JP2007177909A - Twin clutch device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a twin clutch device having a less number of components, improved assembling work and reduced size, comprising a multiplate type first clutch having a first clutch outer and a multiplate type second clutch having a second clutch outer to be rotated with the first clutch outer and arranged coaxially with the first clutch, the pair of clutch outers being connected to each other in a relatively non-rotatable manner. <P>SOLUTION: The first clutch outer 36 has an annular plate portion 36b continuously provided at one end of a cylindrical portion 36a in one unit. The cylindrical portion 36a has a plurality of clutch disc engaging grooves 61 for engaging with a plurality of clutch discs 44 of the first clutch 34 in a relatively non-rotatable manner, and a plurality of clutch outer engaging grooves 62 arranged between the clutch disc engaging grooves 61 for engaging with the outer periphery of the second clutch outer 37 in a relatively non-rotatable manner. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention includes a first multi-plate type clutch having a cylindrical portion and having a first clutch outer that rotates by power transmission from a power source, and a second clutch outer that rotates together with the first clutch outer. The present invention relates to a twin clutch device provided with a multi-plate type second clutch arranged coaxially.

A twin clutch device in which the clutch outers of the first and second clutches are coaxially connected with bolts is already known from Patent Document 1, for example.
JP 61-153023 A

  However, in the structure in which both clutch outers are fastened by bolts as in the twin clutch device disclosed in Patent Document 1, the outer diameter of the clutch outer becomes large due to the bolt injector fastening, resulting in a large size of the twin clutch device. In addition to the increase in the number of parts, the number of parts and the number of assembly steps are increased.

  The present invention has been made in view of such circumstances, and a twin clutch device capable of reducing the number of parts and the number of assembling steps and enabling a reduction in size and connecting a pair of clutch outers so as not to be relatively rotatable. The purpose is to provide.

  In order to achieve the above object, the first aspect of the present invention is a multi-plate type first clutch having a cylindrical portion and having a first clutch outer that is rotated by power transmission from a power source, and rotates together with the first clutch outer. In the twin clutch device having a second clutch outer and a multi-plate type second clutch arranged coaxially with the first clutch, the first clutch outer arranged radially outward of the second clutch is: An annular plate portion is integrally connected to one end of the cylindrical portion, and a plurality of clutch disc engagement members are engaged with the outer periphery of the plurality of clutch discs included in the first clutch in a relatively non-rotatable manner. A plurality of clutch outers arranged between the engagement grooves for the respective clutch disks so that the outer periphery of the second groove and the outer periphery of the second clutch outer are engaged with each other in a relatively non-rotatable manner. And use engaging groove and which are located respectively.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect of the invention, the second clutch outer is disposed at a position where the first clutch inner provided in the first clutch is sandwiched between the annular plate portion. A retaining ring that contacts and engages with the outer periphery of the second clutch outer from the outside in the axial direction is attached to the first clutch outer.

  According to a third aspect of the invention, in addition to the configuration of the first or second aspect of the invention, the axial lengths of the clutch disk engagement groove and the latch outer engagement groove are set differently from each other. It is characterized by.

  Furthermore, in addition to the structure of any one of the first to third aspects, the clutch disk engagement groove and the latch outer engagement groove are opposite to the annular plate portion. It is provided in the cylindrical part at equal intervals in the circumferential direction while opening to the other end of the cylindrical part on the side.

  According to the first aspect of the present invention, the outer periphery of the plurality of clutch disks included in the first clutch is engaged with the cylindrical portion of the first clutch outer so as not to be relatively rotatable, and the outer periphery of the second clutch outer is relatively rotated. Since the engagement is impossible, when the first and second clutch outers are connected so as not to rotate relative to each other, the outer diameters of the first and second clutch outers are prevented from increasing and the twin clutch device is reduced in size. In addition, the number of parts can be reduced, and the number of assembling steps can be reduced to facilitate the assembling.

  According to the second aspect of the present invention, the movement of the second clutch outer relative to the first clutch outer to the axially outer side can be prevented with a simple configuration.

  According to the third aspect of the present invention, it is possible to easily prevent erroneous assembly of the plurality of clutch disks and the second clutch outer to the first clutch outer, thereby facilitating the assembly.

  Furthermore, according to the fourth aspect of the present invention, it is possible to more easily assemble the plurality of clutch disks and the second clutch outer to the first clutch outer.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below based on one embodiment of the present invention shown in the accompanying drawings.

  1 to 9 show an embodiment of the present invention. FIG. 1 is a diagram showing a schematic configuration of a twin clutch gear transmission, FIG. 2 is a longitudinal sectional view of a twin clutch device, and FIG. 4 is a sectional view taken along line 4-4 of FIG. 3, FIG. 5 is a cutaway perspective view of the first clutch outer, FIG. 6 is an enlarged sectional view taken along line 6-6 of FIG. 3, and FIG. FIG. 8 is a diagram showing the shaft rotation position and the lifter displacement amount in comparison, FIG. 8 is a diagram showing the speed change characteristic when shifting up, and FIG. 9 is a diagram showing the speed change characteristic when shifting down.

