JP2008057645A - Transmission clutch device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a transmission clutch device comprising a hydraulic clutch having a hydraulic chamber which faces one face of a clutch piston movable along the rotation axial lines of an input member and an output member, and a canceller chamber which faces the other face of the clutch piston for producing hydraulic pressure to counterbalance an increase of hydraulic pressure in the hydraulic chamber, induced by centrifugal force corresponding to the rotation of at least one of the input member and the output member, the hydraulic clutch being provided between a gear shift mechanism having a main shaft joined to the output member and an engine, having simple construction for supplying operation oil to the hydraulic chamber and the canceller chamber while reducing the number of components. <P>SOLUTION: In the transmission clutch device, an oil supply passage 78 communicating with the hydraulic chamber 56 is coaxially provided and a throttle part 82 interposed between a communication passage 81 communicating with the canceller chamber 62 and the oil supply passage 78 is provided in the main shaft 16. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention includes a hydraulic chamber that faces one surface of a clutch piston movable in a direction along the rotation axis of the input member and the output member, and a centrifugal force according to rotation of at least one of the input member and the output member. A gear transmission mechanism having a main shaft coupled to the output member, a hydraulic clutch having a canceller chamber facing the other surface of the clutch piston to generate a hydraulic pressure that cancels the induced hydraulic pressure increase in the hydraulic chamber; The present invention relates to a shift clutch device provided between engines.

A shift clutch device in which one surface of a clutch piston of a pair of hydraulic clutches arranged coaxially faces a hydraulic chamber and the other surface of both clutch pistons faces a canceller chamber is already known from Patent Document 1, for example. ing.
JP 2005-133937 A

  However, in the speed change clutch device disclosed in Patent Document 1, a distribution sleeve having an oil passage for distributing hydraulic oil to the hydraulic chambers of the hydraulic clutches and the canceller chambers of the hydraulic clutches on the outer periphery includes the clutch and the clutch. It is arranged between the main shafts, and the number of parts increases and the hydraulic oil supply structure is complicated.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a shift clutch device that can supply hydraulic oil to a hydraulic chamber and a canceller chamber with a simple structure that can reduce the number of parts. And

  In order to achieve the above object, the invention according to claim 1 is directed to a hydraulic chamber that faces one surface of a clutch piston that is movable in a direction along the rotation axis of the input member and the output member, and the input member and the output member. A hydraulic clutch having a canceller chamber facing the other surface of the clutch piston so as to generate a hydraulic pressure that cancels an increase in the hydraulic pressure in the hydraulic chamber induced by a centrifugal force according to at least one rotation; A gear transmission mechanism having a main shaft coupled to the engine and a clutch device for transmission provided between the engines, wherein the main shaft is coaxially provided with an oil supply passage that communicates with the hydraulic chamber, and a communication passage that communicates with the canceller chamber; A throttle part interposed between the oil supply passages is provided.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect of the present invention, an escape passage that leads to a communication passage that connects the throttle portion and the canceller chamber is provided in the main shaft. .

  Furthermore, in the invention according to claim 3, the hydraulic chamber that faces one surface of the clutch piston movable in the direction along the rotation axis of the input member and the output member, and at least one of the input member and the output member rotate. First and second hydraulic clutches each having a canceller chamber that faces the other surface of the clutch piston so as to generate a hydraulic pressure that cancels an increase in hydraulic pressure in the hydraulic chamber induced by a corresponding centrifugal force. A gear transmission mechanism having coaxial first and second main shafts that are individually coupled to the output member and a shift clutch device provided between the engines, and a first main shaft coupled to the output member of the first hydraulic clutch The second main shaft that passes coaxially and rotatably is covered by a second hydraulic clutch that covers the first hydraulic clutch. And an inner cylinder forming a second oil supply passage communicating with the hydraulic chamber of the second hydraulic clutch, and a first oil supply passage communicating with the hydraulic chamber of the first hydraulic clutch in the second main shaft. Two outer cylinders are formed between the inner cylinder and the inner circumference of the second main shaft. The outer cylinder is formed between the inner cylinder and a lubricating oil supply passage for supplying lubricating oil to a gear constituting a part of the gear transmission mechanism. A throttle passage inserted between the second hydraulic clutch and the communication path leading to the canceller chamber of the second hydraulic clutch and the second oil supply path is provided in the second main shaft, and the lubricant oil supply path is connected to the first hydraulic clutch. It is connected to the canceller room.

