JP2014190364A - Power transmission device of saddle ride type vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power transmission device of a saddle ride type vehicle which suppresses that free-running feeling occurs upon deceleration of a vehicle with a compact constitution capable of suppressing increase of the number of components, in the power transmission device of the saddle ride type vehicle which includes a belt type continuously variable transmission, a start clutch of a centrifugal type disposed between the belt type continuously variable transmission and a transmission shaft, a planetary gear mechanism disposed between the transmission shaft and a rear wheel and a mechanical transmission which contains the gear change clutch of centrifugal type which switches a gear range of the planetary gear mechanism, the number of rotation as connective state of a gear change clutch of the centrifugal type being set higher than the number of rotation as connective state of the start clutch.SOLUTION: The number of rotation as cut-off state of gear change clutch is set near the number of rotation as the cut-off state of the start clutch, or less than the number of rotation as the cut-off state of the start clutch.

Description

  The present invention relates to a belt type continuously variable transmission that transmits power from an engine so that its rotational speed can be steplessly changed, and a centrifugal starter provided between the belt type continuously variable transmission and a transmission shaft. A clutch, a planetary gear mechanism provided between the transmission shaft and the axle of the rear wheel, and a mechanical transmission including a centrifugal transmission clutch that switches a gear position of the planetary gear mechanism, and a connection state of the transmission clutch; The present invention relates to a power transmission device for a saddle-ride type vehicle in which the rotational speed is set higher than the rotational speed at which the start clutch is engaged.

  Such a power transmission device is already known from, for example, Patent Document 1, in which a clutch inner of a transmission clutch is coupled to a transmission shaft so as not to rotate relative to the transmission shaft, and the clutch outer can be rotated relative to the transmission shaft. The one-way clutch that allows the clutch outer to rotate in the same direction as the transmission shaft is provided between the fixed member and the rotational speed at which the speed change clutch is connected is higher than the rotational speed at which the start clutch is connected. Is also set high. A ring gear of the planetary gear mechanism is continuously connected to the transmission shaft, a planet carrier is linked and connected to the rear wheel axle, and a sun gear is linked and connected to the clutch outer. For this reason, when the speed of the transmission shaft is low and the transmission clutch is in the disconnected state, the rotational power of the transmission shaft is transmitted to the axle side of the rear wheel via the planetary gear mechanism, and the transmission clutch is connected at a high speed. When in the state, the transmission shaft and the planetary gear mechanism rotate as a unit, and the rotation of the transmission shaft is transmitted to the rear wheel axle side at the same speed.

JP 2012-180916 A

  However, in the conventional configuration in which the gear ratio of the mechanical transmission is switched between the planetary gear mechanism and the transmission clutch as disclosed in Patent Document 1, the number of rotations on the connection side of the starting clutch and the transmission clutch is set as follows. As for the number of revolutions on the shut-off side, the speed at which the speed change clutch is in the shut-off state is set higher than the speed at which the start clutch is in the shut-off state, according to the speed difference on the connection side. . In this case, when power is transmitted from the axle side of the rear wheel as the vehicle decelerates, the transmission shaft and the planetary gear mechanism rotate together at the same speed while the speed change clutch is in the connected state. The power transmitted from the planetary gear mechanism to the transmission shaft is made to the engine side via the connected start clutch and belt type continuously variable transmission, so the engine brake is applied, but the rotational speed of the transmission shaft eventually decreases. When the speed change clutch is disengaged, the speed increase of the sun gear of the planetary gear mechanism is allowed, the power from the rear wheel side is absorbed by the speed increase of the sun gear via the planet carrier, and the start clutch is There was a problem that the engine brake did not work sufficiently and the feeling of idling occurred until the vehicle was shut off.

  The present invention has been made in view of such circumstances, and a power transmission device for a saddle-ride type vehicle that is capable of suppressing the occurrence of an idling feeling during vehicle deceleration with a compact configuration that suppresses an increase in the number of parts. The purpose is to provide.

  In order to achieve the above object, the present invention provides a belt-type continuously variable transmission that transmits power from an engine in such a manner that its rotational speed can be continuously changed, and the belt-type continuously variable transmission and transmission shaft. A centrifugal starting clutch, a planetary gear mechanism provided between the transmission shaft and the rear axle, and a mechanical transmission including a centrifugal transmission clutch for switching the speed of the planetary gear mechanism. In the power transmission device for a saddle-ride type vehicle in which the rotational speed at which the transmission clutch is connected is set higher than the rotational speed at which the start clutch is connected, the rotational speed at which the transmission clutch is disconnected is The first feature is that the speed is set near or below the number of revolutions at which the starting clutch is disengaged.

  According to the present invention, in addition to the configuration of the first feature, the difference between the rotational speed at which the shift clutch is disengaged and the rotational speed at which the start clutch is disengaged is a vehicle speed difference caused by the rotational speed difference. Is set to be 25 km / h or less.

  In addition to the configuration of the first or second feature, the present invention has a third feature that the transmission clutch includes a centrifugal weight and is configured as a trailing type.