  First, in FIG. 1, for example, a plurality of pistons 11, 11... Provided in a multi-cylinder engine mounted on a motorcycle are connected in common to a crankshaft 12 rotatably supported by a crankcase (not shown). The rotational power 12 is input to the twin clutch device 15 via the primary reduction gear 13 and the damper rubber 14. On the other hand, the crankcase can be selectively established with an odd-numbered gear stage that can be selectively established, such as an odd-numbered gear stage gear transmission mechanism 16 having first and third gear stages G1 and G3. An even speed stage gear transmission mechanism 17 having second and fourth speed stage gear trains G2, G4, for example, is housed from the crankshaft 12 through a primary reduction device 13 and damper rubbers 14. Transmission and transmission interruption of the transmitted power to the odd speed gear transmission mechanism 16 and the even speed gear transmission mechanism 17 are switched by the twin clutch device 15.

  The crankcase includes a cylindrical first main shaft 18 having an axis parallel to the crankshaft 12 and a first main shaft 18 that coaxially penetrates the first main shaft 18 while allowing relative rotation while maintaining a constant axial relative position. Two main shafts 19 and a counter shaft 30 having an axis parallel to the first and second main shafts 18 and 19 are rotatably supported. Thus, the even speed gear transmission 17 is provided between the first main shaft 18 and the counter shaft 30, and the odd speed gear transmission 16 is provided between the second main shaft 19 and the counter shaft 30. A drive sprocket 31 is fixed to an end portion of the countershaft 30 that passes through the crankcase in a rotatable manner so that a chain for transmitting power to a rear wheel (not shown) is wound around the end.

  The second gear stage gear train G2 is rotatably supported by the second speed drive gear 25 integrally provided on the first main shaft 18 and the counter shaft 30, and meshes with the second speed drive gear 25. The fourth speed gear train G4 is supported by the fourth speed drive gear 27 fixed to the first main shaft 18 and the counter shaft 30 so as to be relatively rotatable. And a fourth speed driven gear 28 that meshes with the fourth speed drive gear 27. Further, a first shifter 29 is splined to the countershaft 30 between the second and fourth speed driven gears 26 and 28, and the second and fourth speed driven gears are moved by the axial movement of the second shifter 29. A state in which the gears 26 and 28 are freely rotated with respect to the countershaft 30 (neutral state) and one of the second and fourth speed driven gears 26 and 28 are coupled to the countershaft 30 so as not to be relatively rotatable. It is possible to switch between a state in which one of the second gear stage gear train G2 and the fourth gear stage gear train G4 is established.

  The first gear stage gear train G1 is supported by the first speed drive gear 20 integrally provided on the second main shaft 19 and the counter shaft 30 so as to be relatively rotatable and meshed with the first speed drive gear 20. The third speed gear train G3 is supported by the third speed drive gear 22 fixed to the second main shaft 19 and the counter shaft 30 so as to be relatively rotatable. And a third-speed driven gear 23 that meshes with the third-speed drive gear 22. A second shifter 24 is splined to the countershaft 30 between the first and third speed driven gears 21 and 23, and the first and third speed driven gears are moved by the axial movement of the first shifter 24. A state in which 21 and 23 are freely rotated with respect to the countershaft 30 (neutral state) and one of the first and third speed driven gears 21 and 23 are coupled to the countershaft 30 so as not to be relatively rotatable. It is possible to switch between a state in which one of the gear stage gear train G1 and the third gear train G3 is established.

  2 and 3 together, the twin clutch device 15 has a first clutch outer 36 that rotates with the power transmitted from the primary reduction gear 13, and the gear transmission mechanism for even speed stages from the crankshaft 12. 17 has a multi-plate type first clutch 34 that switches between transmission and shut-off of power to 17 and a second clutch outer 37 that rotates together with the first clutch outer 36, and is coaxially arranged radially inward of the first clutch 34. And a multi-plate type second clutch 35 that switches between transmission and interruption of power from the crankshaft 12 to the odd-numbered gear transmission mechanism 16, and the first clutch outer 36 is provided with an annular plate at one end of the cylindrical portion 36a. The parts 36b are integrally connected to form a bottomed cylindrical shape.

  The primary reduction gear 13 includes a drive gear 38 that is provided integrally with the crankshaft 12, and a driven gear 39 that is rotatably supported by the second main shaft 19 and meshes with the drive gear 38. Further, connecting bosses 36c are projected integrally at a plurality of locations in the circumferential direction of the annular plate portion 36b in the first clutch outer 36, and these connecting bosses 36c are provided in holding holes 40 provided in the driven gear 39. A holding plate 41 that passes through the inserted damper rubber 14 and contacts the driven gear 39 on the side opposite to the annular plate portion 36b is fastened to the end face of the connecting boss 36c by a rivet 42 that passes through the connecting boss 39c. The That is, the power from the crankshaft 12 is input to the first clutch outer 36 via the primary speed reducer 13 and the damper rubber 14.