  According to the first aspect of the present invention, a part of the hydraulic oil flowing through the oil supply passage to be supplied to the hydraulic chamber is led to the canceller chamber via the throttle portion, and the throttle portion is provided on the main shaft. Therefore, the hydraulic oil and the canceller chamber can be supplied to the hydraulic chamber and the canceller chamber with a simple structure in which the dedicated parts for guiding the hydraulic oil to the canceller chamber are not required and the number of parts is reduced.

  According to the second aspect of the present invention, when the clutch piston is not operated, the hydraulic oil can be quickly discharged to the outside. Therefore, it is possible to avoid the retention of low temperature and high viscosity hydraulic oil around the hydraulic clutch immediately after the engine is started or in a low temperature environment, and to quickly supply hydraulic oil to the hydraulic chamber when the clutch piston is operated. It is possible to improve the disconnection / engagement controllability of the hydraulic clutch.

  According to the third aspect of the present invention, part of the hydraulic oil flowing through the oil supply passage to be supplied to the hydraulic chamber of the second hydraulic clutch is guided to the canceller chamber via the throttle portion. In the canceller chamber of the first hydraulic clutch, there is a lubricating oil supply passage formed between the outer cylinder and the second main shaft that forms an oil supply passage for supplying hydraulic oil to the hydraulic chamber of the first hydraulic clutch with the inner cylinder. Since the hydraulic oil is supplied, the hydraulic pressures of the first and second hydraulic clutches can be reduced with a simple structure that eliminates the need for a dedicated part for guiding the hydraulic oil to the canceller chambers of the first and second hydraulic clutches and reduces the number of parts. Hydraulic oil can be supplied to the chamber and the canceller chamber.

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

  1 to 3 show a first embodiment of the present invention. FIG. 1 is a diagram showing a simplified basic configuration of a power unit, FIG. 2 is a longitudinal sectional view showing a part of a transmission, and FIG. FIG. 3 is an enlarged view of main parts of FIG. 2.

  First, in FIG. 1, a power unit P mounted on a motorcycle, for example, includes an engine E that is, for example, two cylinders, and a transmission M that shifts the output of the engine E and transmits the output to a rear wheel (not shown). The transmission M is provided between a gear transmission mechanism 7 having a gear train of a plurality of shift stages that can be selectively established, for example, first to fifth gear trains G1 to G5, and the engine E and the gear transmission mechanism 7. And a clutch device 8.

  In addition to FIG. 2, the rotational power from the crankshaft 9 (see FIG. 1) provided in the engine E is input to the clutch device 8 via the primary reduction device 11 and the damper springs 12. Further, transmission of power transmitted from the crankshaft 9 via the primary reduction gear 11 and damper springs 12 to the gear transmission 7 and interruption of transmission are switched by the clutch device 8.

  The crankcase 14 provided in the engine body 10 is disposed in the middle portion between the right and left walls 14a and 14b, and the right and left walls 14a and 14b, which are positioned on the right and left sides with the motorcycle facing forward in the traveling direction. The gear transmission mechanism 7 is accommodated in the crankcase 14 between the left side wall 14b and the intermediate wall 14c.

  The gear transmission mechanism 7 includes a cylindrical first main shaft 15 having an axis parallel to the crankshaft 9 and a first main shaft 15 that coaxially penetrates the first main shaft 15 to allow relative rotation while maintaining a constant axial relative position. Two main shafts 16 and a counter shaft 17 having an axis parallel to the first and second main shafts 15 and 16, and these shafts 15 to 17 are rotatably supported by the crankcase 14.

  The second main shaft 16 has one end projecting outward from the right side wall 14a of the crankcase 14 and the other end projecting outward from the left side wall 14b. The wall 14c and the left side wall 14b are rotatably penetrated. A transmission cylinder shaft 18 that is coaxially coupled to the first main shaft 15 and is relatively non-rotatable and surrounds the second main shaft 16 coaxially passes through the right side wall 14a of the crankcase 14 so as to be rotatable. 18 and the right side wall 14a, a ball bearing 19 is interposed between the transmission cylinder shaft 18 and the second main shaft 16, and a needle bearing 20 is interposed between the left side wall 14b and the second main shaft 16. A bearing 21 is interposed. The first main shaft 15 passes through the intermediate wall 14c of the crankcase 14 in a rotatable manner, and a ball bearing 22 is interposed between the intermediate wall 14c and the first main shaft 15, and the first and second main shafts 15, Needle bearings 23 are interposed between 16.

