JP5934157B2 - Multi-disc transmission - Google Patents

Description

  The present invention relates to a multi-disc transmission.

  In Patent Document 1, a primary disk provided on the input shaft and a secondary disk provided on the output shaft are partially overlapped to provide a disk overlap area, and both disks are sandwiched between a pair of pressing rollers in this area. A multi-disc transmission that transmits the rotation of an input shaft to an output shaft by bringing them into contact is disclosed.

  In a multi-disc transmission, a shift is realized by changing a position where a pair of pressing rollers sandwich both discs. That is, if the position between the two disks is close to the input shaft, the gear ratio changes to the low side (large gear ratio side), and if close to the output shaft, the gear ratio changes to the high side (low gear ratio side). .

JP 2010-53995 A

  In the multi-disc transmission described above, the pressing force is applied from the pressing roller to the disc by directly applying the urging force of the spring to the pair of pressing rollers. However, as a structure in which the pressing force is applied from the pressing roller to the disc. For example, a pressing roller is attached to each of a pair of arms whose one end is rotatably supported by a rotating shaft, and the distance between the open ends of the pair of arms is reduced, thereby pressing the disc from the pressing roller to the disk. A structure in which force is applied can also be used.

  However, in the above structure, since the end portion of the arm is supported by the rotation shaft, the axial displacement of the rotation shaft of the pair of arms due to the backlash of the movable portion becomes large at a position far from the rotation shaft. Cheap. When such misalignment occurs, the axial displacement of the rotating shaft also occurs at the position where the pair of pressing rollers attached to the pair of arms contact the disk. There is a problem that the frictional loss due to the peripheral speed difference of the disk becomes large and the transmission loss of the transmission decreases.

  The present invention has been made in view of such a technical problem, and an object of the present invention is to suppress displacement of a position where a pair of pressing rollers contact a disk.

According to an aspect of the present invention, there is provided a multi-disc transmission, an input shaft to which rotation from a power source is input, an output shaft disposed in parallel to the input shaft, and the input shaft. A primary disk, a secondary disk provided on the output shaft and having a disk overlapping area overlapping with the primary disk, and one end of which is rotatably connected via a rotating shaft, and in the disk overlapping area A pair of arms disposed on both sides of the primary disk and the secondary disk; a pair of pressing rollers mounted on the pair of arms and disposed on both sides of the primary disk and the secondary disk; and A pressing force is applied to the pair of arms, and the pair of pressing rollers are moved to the primary disk and the A disc clamp mechanism for pressing the cans secondary disk, the arranged on both sides of the primary disk and the secondary disk, the pair of arms is inserted respectively between the rotating shaft and the pressing roller to the pair of arms Movably supported between the input shaft and the output shaft, and when a pressing force is applied to the pair of arms from the disk clamp mechanism, the pair of arms are elastically deformed to allow the pair of arms to rotate. A multi-disc transmission comprising a guide shaft and a speed change actuator that moves the pair of arms between the input shaft and the output shaft is provided.

According to the above aspect, since the pair of arms are supported by the guide shafts inserted into the arm between the rotation shaft and the pressing roller, the position where the arms are supported is more than the case where the rotation shaft supports the arm. Is also close to the pressing roller. Therefore, it is possible to suppress the displacement of the position where the pair of pressing rollers contact the disk. In addition, when a pressing force is applied to the pair of arms from the disk clamp mechanism, the guide shafts are elastically deformed and the pair of arms are allowed to rotate. A pressing force can be applied.

1 is an overall schematic view of a vehicle including a multi-disc transmission. It is the figure which looked at the multi disc transmission from the engine side. FIG. 3 is a bottom view in FIG. 2. It is IV-IV sectional drawing of FIG. It is VV sectional drawing of FIG. It is VI-VI sectional drawing of FIG. It is VII-VII sectional drawing of FIG.

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

  FIG. 1 is an overall schematic view of a vehicle including a multi-disc transmission 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, and left and right drive wheels 6 and 7.

  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. In addition, about drawing after FIG. 2, a part of member is abbreviate | omitted for description.

  The primary disk 11 is configured by arranging two circular disks 11 a in the axial direction of the input shaft 10 and attaching them to 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 includes a center disk 12 a and a side disk 12 b arranged in the axial direction of the output shaft 14 and attached 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 overlap region where a part of the disk overlaps between the input shaft 10 and the output shaft 14.