  The first clutch 34 includes the first clutch outer 36 described above, a first clutch inner 43 having a cylindrical portion 43 a that is coaxially surrounded by the cylindrical portion 36 a of the first clutch outer 36, and a cylindrical portion of the first clutch outer 36. A plurality of first clutch disks 44, which are engaged with 36a in a relatively non-rotatable manner, and a first clutch disk 44, which is engaged with the cylindrical portion 43a of the first clutch inner 43 in a relatively non-rotatable manner. A plurality of first clutch plates 45 arranged in an overlapping manner, and a first clutch disk 44 and a first clutch plate 45 arranged alternately in an annular shape opposed to the annular plate portion 36b from the opposite side. The first pressure receiving plate portion 43b and the first clutch discs 44 and the first clutch plates 45 that are alternately overlapped with the annular plate portion 3 The first pressure plate 46 is urged to the side where the annular first pressure plate 46 facing from the b side, the first clutch discs 44, and the first clutch plates 45 are sandwiched between the first pressure receiving plate portion 43b. And a first clutch spring 47 that exerts a spring force.

  The first pressure receiving plate portion 43b is formed in an annular shape by projecting integrally from the outer end of the cylindrical portion 43a of the first clutch inner 43 outward in the radial direction. The first clutch inner 43 has an annular connecting plate portion 43c integrally projecting radially inward from the inner end of the cylindrical portion 43a. The inner periphery of the connecting plate portion 43c is the second main shaft. It is connected to 19 so that relative movement in the axial direction is disabled and relative rotation is disabled.

  The first pressure plate 46 is supported by the cylindrical portion 43a of the first clutch inner 43 so as to be capable of relative movement in the axial direction while disabling relative rotation, and is configured by overlapping a plurality of disc springs. The outer periphery of the one clutch spring 47 is brought into contact with the first pressure plate 47 via the annular first spring seat 48. Further, the inner periphery of the first clutch spring 47 is in contact with and supported by a retaining ring 49 attached to the outer periphery of the inner end portion of the cylindrical portion 43 a via the annular first retainer 50.

  Referring also to FIG. 4, the second clutch 35 has a cylindrical portion 37 a that is coaxially surrounded by the cylindrical portion 36 a of the first clutch inner 36 in the first clutch 34, and rotates together with the first clutch outer 36. The second clutch outer 37, the second clutch inner 53 having a cylindrical portion 53a coaxially surrounded by the cylindrical portion 37a of the second clutch outer 37, and the cylindrical portion 37a of the second clutch outer 37 are engaged with each other so as not to be relatively rotatable. And a plurality of second clutch disks 54, which are engaged with the cylindrical portion 53a of the second clutch inner 53 in a relatively non-rotatable manner and alternately overlap with the first clutch disks 54. The second clutch plates 55 and the second clutch disks 54 and the second clutch plates 55 that are arranged alternately are overlapped with the first clutch plates. The annular plate portion is disposed on the annular second pressure receiving plate portion 53b facing the annular plate portion 36b on the opposite side to the annular plate portion 36b, and on the second clutch disks 54 and the second clutch plates 55 arranged alternately. The second pressure plate 56 is biased to the side that sandwiches the annular second pressure plate 56, the second clutch discs 54,..., And the second clutch plates 55 from the second pressure receiving plate portion 53b. And a second clutch spring 57 that exerts a spring force.

  The second clutch outer 37 has an annular outer connecting plate portion 37b projecting radially outward from an outer end of the cylindrical portion 37a, and an annular projecting portion radially inward from an axial intermediate portion of the cylindrical portion 37a. The inner connecting plate portion 37c is integrally provided. Thus, the outer connecting plate portion 37b covers the first clutch inner 43 from the outside so that the first clutch inner 43 is disposed between the annular plate portion 36b of the first clutch outer 36 and the outer connecting plate portion 37b. The outer periphery of the cylindrical portion 37a is integrally connected to the outer end of the cylindrical portion 37a, and the outer periphery of the connecting plate portion 37b is engaged with the cylindrical portion 36a of the first clutch outer 36 in a relatively non-rotatable manner. The inner periphery of the inner connecting plate portion 37c is connected to the end portion of the first main shaft 18 projecting from the second main shaft 19 while disabling relative movement in the axial direction and disabling relative rotation.

  Referring also to FIG. 5, a plurality of clutch disks for engaging the outer periphery of the plurality of first clutch disks 54 in the first clutch with the cylindrical portion 36a of the first clutch outer 36 in a relatively non-rotatable manner. .. Are provided at equal intervals in the circumferential direction while opening to the other end of the cylindrical portion 36a on the side opposite to the annular plate portion 36b, and the outer coupling plate in the second clutch outer 37. A plurality of clutch outer engagement grooves 62, 62... For engaging the outer periphery of the portion 37 b in a relatively non-rotatable manner are disposed between the clutch disk engagement grooves 61, 61. The clutch disk engaging grooves 61, 61,... Are also opened at the outer peripheral surface of the cylindrical portion 36a.