  One end of the countershaft 17 is rotatably supported on the intermediate wall 14c of the crankcase 14 via a ball bearing 24, and the other end of the countershaft 17 passes through the left side wall 14b of the crankcase 14 so as to be rotatable. A ball bearing 25 is interposed between the left side wall 14 b and the counter shaft 17.

  Referring also to FIG. 3, the clutch device 8 includes a multi-plate first hydraulic clutch 28 that switches between transmission and interruption of power transmitted from the primary reduction gear 11 to the first main shaft 15, and the primary And a multi-plate second hydraulic clutch 29 that switches between transmission and interruption of power transmitted from the reduction gear 11 to the second main shaft 16.

  The primary reduction gear 11 includes a drive gear 30 provided on the crankshaft 9 and a driven gear 31 that meshes with the drive gear 30. The driven gear 31 surrounds the first main shaft 15 coaxially and is first. A cylindrical first boss 32 coupled to the main shaft 15 so as not to rotate relative to the main shaft 15 is supported via a roller bearing 33 so as to be relatively rotatable.

  The first and second clutches 28 and 29 are provided with a common input member 34, and this input member 34 is disposed adjacent to the outer side of the primary reduction gear 11 in the direction along the axis of the second main shaft 16. An annular plate portion 34a, a cylindrical inner cylinder portion 34b whose base end is connected to the inner peripheral side of the annular plate portion 34a on the opposite side to the primary reduction gear 11 at a right angle and integrally therewith, and the inner cylinder portion 34b Is formed of an outer cylindrical portion 34c whose base end is connected to the outer peripheral side of the annular plate portion 34a at a right angle and integrally therewith. Connection bosses 34d extending in the opposite direction to the inner cylinder part 34b and the outer cylinder part 34c are integrally provided at a plurality of locations in the circumferential direction of the annular plate part 34a of the input member 34, and these connection bosses are provided. 34d are extended through a long hole 35 provided in the driven gear 31 so as to extend long in the circumferential direction. Further, a holding plate 36 facing the driven gear 31 on the side opposite to the input member 34 is in contact with the connecting boss 34d, and the holding plate 36 is connected to the connecting boss 34d by rivets 37 passing through the connecting bosses 34d. Bonded to the end face. In addition, a leaf spring 38 is provided between the holding plate 36 and the driven gear 31 to exert a spring force that brings the driven gear 31 into contact with the annular plate portion 34 a of the input member 34.

  The driven gear 31 is provided with holding holes 39 extending in the circumferential direction at a plurality of positions shifted from the long holes 35 in the circumferential direction. The holding gears 39 and the input are provided in the holding holes 39. The damper spring 12 is accommodated and held so as to be interposed between the member 34 and the holding plate 36.

  The first hydraulic clutch 28 includes an inner cylindrical portion 34b of the input member 34 described above and a first cylindrical portion 40a that coaxially surrounds the inner cylindrical portion 34b, and is fixed to the first boss 32 so as to be first. A first output member 40 connected to the main shaft 15 so as not to rotate relative to the main shaft 15, a plurality of first clutch disks 41 engaged with the first cylindrical portion 40a so as not to rotate relative to each other, and the inner cylinder of the input member 34 A plurality of first clutch plates 42 that are engaged with the portion 34b in a relatively non-rotatable manner and alternately overlapped with the first clutch disks 41, and the first clutch disks 41 that are alternately overlapped with each other. And the first clutch plates 42... And the first clutch arranged alternately and overlapped with the annular first pressure receiving plates 43 facing the first clutch plates 42 from the annular plate portion 34a side. A first clutch piston 44 disposed on the open end side of the input member 34 having an annular first pressing plate portion 44a opposed to the annular plate portion 34a from the opposite side to the annular plate portion 34a; A first clutch spring 45 that exerts a spring force that urges 44 a toward the side that separates the first pressure receiving plate 43 from the first pressure receiving plate 43.

