rotation angle of the second roller follower 79 decreases as the amount of depression of the brake pedal increases, and becomes constant when the amount of depression of the brake pedal exceeds a predetermined amount. Even when the foot brake force is increased, if the shift position is in the P range, the rotation angle of the second roller follower 79 needs to be at least the second predetermined angle or more in order to interlock the transmission 3. Therefore, when the depression amount of the brake pedal becomes equal to or greater than the predetermined depression amount, the rotation angle of the second roller follower 79 is made constant, and a predetermined pressing force is generated to interlock. The predetermined pressing force is set in advance, and the rotation angle of the second roller follower 79 is equal to or greater than the second predetermined angle, and is a force that interlocks the transmission 3.

  As described above, the rotation angle of the second roller follower 79 is set based on the depression amount of the brake pedal, and when the depression amount of the brake pedal becomes large, the rotation angle is reduced and the pressing force generated by the pressing adjustment mechanism 32. Make it smaller. As a result, when the shift position is changed from the P range to the R range and the accelerator pedal is depressed before the interlock is released and the dry start clutch 15 is engaged, the interlock brake force is reduced to reduce the dry type. The damage received by the starting clutch 15 is reduced.

  The effect of this embodiment will be described.

  When the shift position is in the P range and the brake pedal is depressed, the rotation angle of the second roller follower 79 is set based on the depression amount of the brake pedal, and the pressing force generated by the pressing adjustment mechanism 32 is set. Set. As a result, even if the shift position is changed from the P range to the R range and the rotation is transmitted from the engine 2 before the interlock is released, damage to the dry start clutch 15 can be reduced ( Effect corresponding to claim 1). Further, in the above case, when the interlock is not released, the engine 2 may be stalled. However, in the present embodiment, the engine 2 can be prevented from stalling (corresponding to claim 1). effect).

  When the amount of depression of the brake pedal is large, reducing the interlock brake force reduces the damage received by the dry start clutch 15 and prevents the vehicle from moving when the shift position is in the P range. (Effect corresponding to claim 2). Moreover, when the brake pedal is depressed, the interlock can be released quickly by reducing the rotation angle, and the rotation is not transmitted from the engine 2 before the interlock is released. (Effect corresponding to claim 2).

  The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

2 Engine (Power source)
3 Multi-disc transmission 8 ATCU (Pressing setting means)
10 Input shaft 11 Primary disk (input disk)
12 Secondary disk (output disk)
14 Output shaft 16 Reverse gear 30 Pressing roller mechanism (pressing means)
31 Disk clamp mechanism 32 Pushing force adjustment mechanism 67 Front clamp arm (arm)
68 Rear clamp arm (arm)
73 Rotating part (Nipping pressure adjusting mechanism)
74 Spring (Nipping pressure adjustment mechanism)
90 Second actuator (actuator)

Claims (1)

An input shaft connected to a power source;
An output shaft arranged parallel to the input shaft;
A disc-shaped input disk provided on the input shaft and having an outer peripheral end disposed close to the output shaft;
A disc-shaped output disk provided on the output shaft and having an outer peripheral end disposed close to the input shaft;
A pair of pressing means for sandwiching and pressing both disks at a position corresponding to a target gear ratio in the disk overlapping region where the input disk and the output disk overlap each other, and forming a torque transmission contact portion by elastic deformation of both disks; ,
A pair of arms sandwiching the pair of pressing means, with the rotating shaft as a fulcrum;
A sandwiching pressure adjusting mechanism that pivots about an axis provided at one arm end opposite to the pivoting shaft, and that adjusts the sandwiching press according to a pivoting angle;
An actuator for rotating the clamping pressure adjusting mechanism;
When connected to the power source, a reverse gear that rotates the output shaft in a direction opposite to the rotation direction of the output shaft when the both discs are sandwiched and pressed by the pressing means;
A clutch provided between the power source and the input shaft ;
When the position of the shift lever is in a parking range that prevents movement of the vehicle, the input shaft and the reverse gear are connected, and the both discs are sandwiched and pressed by the pressing means, so that the torque transmission contact portion is A multi-disc transmission to form,
When the position of the shift lever is the parking range and the brake pedal is depressed, the larger the amount of depression of the brake pedal is, the smaller the clamping pressure by the clamping pressure adjusting mechanism is reduced .
The multi-disc transmission according to claim 1 , wherein the clutch is disengaged when the shift lever is in the parking range .

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