  Moreover, the second clutch outer 37 is prevented from moving inward in the axial direction by a thrust bearing 68 described later, and the outer periphery of the outer coupling plate portion 37b of the second clutch outer 37 is contacted from the outer side in the axial direction. A retaining ring 63 that contacts and engages is attached to the cylindrical portion 36 a of the first clutch outer 36.

  Thus, on the outer periphery of the first clutch disk 44, an engaging projection 44a that engages with each of the clutch disk engaging grooves 61, 61 is projected, and the outer coupling plate portion 37b of the second clutch outer 37 is projected. Are engaged with the clutch outer engagement grooves 62, 62, and the clutch disk engagement grooves 61, 61, and the clutch outer. The axial lengths of the engaging grooves 62, 62... Are set differently from each other. In this embodiment, the connecting plate portion 37b of the second clutch outer 37 is more axial than the first clutch disc 44. The axial length of the clutch disk engaging grooves 61, 61... Is set larger than the axial length of the clutch outer engaging grooves 62, 62.

  A plurality of, for example, three first lifter pins for exerting a control force for driving the first clutch 34 that maintains the connected state by the spring force of the first clutch spring 47 against the spring force of the first clutch spring 47 toward the shut-off side 65... Have a line parallel to the rotational axis of the first clutch 34 and pass through a plurality of, for example, three places at equal intervals in the circumferential direction of the cylindrical portion 43 a of the first clutch inner 43, so as to be freely movable in the axial direction. One end of each of the first lifter pins 65 is brought into contact with the first pressure plate 46 of the first clutch 34 so as to be able to press the first pressure plate 46 against the spring force of the first clutch spring 47. The

  A plurality of, for example, three second lifter pins for exerting a control force for driving the second clutch 35 that maintains the connected state by the spring force of the second clutch spring 57 against the spring force of the second clutch spring 57 to the cutoff side 66... Have a line parallel to the rotational axis of the second clutch 35 and pass through a plurality of, for example, three places at equal intervals in the circumferential direction of the cylindrical portion 53a of the second clutch inner 53, so as to be freely movable in the axial direction. One end of each of these second lifter pins 66 is brought into contact with the second pressure plate 56 of the second clutch 35 so as to be able to press the second pressure plate 56 against the spring force of the second clutch spring 57. The

  Further, the first clutch inner 43 is sandwiched between the annular plate portion 36b of the first clutch outer 36, and the outer coupling plate portion 37b of the second clutch outer 37 constituting a part of the second clutch 35 is equally spaced in the circumferential direction. Drive pins 67 having an axis parallel to the rotation axes of the first and second clutches 34 and 35 are penetrated through a plurality of locations, for example, three locations, in an axially movable manner. Is connected to one end of the first lifter pins 65 through an annular thrust bearing 68.

  Further, in order to prevent the thrust bearing 68 from moving in a plane orthogonal to the axis of the first and second clutches 34 and 35, the outer connecting plate portion 37b has an annular recess 69 for receiving and holding the thrust bearing 68. It is formed.

  At the other end of the second lifter pins 66 and the other end of the drive pins 67, a camshaft 70 that is rotatable about an axis perpendicular to the rotation axis of the first and second clutches 34 and 35, and its cam A clutch disengagement / contact control means 72 having an actuator 71 coupled to the camshaft 70 so as to rotate the shaft 70 includes a second lifter pin 66... And the drive pin 67 according to the rotation position of the camshaft 70. ... are linked and linked to drive each other independently.

  The camshaft 70 is rotatably supported by a cover 73 coupled to a crankcase (not shown), and a return spring 74 is provided between the camshaft 70 and the cover 73.

  Referring also to FIG. 6, the camshaft 70 is disposed at the center between a pair of first cams 75, 75 that are spaced apart in the axial direction, and the first cams 75. A second cam 76 is integrally provided, and the camshaft 70 is supported by the cover 73 so that the second cam 76 is positioned on the extension line of the first and second main shafts 18 and 19. .

  The other ends of the drive pins 67 are connected to a ring-shaped first lifter 77 in common, and a first lifter 78 formed in a cylindrical shape so that one end thereof is in sliding contact with the first cams 75, 75. A first cam follower 77 is connected via a first release bearing 79. The other ends of the second lifter pins 66 are connected in common to an annular second lifter 80 that is coaxially surrounded by the first lifter 77, and the first lifter 78 is slidably contacted with the second cam 76. A second cam follower 80 is connected to a second lifter 81 slidably fitted to the second lifter 81 via a second release bearing 82.

  Referring to FIG. 2, the actuator 71 includes a single electric motor 85 and a speed reduction mechanism 86 that decelerates the output of the electric motor 85 and transmits it to the camshaft 70. The electric motor 85 having a rotation parallel to the motor is attached to a speed reduction mechanism case 87 supported by the crankcase so as to accommodate the speed reducer 86. Thus, the speed reduction mechanism case 87 is formed by coupling a pair of case halves 88 and 89 to each other, and the electric motor 85 has one of its output shafts 90 inserted into the speed reduction mechanism case 87. Attached to the case half 88.