  The inner peripheral portion of the first clutch piston 44 having an annular first pressing plate portion 44a on the outer periphery is in fluid-tight sliding contact with the outer periphery of the first boss 32, and the first output member 40 includes the first output member 40. One end of the first cylindrical portion 40a is integrally connected to the outer periphery of the dish-shaped connecting plate portion 40b that is welded to the boss 32 and is opposed to the first clutch piston 44 from the outside. The outer periphery of the first pressing plate portion 44a of the first clutch piston 44 is fitted in a liquid-tight and slidable manner on the inner surface of the outer peripheral portion of the connecting plate portion 40b. Thus, a first hydraulic chamber 46 is formed between the first clutch piston 44 and the first output member 40, and the first clutch spring 45 is arranged on the side that contracts the volume of the first hydraulic chamber 46. Is provided between the first retainer 47 and the first clutch piston 44 mounted on the outer periphery of the first boss 32. A retaining ring 48 that contacts the outer periphery of the first pressure receiving plate 43 from the side opposite to the first pressing plate portion 44a is attached to the inner surface near the open end of the first cylindrical portion 40a.

  In such a first hydraulic clutch 28, the first clutch disks 41... And the first clutch alternately overlapped between the first pressing plate portion 44 a and the first pressure receiving plate 43 as the hydraulic pressure in the first hydraulic chamber 46 increases. The plates 42 are clamped and frictionally engaged, and power is transmitted from the inner cylindrical portion 34b of the input member 34 to the first output member 40. Power from the crankshaft 9 is transmitted from the first boss 32. It is transmitted to the first main shaft 15 via the cylindrical shaft 18.

  The second hydraulic clutch 29 has an outer cylindrical portion 34c of the input member 34 and a second cylindrical portion 50a that coaxially surrounds the first cylindrical portion 40a of the first hydraulic clutch 28 inside the outer cylindrical portion 34c. A second output member 50 that is connected to the second main shaft 16 so as not to rotate relative to the second main shaft 16, a plurality of second clutch disks 51 that are engaged with the outer cylinder portion 34c so as not to rotate relative to each other, and a second cylindrical portion. A plurality of second clutch plates 52... That are alternately engaged with the second clutch disks 51 and alternately overlapped with the second clutch disks 51. On the second clutch plates 52... And the second clutch plates 52, which are arranged alternately and overlapped with the annular second pressure receiving plates 53 facing the second clutch plates 52. A second clutch piston 54 having an annular second pressing plate portion 54a facing from the opposite side to the annular plate portion 34a, and a spring force that urges the second pressing plate portion 54a toward the side separating the second pressing plate portion 54a from the second pressure receiving plate 53. And a second clutch spring 55 that exhibits the following.

  A cylindrical second boss 59 that coaxially surrounds the second main shaft 16 is coupled to one end of the second main shaft 16 so as not to be relatively rotatable. The second output member 50 is connected to the first hydraulic clutch 28. One end of the second cylindrical portion 50a is integrated with the outer periphery of the dish-shaped connecting plate portion 50b that faces the connecting plate portion 40b of the first output member 40 from the outside and is welded to the second boss 59 at the inner peripheral portion. It is formed by being connected in series. Further, the inner peripheral portion of the second clutch piston 54 that has an annular second pressing plate portion 54 a on the outer periphery and faces the connecting plate portion 50 b of the second output member 50 from the outside is disposed on the outer periphery of the second boss 59. A second clutch piston 54 that is in close sliding contact and has a larger diameter than the first clutch piston 44 of the first hydraulic clutch 28 is arranged so as to be aligned with the first clutch piston 44 in the axial direction.

  Further, the second clutch piston 54 is formed in a dish-like shape with a third cylindrical portion 60a that fits the outer periphery of the second pressing plate portion 54a in a liquid-tight and slidable manner on the outer periphery, and is formed in a dish shape. The inner periphery of the case member 60 forming the second hydraulic chamber 56 is fixed to the second boss 59 in a liquid-tight manner. The second clutch spring 55 urges the second clutch piston 54 toward the side that contracts the volume of the second hydraulic chamber 56, and the second retainer 57 is attached to the connecting plate portion 50 b of the second output member 50. And between the second clutch piston 54. A retaining ring 58 that contacts the outer periphery of the second pressure receiving plate 53 from the side opposite to the second pressing plate portion 54a is attached to the inner surface near the open end of the second cylindrical portion 50a.