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

  On the other hand, in a situation where the pressing force by the pressing mechanism 13 is applied, the primary disk 11 and the secondary disk 12 are elastically deformed to come into contact with 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 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 pressing mechanism 13 includes a pressing roller mechanism 30, a disk clamp mechanism 31, a pressing force adjustment mechanism 32, and a first actuator 33.

  The first actuator 33 moves the pressing roller mechanism 30 along the axis connection line O.

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

  One end of the ball screw mechanism 35 is coupled to the rotating shaft of the electric motor 34 and rotates in the forward direction or the reverse direction depending on the rotating direction of the rotating shaft of the 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 electric motor 34 side. When the bracket 37 is reciprocated by the 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. The clutch is engaged and released.

  The bracket 37 is connected to the roller holding arms 42 and 43 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 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 moves to the bracket 37 and the first. It is integrated with the shaft 38 and moves back and forth along the direction of the axis connection line O.

  5 is a cross-sectional view taken along the line VV in FIG.

  The pressing roller mechanism 30 includes a pressing roller 40, a holding unit 41, roller holding arms 42 and 43, a rolling shaft 44, and an urging unit 45.

  The pressing roller mechanism 30 is disposed on both sides of the primary disk 11 and the secondary disk 12 and is slidably supported by the two guide shafts 51. The guide shaft 51 is disposed on both sides of the primary disk 11 and the secondary disk 12, and extends in the direction of the axis connection line O and is attached to the transmission case 9 as shown in FIG. Both ends are supported by The pressing roller mechanism 30 is moved in the direction of the axis connection line O by the first actuator 33 and forms a torque transmission contact portion at a position where a target speed ratio is realized. The guide shaft 51 will be described in detail later.

  One end of each of the roller holding arms 42 and 43 is rotatably connected via a rotation shaft 52. As shown in FIG. 5, the roller holding arms 42 and 43 have a cross-sectional shape opened to the disks 11 and 12 side.

  Roller shafts 44 are attached to the open ends of the roller holding arms 42 and 43, respectively. The rolling shaft 44 is rotatably supported by the roller holding arms 42 and 43 via needle bearings provided at both ends. When a pressing force is applied to the rolling shaft 44 from the front clamp arm 67 and the rear clamp arm 68 of the disc clamp mechanism 31, the roller holding arms 42 and 43 rotate about the rotation shaft 52. When the pressing roller mechanism 30 is moved in the direction of the axis connection line O by the first actuator 33 in a state where the pressing force is applied, the rolling shaft 44 rolls, and thus the movement of the pressing roller mechanism 30 is hindered. There is no.

  The holding portion 41 is attached to the openings of the roller holding arms 42 and 43, respectively. The holding portion 41 has a support shaft 41a and a support shaft 41b that are mounted coaxially in a direction that intersects the direction of the axis connection line O. The support shaft 41a and the support shaft 41b provide the roller holding arms 42 and 43 with the support shaft 41a. , And is rotatably supported via a needle bearing.

  As shown in FIG. 4, the pressing roller 40 is rotatably supported by a first shaft portion 57 fixed to the holding portion 41 via a needle bearing. 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 increases, the pressing roller 40 elastically deforms the disks 11 and 12 to form a torque transmission contact portion.

  The urging portion 45 includes a bracket 45a and a compression spring 45b, and is attached to the roller holding arms 42 and 43, respectively. As shown in FIG. 5, the open end of the compression spring 45b abuts on the holding portion 41 at a position closer to the discs 11 and 12 than the support shafts 41a and 41b, which are pivotal central axes of the holding portion 41, as shown in FIG. The holding part 41 is always urged by the compression reaction force so that the holding part 41 rotates in the direction of the arrow. The holding part 41 comes into contact with a stopper (not shown) and stops rotating. The position of the stopper is, for example, in a state where the holding portion 41 is inclined by 1 ° in the direction of the arrow in FIG. 4 when the state in which the disks 11 and 12 and the holding portion 41 are orthogonal to each other is a reference angle (0 °). The rotation is set to stop.

  Here, the shape of the pressing roller 40 is set so as to contact the side disk 12b at a position offset to the input shaft 10 side with respect to the rotation center axis of the holding portion 41. The offset amount is 1 mm, for example. Therefore, when a pressing force is applied to the disks 11 and 12 from the pressing roller 40, the holding portion 41 is moved in the direction opposite to the arrow shown in FIG. 4 according to the reaction force that the pressing roller 40 receives from the disks 11 and 12. A moment to rotate is generated, and the holding portion 41 rotates in the direction opposite to the arrow in FIG. 4 so as to balance the urging force of the compression spring 45b.