  According to the present invention, in addition to any of the configurations of the first to third features, the start clutch and the shift clutch, each having a centrifugal weight, have at least the shape of the centrifugal clutch, the start clutch, and the shift clutch. The fourth feature is that they are configured differently.

  According to the present invention, in addition to any one of the first to fourth features, a clutch inner of the transmission clutch is connected to the transmission shaft so as not to rotate relative to the transmission shaft, and a clutch outer of the transmission clutch is relative to the transmission shaft. An intermediate shaft that is rotatably supported and is spaced from the transmission shaft in the longitudinal direction of the vehicle and has an axis parallel to the transmission shaft is rotatably supported by the transmission case, and is coaxial with the intermediate shaft. The planetary gear mechanism disposed in the ring includes a ring gear to which power from the transmission shaft is transmitted, a plurality of planetary gears meshed with the ring gear, and rotatably supporting the planetary gears on the rear wheel axle. A planetary carrier that is interlocked and coupled, and a sun gear that meshes with the plurality of planetary gears, and a power transmission gear that transmits the power of the clutch outer to the sun gear is a relative rotation to the sun gear. A fifth feature is that a one-way clutch, which is impossiblely connected and is arranged coaxially with the intermediate shaft, is provided between the clutch outer and the transmission case to allow rotation of the transmission shaft in the forward rotation direction. .

  According to the present invention, in addition to the configuration of the fifth feature, an outer tooth portion that meshes with a gear provided on the transmission shaft is formed on an outer periphery of a ring portion included in the ring gear, and an inner tooth portion meshed with the planetary gear. Is formed on the inner periphery of the ring portion.

  In the present invention, in addition to the configuration of the fifth or sixth feature, the ring gear and the power transmission gear are arranged side by side in the axial direction of the intermediate shaft, and when viewed from the axial direction of the intermediate shaft, A seventh feature is that a part of the shift clutch is disposed between the ring gear and the power transmission gear in the axial direction of the intermediate shaft so as to partially overlap the power transmission gear.

  According to the present invention, in addition to any of the configurations of the fifth to seventh features, a driven gear is provided on the axle, and meshes with the driven gear so as to transmit power from the planet carrier to the axle side. The output gear is disposed between the ring gear and the power transmission gear in the axial direction of the intermediate shaft while overlapping with a part of the transmission clutch when viewed from a direction orthogonal to the axis of the intermediate shaft. Eight features.

  In addition to any of the configurations of the fifth to seventh features, the present invention provides at least one central portion of the planetary gear mechanism and the power transmission gear between both end portions of the intermediate shaft and the transmission case. A ninth feature is that a first recess is provided to receive at least a part of at least one of the pair of intermediate shaft bearings.

  According to the present invention, in addition to any of the configurations of the fifth to ninth features, a hub of a wheel of the rear wheel is fixed to a protruding portion of the axle from the transmission case, and the hub and the rim are The rim and the hub are connected by a plurality of spokes so as to form a second recess opened on the transmission case side, and are interposed between the rear wheel side end of the transmission shaft and the transmission case. At least a part of the transmission shaft bearing is accommodated in the second recess on the center side in the vehicle width direction of the rear wheel with respect to the imaginary straight line connecting the end portions on the transmission case side of the hub and the rim. Is a tenth feature.

  In addition to any of the configurations of the fifth to tenth aspects of the present invention, the transmission case accommodates the belt-type continuously variable transmission and the starting clutch, and accommodates a recess in the side surface on the rear wheel side. The housing recess is formed so as to form a belt-type continuously variable transmission housing portion formed between the belt-type continuously variable transmission housing and the belt-type continuously variable transmission housing portion for housing the mechanical transmission. And a cover member that is fastened to the belt-type continuously variable transmission housing portion and has a bottom-shaped clutch outer that has an open end directed toward the belt-type continuously variable transmission housing portion side. The restriction member that is disposed in a manner and is configured to cooperate with the anti-rotation member supported on the outer surface side of the bottom portion of the clutch outer to constitute the one-way clutch enables the anti-rotation member to be engaged. From the side It is attached to the belt type continuously variable transmission housing portion, and the rotation preventing member and the regulating member are arranged on the cover member side from the fastening surface of the cover member and the belt type continuously variable transmission housing portion. Is an eleventh feature.

  According to the first aspect of the present invention, the rotational speed at which the shift clutch is engaged is set higher than the rotational speed at which the start clutch is engaged, and the rotational speed at which the shift clutch is disconnected is reduced. Because the speed is less than or equal to the number of revolutions, the transmission clutch is disengaged in advance of the starting clutch when the vehicle is decelerating while enabling power transmission fully utilizing both gear ratios before and after the gear change by the planetary gear mechanism. Thus, it is possible to suppress the feeling of idling when decelerating, and to sufficiently apply the engine brake until the start clutch is disengaged. In addition, it is not necessary to use a dedicated part such as a one-way clutch for engine braking, and the power transmission device can be made compact by avoiding an increase in the number of components, making the power transmission device suitable for saddle riding type vehicles. be able to.