  In the second hydraulic clutch 29, the second clutch disks 51... And the second clutch alternately overlapped between the second pressing plate portion 54 a and the second pressure receiving plate 53 in accordance with the increase in the hydraulic pressure in the second hydraulic chamber 56. The plates 52 are clamped and frictionally engaged, and power is transmitted from the outer cylindrical portion 34c of the input member 34 to the second output member 50. Power from the crankshaft 9 is transmitted from the second boss 59 to the second output member 50. 2 is transmitted to the main shaft 16.

  Incidentally, in the first hydraulic clutch 28, a first canceller chamber 61 that faces the other surface of the first clutch piston 44 with one surface facing the first hydraulic chamber 46 is provided between the first retainer 47 and the first clutch piston 44. The first clutch spring 45 is accommodated in the first canceller chamber 61. Thus, by introducing the hydraulic oil into the first canceller chamber 61, the inside of the first hydraulic chamber 46 induced by the centrifugal force according to the rotation of at least one of the input member 34 and the first output member 40. Oil pressure that cancels out the increase in oil pressure is generated in the first canceller chamber 61.

  Further, in the second hydraulic clutch 29, a second canceller chamber 62 that faces the other surface of the second clutch piston 54 with one surface facing the second hydraulic chamber 56 is provided between the second output member 50 and the second clutch piston 54. The second clutch spring 55 is accommodated in the second canceller chamber 62. Thus, by introducing the hydraulic oil into the second canceller chamber 62, the inside of the second hydraulic chamber 56 induced by the centrifugal force corresponding to the rotation of at least one of the input member 34 and the second output member 50. Oil pressure that cancels out the increase in oil pressure is generated in the second canceller chamber 62.

  Referring again to FIG. 2, the left side wall 14b of the crankcase 14 is covered with an engine cover 63, and a passage hole 65 having an end wall 64 at the inner end is formed in the engine cover 63 in the first and second mains. It is provided coaxially with the shafts 15 and 16, and the outer end of the passage hole 65 is liquid-tightly closed with a cap 66.

  A wall member 67 is fitted in the passage hole 65 in a liquid-tight manner. A first hydraulic oil supply chamber 68 is formed between the wall member 67 and the end wall 64, and the wall member 67 and the cap 66 are formed. A second hydraulic oil supply chamber 69 is formed between them. In addition, the second main shaft 16 is coaxially provided with a bottomed center hole 70 having a wall portion 16a (see FIG. 3) on one end side and opening the other end side. The other end portion of the inner cylinder 71 that is disposed in the vicinity of the wall portion 16a and is coaxially inserted into the center hole 70 penetrates the end wall 64 and is held in a liquid-tight manner by the wall member 67. An annular seal member 72 (see FIG. 3) is interposed between the one end and the inner surface of the center hole 70. Further, an annular seal member 74 is inserted between one end portion of the outer cylinder 73 that is coaxially inserted into the center hole 70 so as to extend to the vicinity of one end portion of the inner cylinder 71 and coaxially surrounds the inner cylinder 71 and the inner surface of the center hole 70. (See FIG. 3) is interposed, and the other end of the outer cylinder 73 penetrates the left side wall 14b of the crankcase 14 in a liquid-tight manner and is fitted and held in the end wall 64 of the passage hole 65 in a liquid-tight manner. .

  Referring to FIG. 3, a plurality of first communication passages 75 that communicate with the first hydraulic chamber 46 of the first hydraulic clutch 28 are provided radially across the first boss 32, the transmission cylinder shaft 18, and the second main shaft 16. An annular first oil supply passage 76 is formed between the inner cylinder 71 and the outer cylinder 73 so that the first communication passages 75... Communicate with the first hydraulic oil supply chamber 68. Further, a plurality of second communication passages 77 that communicate with the second hydraulic chamber 56 of the second hydraulic clutch 29 are provided radially on the second boss 59, and these second communication passages 77 are supplied with the second hydraulic oil. A second hydraulic passage 78 communicating with the chamber 69 is formed in the inner cylinder 71 and the inner end of the center hole 70.

  That is, in the second main shaft 16, first and second oil supply for individually applying hydraulic pressure to the first and second clutch pistons 44 and 54 of the first and second hydraulic clutches 28 and 29 in the clutch device 8 are provided. The passages 76 and 78 are formed concentrically so that hydraulic oil can be supplied from the other end side of the second main shaft 16.