  The shape of the pressing roller 40 is set so that the position where the side disk 12b contacts, that is, the above-described offset amount does not change even if the angle at which the holding portion 41 rotates and contacts the side disk 12b changes. At the same time, the pressing force applied from the pressing roller 40 to the disks 11 and 12 increases, and the curvature of the portion that contacts the side disk 12b increases as the holding portion 41 rotates in the direction opposite to the arrow in FIG. It is set to be smaller. Therefore, as the pressing force increases, the contact area between the pressing roller 40 and the side disk 12b increases, so that the stress applied to the pressing roller 40 and the disks 11, 12 is reduced, and the durability of the pressing roller 40 and the disks 11, 12 is reduced. Is secured.

  Next, the guide shaft 51 will be described. 6 is a cross-sectional view taken along the line VI-VI in FIG. FIG. 7 is a VII-VII cross section of FIG.

  The guide shaft 51 is inserted through the insertion hole 41 c formed in the holding portion 41 via the linear motion bush 53. The insertion hole 41c is formed in the holding portion 41 between the rotation shaft 52 and the pressing roller 40 and coaxially with the support shafts 41a and 41b. The two guide shafts 51 support the pressing roller mechanism 30 movably by supporting the roller holding arms 42 and 43 via the holding portion 41, respectively.

  As a structure for supporting the pressing roller mechanism 30 in this way, for example, the rotating shaft 52 extends in the direction of the axis connection line O and is fixed to the transmission case 9 to support the roller holding arms 42 and 43. In this case, since the end portions of the roller holding arms 42 and 43 are supported, the shafts of the roller holding arms 42 and 43 due to the backlash of the movable portion are provided at a position far from the rotation shaft 52. Misalignment in the direction of the core connecting line O tends to increase. When such misalignment occurs, the misalignment in the direction of the axis connection line O also occurs at a position where the pair of pressing rollers 40 respectively attached to the roller holding arms 42 and 43 via the holding portion 41 contacts the side disk 12b. Occurs. For this reason, the width of the torque transmission contact portion is widened, the friction loss due to the peripheral speed difference between the disks 11 and 12 is increased, and the transmission efficiency of the transmission 3 may be reduced.

  On the other hand, in the present embodiment, the roller holding arms 42 and 43 are supported via the holding portion 41 by the guide shaft 51 that is inserted into the holding portion 41 between the rotation shaft 52 and the pressing roller 40, respectively. The positions at which the roller holding arms 42 and 43 are respectively supported are closer to the pressing roller 40 than when the rotation shaft 52 is supported. For this reason, the influence of the positional deviation of the roller holding arms 42 and 43 in the direction of the axial connection line O on the positional deviation of the pair of pressing rollers 40 in the direction of the axial connection line O is reduced. The shift of the position in contact with 12b can be suppressed. Therefore, it is possible to suppress the width of the torque transmission contact portion from becoming wide and increase the friction loss due to the difference in peripheral speed between the disks 11 and 12, and to suppress the reduction in transmission efficiency of the transmission 3.

  Further, as described above, the angle at which the pressing roller 40 contacts the side disk 12b is changed by rotating the holding portion 41 in accordance with the magnitude of the pressing force applied from the pressing roller 40 to the disks 11 and 12. The durability of the pressing roller 40 and the disks 11 and 12 is ensured by changing the contact area between the pressing roller 40 and the side disk 12b, but the contact length between the insertion hole 41c and the direct acting bush 53 is long. Then, since the direct acting bush 53 prevents the holding portion 41 from rotating, the operating amount of the holding portion 41 cannot be ensured.

  In contrast, in the present embodiment, as shown in FIG. 6, a convex portion 41 d is formed over the entire circumference at the central portion of the inner periphery of the insertion hole 41 c, and the contact between the insertion hole 41 c and the linear motion bush 53 is achieved. Since the length is shortened, the direct acting bush 53 does not hinder the rotation of the holding portion 41. That is, since the guide shaft 51 supports the holding portion 41 through the linear motion bush 53 so as to be tiltable, the displacement of the position where the pair of pressing rollers 40 are in contact with the side disk 12b can be suppressed as described above. Even if the guide shaft 51 is inserted through the holding portion 41 at a position close to the pressing roller 40, the operation amount of the holding portion 41 can be secured, and the angle at which the pressing roller 40 contacts the side disk 12b can be changed. it can.