  The speed reduction mechanism 86 is provided between the output shaft 90 of the electric motor 85 and the camshaft 70 in the speed reduction mechanism case 87, and includes a pinion 93 formed integrally with the output shaft 90, A first intermediate gear 94 that is provided integrally with a first intermediate shaft 91 that has an axis parallel to the camshaft 70 and is rotatably supported by the speed change mechanism case 87, and meshes with the pinion 93; The second intermediate gear 95 provided integrally with 91 and the second intermediate shaft 92 having an axis parallel to the output shaft 90 and the camshaft 70 and rotatably supported by the speed change mechanism case 87 are provided integrally. A third intermediate gear 96 meshed with the second intermediate gear 95, a fourth intermediate gear 97 provided integrally with the second intermediate shaft 92, and fixed to the camshaft 70 and meshed with the fourth intermediate gear 97. Consisting of Dohaguruma 98 Metropolitan.

  A potentiometer 99 connected coaxially to the end of the camshaft 70 is attached to the speed reduction mechanism case 87, and the rotation angle of the camshaft 70 is detected by the potentiometer 99.

  The first cams 75... And the second cams 76 are provided on the camshaft 70 with a phase difference of, for example, 90 degrees between them, and the actuator 71 includes the first cams 75. As shown in FIG. 7, the camshaft 70 is driven to rotate, and the power transmission to the even-speed gear transmission mechanism 17 is switched according to the rotation of the camshaft 70. The lift amount of the first lifter 78 corresponding to the clutch 34 changes as shown by the broken line in FIG. 7, and the second clutch 35 corresponding to the second clutch 35 that switches the power transmission to the odd-numbered gear transmission mechanism 16 is switched. The lift amount of the two lifters 81 changes as shown by the solid line in FIG.

  In other words, the actuator 71 switches the camshaft so as to switch between a state in which one of the first and second clutches 34, 35 is connected and the other is disconnected, and a state in which the first and second clutches 34, 35 are both connected. 70 is rotationally driven.

  The basic operation of the actuator 71 is to make one of the first and second clutches 34 and 35 in a connected state and the other in a disconnected state in a normal operation state, thereby allowing even-numbered gear shifting. One of the mechanism 17 and the gear transmission mechanism 16 for odd-numbered gears obtains a shift state by one gear train of even-numbered gears and odd-numbered gears. In the mechanism 16, when the gear shift is switched from the normal state, the gear train of the next gear stage that continues next in the gear shift direction among the gear trains G1 to G4 for the first to fourth speeds is changed to the next gear gear among the clutches 34 and 35. One of the first and second shifters 29 and 24 is operated so as to be established in advance in a state where the clutch corresponding to the gear train of the shift stage is disconnected, and then both clutches 3 , 35 connection and disconnection is switched by operation of the actuator 71.

  For example, when shifting from the first gear to the second gear, the first speed gear train G1 of the odd gear gear transmission mechanism 16 is established and the second clutch 35 is connected to change the first gear shift. In the state where the ratio is obtained, the second speed gear train G2 of the even gear stage gear train 17 is established with the first clutch 34 disengaged, and then the second clutch 35 is disengaged and the first gear train is disengaged. The clutch 34 is connected.

  By the way, at the time of performing the shift switching between the even speed stages or the odd speed stages, it corresponds to the gear transmission mechanism that is the object of gear train establishment switching among the even speed gear transmission mechanism 17 and the odd speed gear transmission mechanism 16. If the clutch is kept in the disengaged state, the first main shaft 18 or the second main shaft 18 on the input side of the gear transmission mechanism at the rotation speed before the gear train establishment switching is executed until the gear train establishment switching is completed. While the main shaft 19 rotates, when the gear train establishment switching is completed, the rotational speed of the first main shaft 18 or the second main shaft 19 changes greatly, and a shift shock occurs.

For example, when shifting up from the first speed gear stage to the third speed gear stage, the odd speed stage gear transmission mechanism 16 changes from the established state of the first speed gear train G1 to the established state of the third speed gear train G3. If the second clutch 35 is kept disconnected when the shifter 24 is operated, the rotational speeds of the crankshaft 12, the first main shaft 18 and the second main shaft 19 change as shown in FIG. To do. That is, the second clutch 35 is connected and the first clutch 34 is disconnected, the first speed gear train G1 is established in the odd speed gear transmission mechanism 16, and the second speed gear train of the even speed gear transmission mechanism 17 is established. When the second clutch 35 is disconnected and the first clutch 34 is connected at time t _{1 when} G2 is established and the gear ratio of the first gear is obtained, the second main shaft 19 is connected to the time before time t _1. It is rotated at the same rotational speed as, at time t ₂ of the condition, when establishing the third speed gear train G3 in the odd-numbered gear-change gear transmission mechanism 16, the rotational speed is decreasing side only ΔNa of the second main shaft 19 The gear shift shock will increase greatly.