  One end portion of the second main shaft 16 is provided with a passage hole 79 having the wall portion 16a interposed between the second main shaft 16 and the center hole 70, and an opening end of the passage hole 79 opposite to the wall member 16a is The lid member 80 is closed in an oil-tight manner. In addition, the second boss 59 and the second main shaft 16 of the second hydraulic clutch 29 are provided with a third communication path 81 for communicating the second canceller chamber 62 between the wall member 16a and the lid member 80, The wall portion 16 a of the second main shaft 16 is coaxially provided with a throttle portion 82 interposed between the second oil supply chamber 78 and the third communication passage 81. In other words, the second oil supply passage 78 communicates with the third communication passage 81 communicating with the second canceller chamber 62 via the throttle portion 82.

  An annular lubricating oil supply passage 84 is formed between the inner periphery of the center hole 70 in the second main shaft 16 and the outer periphery of the outer cylinder 73, and the lubricating oil supply passage 84 is formed in the first hydraulic clutch 28. The first boss 32 and the fourth main passage 15 are connected to the first canceller chamber 61 via a fourth communication passage 83.

  Incidentally, the second and fourth speed gear trains G2 and G4 of the gear transmission mechanism 7 are provided between the first main shaft 15 and the counter shaft 17, and the first, third and fifth speed gear trains G1, G3 and G5 are provided. Is provided between the second main shaft 16 and the counter shaft 17. The power output from the other end of the countershaft 17 protruding from the left side wall 14b of the crankcase 14 is transmitted to an output shaft (not shown) via the damper spring 85 and the secondary reduction gear 86.

  The second speed gear train G2 is supported on the counter shaft 17 so as to be rotatable relative to the second speed drive gear 88 provided integrally with the first main shaft 15 and meshes with the second speed drive gear 88. The fourth-speed gear train G4 includes a second-speed driven gear 89, and is supported by the fourth-speed drive gear 90 fixed to the first main shaft 15 and the counter shaft 17 so as to be relatively rotatable. And a fourth speed driven gear 91 meshing with the fourth speed driving gear 90.

  In addition, the countershaft 17 between the second and fourth speed driven gears 89 and 91 is engaged with either the second or fourth speed driven gear 89 or 91 and the second and fourth speed driven gears. The first shifter 92 is spline-coupled so that the state of engagement with any of the gears 89 and 91 can be switched, and the second and fourth speed driven gears 89 and 91 are moved by the axial movement of the first shifter 92. A state in which the counter shaft 17 is freely rotated (neutral state) and any one of the second and fourth speed driven gears 89 and 91 are coupled to the counter shaft 17 so as not to rotate relative to the second speed gear train. It is possible to switch between the state of establishing either G2 or the fourth speed gear train G4.

  The first speed gear train G1 is supported by the first speed drive gear 93 integrally provided on the second main shaft 16 and the counter shaft 17 so as to be relatively rotatable, and meshes with the first speed drive gear 93. The third-speed gear train G3 includes a first-speed driven gear 94, and a third-speed gear train G3 that is spline-coupled to the second main shaft 16 so as to be axially slidable and relatively non-rotatable. The third-speed driven gear 96 is rotatably supported by the countershaft 17 and meshed with the third-speed drive gear 95. The fifth-speed gear train G5 is relative to the second main shaft 16. A fifth-speed driving gear 97 that is rotatably supported, and a fifth-speed driven gear that is supported so as not to rotate relative to the countershaft 17 while being axially slidable and meshes with the fifth-speed driving gear 97. 98 and Et al made.

  The third-speed drive gear 95 can be switched between engagement and disengagement with the fifth-speed drive idle gear 97 that is rotatably supported on the second main shaft 16. The fifth-speed driven gear 98 is integrally provided with the spline-coupled second shifter 99, and the fifth-speed driven gear 98 is supported by the countershaft 17 so as to be relatively rotatable, respectively. The third shifter 100 that is spline-coupled to the countershaft 17 is integrally provided so as to be able to switch between the state in which it is engaged and the state in which it is not engaged with any of the first and third driven gears 94 and 96. .