  Further, when a pressing force is applied from the disk clamp mechanism 31 to the roller holding arms 42 and 43, the roller holding arms 42 and 43 rotate around the rotation shaft 52. At this time, the rigidity of the guide shaft 51 is reduced. If it is high, the rotation of the roller holding arms 42 and 43 is hindered, and the pressing force cannot be applied to the disks 11 and 12 from the pressing roller.

  On the other hand, the guide shaft 51 according to the present embodiment causes the disc 11 to be pressed by the pressing force transmitted through the holding portion 41 when a pressing force is applied from the disc clamp mechanism 31 to the roller holding arms 42 and 43. The shaft is a thin shaft that is elastically deformed to the 12 side. Therefore, when a pressing force is applied to the roller holding arms 42 and 43, the guide shaft 51 is bent and the rotation of the roller holding arms 42 and 43 is allowed, so that the pressing roller 40 is not hindered. Thus, a pressing force can be applied to the disks 11 and 12.

  As described above, both ends of the guide shaft 51 are supported by the frame 9a. Specifically, as shown in FIG. 7, the plunger 54 is supported by the compression spring 54 a of the plunger 54 in a state of being urged toward the disks 11 and 12 in a slot hole provided in the frame 9 a.

  In a state where the disc clamping mechanism 31 does not apply a pressing force to the pressing roller mechanism 30, the roller holding arms 42 and 43 are extended in the direction in which the distance is increased by the reaction force of the discs 11 and 12 transmitted through the pressing roller 40. To turn. At this time, if the guide shaft 51 is fixed to the frame 9 a, the rotation of the roller holding arms 42 and 43 is hindered, and the disc clamping mechanism 31 does not apply the pressing force to the pressing roller mechanism 30. It is conceivable that the pressing roller 40 brings the primary disk 11 and the secondary disk 12 into contact with each other and rotation is transmitted from the input shaft 10 to the output shaft 14.

  In contrast, in this embodiment, when the reaction force of the disks 11 and 12 is transmitted to the guide shaft 51 via the pressing roller 20 and the holding portion 41, the guide shaft 51 compresses the compression spring 54a of the plunger 54. And move away from the disks 11 and 12. Therefore, the guide shaft 51 does not hinder the rotation of the roller holding arms 42, 43, and the disk clamp mechanism 31 rotates from the input shaft 10 to the output shaft 14 in a state where no pressing force is applied to the pressing roller mechanism 30. Can be prevented from being transmitted.

  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 axis 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 front clamp arm 67 is in contact with the rolling shaft 44 at the side surface 67 a (the surface forming the thickness of the plate member) on the disk 11, 12 side.

  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 (the surface forming the thickness of the plate member) of the rear clamp arm 68 is in contact with the rolling shaft 44.

  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 sandwich the roller holding arms 42 and 43 so that the primary disk 11 and the secondary disk 12 are subjected to a pressing force.

  As shown in FIG. 4, 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.

  As shown in FIG. 2, a rotating shaft 90 a of a second actuator 90 fixed to the transmission case 9 is connected to the rotating unit 73 via a connecting mechanism 91. The coupling mechanism 91 includes two shafts 91a and a slit coupling 91b, and the rotation unit 73 and the rotation shaft 90a of the second actuator 90 are connected to the shaft 91a.

  The slit coupling 91b is formed by forming a plurality of slits in the coupling connecting the two shafts 91a, and the thin portion between the slits is elastically deformed to elastically deform the two shafts 91a, the tensile direction, and the shearing direction. And a member that transmits rotation while allowing relative displacement in the bending direction.

  The rear clamp arm 68 rotates with the arm shaft 65 as a fulcrum by the pressing force generated by the pressing force adjusting mechanism 32. According to the configuration described above, the second actuator 90 is moved within the movable range of the slit coupling 91b. It becomes possible to decenter the rotation shaft 90a and the rotation center axis (second shaft portion 71) of the rotation unit 73 without resistance.

  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 reaction 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 rotates the second shaft portion 71 integrally with the rotary body 77 by the second actuator, and is always biased 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, that is, the pressing force which clamps the roller holding arms 42 and 43 is changed.