Further, at the time of downshifting from the third speed gear stage to the first speed gear stage, the odd-numbered gear stage gear transmission mechanism 16 changes from the established state of the third speed gear train G3 to the established state of the first speed gear train G1. If the second clutch 35 is kept disconnected when the shifter 24 is operated, the rotational speeds of the crankshaft 12, the first main shaft 18 and the second main shaft 19 change as shown in FIG. 9 (a). To do. That is, the third speed gear train G3 is established in the odd speed gear transmission mechanism 16 and the second speed gear train G2 of the even speed gear transmission mechanism 17 is established, and the first clutch 34 is connected and the second clutch. At time t _{3 when} the gear ratio of the second gear is obtained by shutting off 35, the odd-numbered gear shift mechanism 16 is established from the third gear train G3 to the first gear train G1. When the start switching, so as to cut off the first clutch 34 while connecting the second clutch 35 further in a subsequent time t _4, the established state from the third speed gear train G3 to the first-speed gear train G1 At the switching time t ₃ , the rotation speed of the second main shaft 19 changes greatly to the increasing side by ΔNa, and the shift shock increases.

  Therefore, when executing the shift switching between the even speed stages or the odd speed stages, one of the even speed gear transmission mechanism 17 and the odd speed gear transmission mechanism 16 is in the middle of the gear train establishment switching. Of the even gear stage gear transmission mechanism 17 and the odd gear stage gear transmission mechanism 16, the clutch corresponding to the gear transmission mechanism to which the gear train is to be switched is briefly released from the disconnected state. Only after temporarily switching off as the connected state, the shift control for switching from the disconnected state to the connected state is performed after completion of the switching of the gear train.

Thus, for example, when shifting up from the first speed gear stage to the third speed gear stage, the odd speed stage gear transmission mechanism 16 changes from the established state of the first speed gear train G1 to the established state of the third speed gear train G3. When the second shifter 24 is operated, the crankshaft 12, the first main shaft 18 and the second clutch 35 when the second clutch 35 is temporarily connected for a short time in the neutral state of the gear transmission mechanism 16 for odd-numbered gears. The rotation speed of the second main shaft 19 changes as shown in FIG. That is, the second clutch 35 is connected and the first clutch 34 is disconnected, the first speed gear train G1 is established in the odd speed gear transmission mechanism 16, and the second speed gear train of the even speed gear transmission mechanism 17 is established. at time t ₁ in a state in which obtaining a gear ratio of first gear position to establish G2, after connecting the first clutch 34 while blocking the second clutch 35, the odd-numbered gear shift stage gear transmission mechanism 16 at time t ₁₂ in the first speed gear train G1 to the third speed neutral state in establishing switching換途gear train G3, the second clutch 35 is only temporarily connected state a short time (i.e., the first and second clutch 34 and 35 are temporarily connected to each other for a short time), and at this time, the first clutch 34 is in the connected state and the second speed gear train G2 of the even speed gear transmission 17 is established. Because the second me Nshafuto 19 will be lowered to the same level as the rotational speed of the first main shaft 18, speed change amount of the second main shaft 19 when a further time t ₂ has established a third speed gear train G3 is relatively A small value ΔNb (<ΔNa) is obtained, and the shift shock can be reduced.

Further, for example, at the time of downshift from the third speed gear stage to the first speed gear stage, the odd speed stage gear transmission mechanism 16 changes from the established state of the third speed gear train G3 to the established state of the first speed gear train G1. When the second shifter 24 is operated, the crankshaft 12, the first main shaft 18 and the first shaft 18 when the second clutch 35 is temporarily connected for a short time in the neutral state of the gear transmission mechanism 16 for odd-numbered gears. 2 The rotation speed of the main shaft 19 changes as shown in FIG. That is, the third speed gear train G3 is established in the odd speed gear transmission mechanism 16 and the second speed gear train G2 of the even speed gear transmission mechanism 17 is established, and the first clutch 34 is connected and the second clutch. In the state where the gear ratio of the second gear is obtained by shutting off 35, the established state is switched from the third gear train G3 to the first gear train G1 in the odd gear gear transmission mechanism 16. When the second clutch 35 is temporarily connected for a short time at the time t ₃ in the neutral state (that is, both the first and second clutches 34 and 35 are temporarily connected for a short time), At this time, since the first clutch 34 is in a connected state and the second speed gear train G2 of the even speed gear transmission 17 is established, the second main shaft 19 is rotated at the rotational speed of the first main shaft 18. Will be increased to the same level, the speed change amount of the second main shaft 19 when the first-speed gear train G1 in the subsequent time t ₃₄ is established relatively small value ΔNb (<ΔNa), and the shift shock Can be relaxed.