  Thus, by moving the second and third shifters 99, 100 in the axial direction, the fifth speed drive gear 97 is freely rotated with respect to the second main shaft 16, and the first and third speed driven gears 94, A state in which 96 is freely rotated with respect to the countershaft 17 (neutral state), and a state in which the first speed driven gear 94 is coupled to the countershaft 17 so as not to be relatively rotatable to establish a first speed gear train G1. The third speed drive gear 95 is coupled to the second main shaft 16 so as not to be relatively rotatable, and the third speed driven gear 96 is coupled to the counter shaft 17 so as not to be relatively rotatable. Thus, a third speed gear train G3 is established. And a state in which the fifth speed drive gear 97 is coupled to the second main shaft 16 so as not to be relatively rotatable to establish a fifth speed gear train G5.

  Thus, the lubricating oil supply passage 76 has a third speed driving gear 95 and a fifth speed driving gear mounted on the second main shaft 16 among the gears 88 to 98 constituting the gear reduction mechanism 7. The lubricating oil is supplied to the 97 side, between the first and second main shafts 15 and 16, and between the second main shaft 16 and the transmission cylinder shaft 18. The lubricating oil supply passage 76 is connected to the second main shaft 16. And a plurality of passages 101 for guiding the oil to the third speed driving gear 95 and the fifth speed driving gear 97 side, and a plurality of passages for guiding the oil in the lubricating oil supply passage 76 to the first and second main shafts 15 and 16. And a plurality of passages 103 led between the second main shaft 16 and the transmission cylinder shaft 18 of the lubricating oil supply passage 76 are provided.

  Next, the operation of the first embodiment will be described. The clutch device 8 includes a first hydraulic clutch 28 and a second hydraulic clutch 29 that covers the first hydraulic clutch 28, and the first hydraulic clutch 28 has a first hydraulic clutch 28. A second main shaft 16 that passes through the first main shaft 15 coupled to the output member 40 coaxially and relatively rotatably is coupled to the second output member 50 of the second hydraulic clutch 29, and is provided in the second main shaft 16. The inner cylinder 71 that forms the second oil supply path 78 that communicates with the second hydraulic chamber 56 of the second hydraulic clutch 29 and the first oil supply path 76 that communicates with the first hydraulic chamber 46 of the first hydraulic clutch 28 include the inner cylinder. A lubricating oil supply passage 84 that is formed between the second main shaft 16 and the third and fifth drive gears 95 and 97 that form part of the gear transmission mechanism 7 and that forms part of the gear transmission mechanism 7. Formed during The outer cylinder 73 is inserted in a double cylindrical shape, and a throttle portion 82 interposed between the communication path 81 and the second oil supply path 78 communicating with the second canceller chamber 62 of the second hydraulic clutch 29 is provided in the second main shaft 16. Is provided.

  Therefore, a part of the hydraulic oil flowing through the second oil supply passage 78 to be supplied to the second hydraulic chamber 56 is guided to the second canceller chamber 62 through the throttle portion 82, and the throttle portion 82 is connected to the second main chamber 62. Since it is provided on the shaft 16, a dedicated structure for guiding the hydraulic oil to the second canceller chamber 62 is not required, and a simple structure with a reduced number of parts is provided, and the second hydraulic chamber 56 and the second canceller chamber 62 are provided. Hydraulic oil can be supplied.

  Moreover, since the lubricating oil supply passage 84 communicates with the first canceller chamber 61 of the first hydraulic clutch 28, a dedicated part for guiding the hydraulic oil to the first canceller chamber 61 of the first hydraulic clutch 28 is not required. Thus, 61 hydraulic oil can be supplied to the first hydraulic chamber 46 and the first canceller chamber of the first hydraulic clutch 28 with a simple structure with a reduced number of sensitive points.

  FIG. 4 shows a second embodiment of the present invention. Parts corresponding to those of the first embodiment of FIGS. 1 to 3 are designated by the same reference numerals and detailed description is omitted. .

  A lid member 104 having an escape passage 105 is fitted and fixed to a passage hole 79 provided at one end of the second main shaft 16 so that the wall portion 16a is interposed between the center hole 70 and the center hole 70. A third communication passage 81 provided on the second boss 59 and the second main shaft 16 of the second hydraulic clutch 29 and communicating the second canceller chamber 62 between the wall member 16a and the lid member 104 is the escape passage 105. You will communicate with.