  As described above, according to the above aspect, the roller holding arms 42 and 43 are respectively supported via the holding portion 41 by the guide shaft 51 inserted between the rotating shaft 52 and the pressing roller 40 in the holding portion 41. Therefore, the position where the roller holding arms 42 and 43 are supported is closer to the pressing roller 40 than when the rotation shaft 52 is supported. For this reason, the influence of the positional deviation of the roller holding arms 42 and 43 in the direction of the axial connection line O on the positional deviation of the pair of pressing rollers 40 in the direction of the axial connection line O is reduced. The shift of the position in contact with 12b can be suppressed. Further, when a pressing force is applied to the roller holding arms 42 and 43, the guide shaft 51 is elastically deformed and the rotation of the roller holding arms 42 and 43 is allowed, so that the guide shaft 51 does not hinder the pressing. A pressing force can be applied to the disks 11 and 12 from the roller 40 (effect corresponding to claim 1).

  In addition, since the guide shaft 51 supports the holding portion 41 so as to be tiltable via the linear motion bush 53, the guide roller 51 is provided with the pressing roller 40 so that the displacement of the position where the pair of pressing rollers 40 contacts the side disk 12b can be suppressed. Even if the guide shaft 51 is inserted through the holding portion 41 at a close position, the operation amount of the holding portion 41 can be ensured, and the angle at which the pressing roller 40 contacts the side disk 12b can be changed. Corresponding effect).

  Further, since the guide shaft 51 is supported by the compression spring 54a of the plunger 54 in a state of being urged toward the discs 11 and 12 in the slot holes provided in the frame 9a, the disc clamp mechanism 31 is pressed against the pressing roller mechanism 30. When the reaction force of the disks 11 and 12 is transmitted to the guide shaft 51 via the pressing roller 40 and the holding portion 41 in a state where no pressing force is applied to the guide shaft 51, the guide shaft 51 compresses the compression spring 54a of the plunger 54. And move away from the disks 11 and 12. Therefore, the guide shaft 51 does not hinder the rotation of the roller holding arms 42, 43, and the disk clamp mechanism 31 rotates from the input shaft 10 to the output shaft 14 in a state where no pressing force is applied to the pressing roller mechanism 30. Can be prevented from being transmitted (effect corresponding to claim 3).

  The embodiment of the present invention has been described above, but the above embodiment is merely one example of application of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. is not.

3 Multi-disc transmission (transmission)
2 Engine (Power source)
DESCRIPTION OF SYMBOLS 10 Input shaft 14 Output shaft 11 Primary disk 12 Secondary disk 52 Rotating shaft 42 Roller holding arm (arm)
43 Roller holding arm (arm)
40 pressing roller 31 disc clamp Organization 51 guide shaft (guide shaft)
33 First actuator (shifting actuator)
41 Holding part (roller holding part)
54a Compression spring (spring)
9 Transmission case

Claims (3)

A multi-disc transmission,
An input shaft to which rotation from a power source is input;
An output shaft disposed parallel to the input shaft;
A primary disk provided on the input shaft;
A secondary disk provided on the output shaft and having a disk overlap area overlapping the primary disk;
A pair of arms that are rotatably connected via a rotation shaft and disposed on both sides of the primary disk and the secondary disk in the disk overlapping region;
A pair of pressing rollers respectively attached to the pair of arms and disposed on both sides of the primary disk and the secondary disk;
A disk clamping mechanism that applies a pressing force to the pair of arms, and presses the pair of pressing rollers against the primary disk and the secondary disk;
It is arranged on both sides of the primary disk and the secondary disk, and is inserted through the pair of arms between the rotating shaft and the pressing roller, respectively, and the pair of arms is connected between the input shaft and the output shaft. A pair of guide shafts that are elastically deformed and allow the pair of arms to rotate when a pressing force is applied to the pair of arms from the disk clamp mechanism.
A speed change actuator that moves the pair of arms between the input shaft and the output shaft;
A multi-disc transmission comprising: The multi-disc transmission according to claim 1,
The pair of arms are attached with the pair of pressing rollers, respectively, and change the angle of pressing the pair of pressing rollers against the primary disk and the secondary disk according to the magnitude of the pressing force acting from the disk clamping mechanism. Each has a roller holder,
The pair of guide shafts are respectively inserted into the roller holding portions and support the roller holding portions so as to be tiltable.
A multi-disc transmission characterized by that. The multi-disc transmission according to claim 1 or 2,
The pair of guide shafts in a state of being biased towards the primary disc and the secondary disc by a spring, are respectively supported on the transmission case,
A multi-disc transmission characterized by that.

Images