  Next, the operation of this embodiment will be described. A first clutch 34 having a first clutch outer 36 in which an annular plate portion 36b is integrally connected to one end of a cylindrical portion 36a, and a radially inner portion of the first clutch 34 are described. In the twin clutch device 15 including the second clutch 35 disposed coaxially, the first and second clutch inners 43 and 53 of the first and second clutches 34 and 35 respectively on the annular plate portion 36b side are provided. Ring-shaped first and second pressure plates 46 and 56 for switching the on / off state of the first and second clutches 34 and 35 are supported at the end portions so as to be operable in the axial direction, and the pressure plates thereof. First and second clutch springs 47 and 57 for urging 46 and 56 to the connection side are provided, respectively. One end of each of the first and second lifter pins 65, 66 having an axis parallel to the rotation axis of the hooks 34, 35 and passing through both the clutch inners 43, 53 so as to be movable in the axial direction is the pressure plates 46, 56. Can be pressed against the spring urging force of the clutch springs 47 and 57, and are in contact with the pressure plates 46 and 56, respectively, and are parallel to the rotation axes of the first and second clutches 34 and 35. One end of a drive pin 67 that has an axis and passes through the outer connecting plate portion 37b of the second clutch outer 37 so as to be axially movable, passes through the first clutch inner 43 of the lifter pins 65, 66. The other end of 65 is connected via a thrust bearing 68.

  Accordingly, the first and second clutches 34 and 35 are disconnected by applying an external force to the first and second lifter pins 65 and 66 passing through the first and second clutch inners 43 and 53, respectively, and pressing them in the axial direction. It can be. In addition, the first clutch inner 43 is disposed between the annular plate portion 36 b of the first clutch outer 36 and the outer connecting plate portion 37 b of the second clutch outer 37, and the second clutch outer 37 is rotated relative to the first clutch inner 43. Although possible, one end of the drive pin 67 that passes through the outer connecting plate portion 37b in an axially movable manner is connected to the other end of the first lifter pin 65 that passes through the first clutch inner 43 via a thrust bearing 68. Therefore, regardless of the relative rotation of the first clutch inner 43 and the second clutch outer 37, the first lifter pin 65 can be driven in the axial direction, and the thrust bearing 68 is provided between the first lifter pin 65 and the drive pin 67. Due to the simple structure interposed, the first clutch 34 having the first clutch inner 43 is made to act by the action of an external force. It can be a cutoff state.

  In addition, since the operating direction and the driving direction of the first and second lifter pins 65 and 66 are the same, the configuration of the clutch disconnection / contact control means 72 for driving the first and second clutches 34, 35 to disconnect / connect is simplified. Can be

  In addition, since the annular spring seats 48 and 58 are interposed between the first and second clutch springs 47 and 57 and the first and second pressure plates 46 and 57, respectively, the first and second clutch springs 47 are provided. , 57 can be applied evenly over the entire circumference of the pressure plates 46, 56, so that reliable switching between the first and second clutches 34, 35 can be obtained.

  Further, the other ends of the second lifter pin 66 and the drive pin 67 are rotatable around an axis perpendicular to the rotation axis of the first and second clutches 34 and 35 and are individually provided to the first and second clutches 34 and 35. The clutch disengagement / contact control means 72 having the camshaft 70 provided with the first and second cams 75, 76 corresponding to the second lifter pin 66 and the drive pin 67 according to the rotational position of the camshaft 70. The first and second clutches 34 are independently coupled to each other by using the clutch disengagement / contact control means 72 common to the first and second clutches 34 and 35. , 35 can be switched, and the structure for applying an external force to switch the connection / disconnection to the first and second clutches 34, 35 is simplified.

  The camshaft 70 is rotationally driven by a single actuator 71, and only one actuator 71 is required to rotationally drive the camshaft 70, so that the number of parts is reduced and the structure is simplified. In addition, the cost can be reduced and the size can be reduced.

  Furthermore, since the actuator 71 includes a single electric motor 85 and a speed reduction mechanism 86 that decelerates the output of the electric motor 85 and transmits it to the camshaft 70, the actuator 71 can be configured to be lightweight and compact. it can.

  By the way, a plurality of clutch disk engagement grooves 61 for engaging the outer periphery of the plurality of first clutch disks 44 in a relatively non-rotatable manner with the cylindrical portion 36a provided in the first clutch outer 35 of the first clutch 34; A plurality of clutch outer engagement grooves 62 arranged between the clutch disk engagement grooves 61 so as to engage the outer periphery of the second clutch outer 37 provided in the second clutch outer 35 in a relatively non-rotatable manner. And are provided respectively.

  That is, the outer periphery of the first clutch disks 44 is engaged with the cylindrical portion 36a of the first clutch outer 36 so as not to be relatively rotatable, and the outer periphery of the second clutch outer 37 is engaged so as not to be relatively rotatable. When the first and second clutch outers 36 and 37 are connected so as not to rotate relative to each other, the outer diameters of the first and second clutch outers 36 and 37 are prevented from becoming large, and the twin clutch device 15 is reduced in size. In addition, the number of parts can be reduced, and the number of assembling steps can be reduced to facilitate the assembling.