  That is, the escape passage 105 that leads to the third communication passage 81 that connects the throttle portion 82 and the second canceller chamber 62 is provided in the lid member 104 that is fitted and fixed to the second main shaft 16.

  According to the second embodiment, when the second clutch piston 54 is not operated, the hydraulic oil can be quickly discharged to the outside. Accordingly, it is avoided that the hydraulic oil having a low temperature and high viscosity stays around the second hydraulic clutch 29 immediately after the engine E is started or in a low temperature environment, and the second hydraulic chamber 56 is operated when the second clutch piston 54 is operated. Oil can be supplied promptly, and the disengagement / contact controllability of the second hydraulic clutch 29 can be improved.

  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 simplifies and shows the basic composition of the power unit of 1st Example. It is a longitudinal cross-sectional view which shows a part of transmission. FIG. 3 is an enlarged view of a main part of FIG. 2. It is sectional drawing corresponding to FIG. 3 of 2nd Example.

Explanation of symbols

7 ... gear transmission mechanism 15 ... first main shaft 16 ... second main shaft 28,29 ... hydraulic clutch 34 ... input members 40, 50 ... output members 44, 54 ... Clutch pistons 46, 56 ... hydraulic chambers 61, 62 ... canceller chamber 71 ... inner cylinder 76 ... first oil supply passage 78 ... second oil supply passage 84 ... lubricating oil supply passage 95 97 ... Gear E ... Engine

Claims (3)

  A hydraulic chamber (56) that faces one surface of the clutch piston (54) movable in a direction along the rotation axis of the input member (34) and the output member (50), the input member (34), and the output member (50) ) Canceller chamber (facing the other surface of the clutch piston (54) to generate a hydraulic pressure that cancels an increase in hydraulic pressure in the hydraulic chamber (56) induced by centrifugal force in response to rotation of at least one of 62), a hydraulic clutch (29) having a main shaft (16) coupled to the output member (50) and a transmission clutch device provided between the engine (E). The main shaft (16) is coaxially provided with an oil supply passage (78) that leads to the hydraulic chamber (56) and communicates with the canceller chamber (62). Communication passage (81) and said oil supply passage (78) stop portion interposed between (82) the shifting clutch device, wherein a is provided.   The speed change according to claim 1, wherein an escape passage (105) communicating with the communication passage (81) connecting between the throttle portion (82) and the canceller chamber (62) is provided in the main shaft (16). Clutch device.   A hydraulic chamber (46, 56) for facing one surface of the clutch piston (44, 54) movable in a direction along the rotation axis of the input member (34) and the output member (40, 50), and the input member (34) And the clutch piston (44) to generate a hydraulic pressure that counteracts the increase in hydraulic pressure in the hydraulic chamber (46, 56) induced by centrifugal force in response to rotation of at least one of the output members (40, 50). , 54) have first and second hydraulic clutches (28, 29) each having a canceller chamber (61, 62) facing the other surface, and output members (40, 50) of the hydraulic clutches (28, 29). In the clutch device for transmission provided between the gear transmission mechanism (7) and the engine (E) having coaxial first and second main shafts (15, 16) individually coupled to each other) Thus, the second main shaft (16) passing through the first main shaft (15) coupled to the output member (40) of the first hydraulic clutch (28) coaxially and relatively rotatably is connected to the first hydraulic clutch ( 28) is coupled to the output member (50) of the second hydraulic clutch (29) covering the second main shaft (16), and is connected to the hydraulic chamber (56) of the second hydraulic clutch (29). A first oil supply passage (76) that communicates with the hydraulic chamber (46) of the first hydraulic clutch (28) is formed between the inner cylinder (71) that forms the oil supply passage (78) and the inner cylinder (71). In addition, a lubricating oil supply passage (84) for supplying lubricating oil to the gears (95, 97) constituting a part of the gear transmission mechanism (7) is formed between the inner periphery of the second main shaft (16). The outer cylinder (73) is inserted into a double cylinder, and the second hydraulic cylinder A throttle part (82) interposed between the communication path (81) leading to the canceller chamber (62) of the hose (29) and the second oil supply path (78) is provided in the second main shaft (16), and the lubricating oil supply The speed change clutch device, wherein the path (84) communicates with the canceller chamber (61) of the first hydraulic clutch (28).

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