  The second clutch outer 37 is disposed at a position where the first clutch inner 43 provided in the first clutch 34 is sandwiched between the second clutch outer 37 and the outer periphery of the second clutch outer 37 from the outside in the axial direction. Since the retaining ring 63 that contacts and engages is attached to the cylindrical portion 36a, the movement of the second clutch outer 37 outward in the axial direction with respect to the first clutch outer 36 can be prevented with a simple configuration.

  Further, since the axial lengths of the clutch disk engagement grooves 61 and the latch outer engagement grooves 62 are set to be different from each other, the first clutch disks 44 and the first clutch outer 36 of the second clutch outer 37 are set. Assembling can be easily prevented, and this also facilitates the assembling.

  In addition, a plurality of clutch disk engagement grooves 61 and a plurality of clutch outer engagement grooves 62 open to the other end of the cylindrical portion 36a on the opposite side of the annular plate portion 36b of the first clutch outer 36. Since they are provided at equal intervals in the circumferential direction, the assembly of the plurality of first clutch disks 44... And the second clutch outer 37 to the first clutch outer 36 becomes easier.

  In the normal operation state, one of the first and second clutches 34 and 35 is connected and the other is disconnected so as to obtain a shift state by one gear train of the even-numbered gear stage and the odd-numbered gear stage. Therefore, it is possible to suppress the friction loss in the normal operation state.

  Further, when executing the gear change switching for changing the gear ratio from the normal operation state, the gear train of the next gear step that continues in the gear shift direction among the gear trains G1 to G4 of the plurality of gear steps corresponds to the gear train. Since it is established in advance with the clutch disconnected and the clutches 34 and 35 are switched between on and off, shifting control by switching between the clutches 34 and 35 is facilitated and the shift response is improved. Can do.

  Further, when performing the shift switching between the even speed stages or the odd speed stages, one of the even speed gear transmission mechanism 17 and the odd speed gear transmission mechanism 16 is in the neutral state during the gear train establishment switching. Of the even gear stage gear transmission mechanism 17 and the odd gear stage gear transmission mechanism 16, the clutch corresponding to the gear transmission mechanism for which the gear train is to be switched is temporarily released from the disconnected state for a short time. After disconnecting again as the connected state, the switching from the disconnected state to the connected state is completed after the end of the gear train establishment switching, so that as described with reference to FIGS. 8 (b) and 9 (b) above, The shift shock when the establishment switching is completed can be alleviated.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the present invention described in the claims. It is.

It is a figure which shows schematic structure of a twin clutch type gear transmission. It is a longitudinal cross-sectional view of a twin clutch apparatus. FIG. 3 is an enlarged view of a main part of FIG. 2. FIG. 4 is a cross-sectional view taken along line 4-4 of FIG. It is a notch perspective view of a 1st clutch outer. FIG. 6 is an enlarged sectional view taken along line 6-6 of FIG. It is a figure which contrasts and shows the rotation position of a cam shaft, and the amount of displacement of a lifter. It is a figure which shows the speed change characteristic at the time of upshifting. It is a figure which shows the speed change characteristic at the time of downshift.

Explanation of symbols

15 ... Twin clutch device 34 ... first clutch 35 ... second clutch 36 ... first clutch outer 36a ... cylindrical portion 36b ... annular plate portion 37 ... second clutch outer 44... Clutch disk 61... Clutch disk engagement groove 62... Clutch outer engagement groove 63.

Claims (4)

  A multi-plate first clutch (34) having a cylindrical portion (36a) and having a first clutch outer (36) that rotates by power transmission from a power source, and a second clutch that rotates together with the first clutch outer (36) In a twin clutch device having an outer (37) and a multi-plate second clutch (35) arranged coaxially with the first clutch (34), it is arranged radially outward of the second clutch (35). The first clutch outer (36) is formed by integrally connecting an annular plate portion (36b) to one end of the cylindrical portion (36a). The cylindrical portion (36a) includes a first clutch (34). A plurality of clutch disk engaging grooves (61) for engaging the outer periphery of the plurality of clutch disks (44) in a relatively non-rotatable manner and the outer periphery of the second clutch outer (37). Twin clutch device, characterized in that the engagement for the clutch discs as occupied engage groove (61) engaging a plurality of clutch outer disposed between groove and (62) are provided respectively.   The second clutch outer (37) is disposed at a position where the first clutch inner (43) included in the first clutch (34) is sandwiched between the annular plate portion (36b) and the second clutch outer (37). The twin clutch device according to claim 1, wherein a retaining ring (63) that comes into contact with and engages with an outer periphery from the axial direction is attached to the cylindrical portion (36a) of the first clutch outer (36). .   3. The twin clutch device according to claim 1, wherein axial lengths of the clutch disk engaging groove (61) and the latch outer engaging groove (62) are set different from each other.   The clutch disk engaging groove (61) and the latch outer engaging groove (62) open in the circumferential direction while opening to the other end of the cylindrical part (36a) on the side opposite to the annular plate part (36b). The twin clutch device according to any one of claims 1 to 3, wherein the twin clutch device is provided in the cylindrical portion (36a) at equal intervals.

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