  Further, according to the second feature of the present invention, the speed is reduced by bringing the speed at which the speed change clutch is in the disengaged state and the speed at which the start clutch is in the disengaged state close to each other so as to suppress the vehicle speed difference to 25 km / h or less. It is possible to effectively suppress the feeling of running at the time.

  According to the third aspect of the present invention, the speed change feeling can be made smooth by configuring the speed change clutch to be a trailing type, and the speed change clutch is in the disconnected state and connected. It is easy to increase the range of the rotational speed difference from the rotational speed, and it is possible to easily approach the rotational speed at which the starting clutch is disconnected only on the disconnected side.

  According to the fourth aspect of the present invention, by changing the shape of at least the centrifugal clutch of the start clutch and the shift clutch, the positions of the center of gravity of the centrifugal weights can be made different. In addition to making the number different, it is easy to set the rotational speed at which the shift clutch is disengaged to be equal to or lower than the rotational speed at which the start clutch is disengaged.

  According to the fifth aspect of the present invention, the transmission clutch is disposed coaxially with the transmission shaft that inputs the power from the engine to the mechanical transmission side, whereas the planetary gear mechanism is provided on the transmission shaft. In contrast, it is arranged at a distance in the longitudinal direction of the vehicle and coaxially with the intermediate shaft having an axis parallel to the transmission shaft, and the clutch outer of the speed change clutch is linked and connected to the sun gear of the planetary gear mechanism. The mechanical transmission is arranged in a direction along the axis of the transmission shaft as compared with a configuration in which the clutch and the planetary gear mechanism are displaced in the vehicle longitudinal direction, and the planetary gear mechanism and the transmission clutch are arranged coaxially with the transmission shaft. The power transmission device can be made compact, and it becomes easy to secure the bank angle of the vehicle by mounting the power transmission device on the saddle riding type vehicle, so that the power transmission device suitable for the saddle riding type vehicle can be obtained.

  According to the sixth aspect of the present invention, the power transmission is performed by the outer teeth and the inner teeth formed respectively on the outer periphery and the inner periphery of the ring portion included in the ring gear. The machine can be made compact in the axial direction.

  According to the seventh aspect of the present invention, a part of the speed change clutch is overlapped with the ring gear and the power transmission gear arranged in the axial direction of the intermediate shaft as viewed from the axial direction of the intermediate shaft. Therefore, the ring gear, speed change clutch, and power transmission gear are arranged compactly in the direction along the axis of the intermediate shaft, and the mechanical transmission is made compact in the direction along the axis of the intermediate shaft to increase the bank angle of the vehicle. It is possible to sufficiently ensure the distance between the transmission shaft and the intermediate shaft.

  According to the eighth aspect of the present invention, the output gear for transmitting the power from the planet carrier to the axle side overlaps with a part of the speed change clutch as viewed from the direction orthogonal to the axis of the intermediate shaft. Since it is arranged between the ring gear and the power transmission gear in the axial direction, the ring gear, the output gear, the transmission clutch and the power transmission gear are arranged more compactly in the direction along the axis of the intermediate shaft, and the machine in the direction along the axis of the intermediate shaft. The type transmission can be made more compact.

  According to the ninth feature of the present invention, the first recess is provided in the central portion of at least one of the planetary gear mechanism and the power transmission gear, and the pair of intermediate shafts are provided between both ends of the intermediate shaft and the transmission case. Since at least a part of at least one of the bearings is accommodated in the first recess, at least a part of at least one of the planetary gear mechanism and the power transmission gear is disposed in a space around at least one of the intermediate shaft bearings. The power transmission device can be made more compact and lighter in the axial direction of the intermediate shaft.

  According to the tenth feature of the present invention, the hub of the wheel of the rear wheel is fixed to the protruding portion of the axle from the transmission case, and the transmission is opened in the second recess formed in the wheel by opening to the transmission case side. At least a part of the transmission shaft bearing interposed between the rear wheel side end of the shaft and the transmission case is centered in the vehicle width direction of the rear wheel from a virtual straight line connecting between the transmission case side ends of the hub and the rim. Since the transmission shaft can be arranged closer to the rear wheel side, the bank angle can be easily avoided by avoiding the enlargement of the power transmission device on the outer side in the vehicle width direction. Can be secured.

  Further according to the eleventh feature of the present invention, the transmission case has a mechanical speed change between the belt-type continuously variable transmission accommodating portion for accommodating the belt-type continuously variable transmission and the belt-type continuously variable transmission accommodating portion. A cover member that forms a mechanical transmission housing chamber for housing the machine and is fastened to the belt type continuously variable transmission housing portion, and a rotation preventing member supported by the clutch outer, and a rotational direction of the clutch outer. Since the regulating member configured to cooperate with the non-rotating member for the regulating one-way clutch is disposed closer to the cover member than the fastening surface of the cover member and the belt-type continuously variable transmission housing portion, the belt-type continuously variable transmission In a state where the cover member is removed from the machine housing portion, the rotation preventing member and the regulating member are disposed outside the fastening surface, and assembly is facilitated. In addition, the clutch outer formed in a bowl shape having a bottom portion is disposed with its open end facing the belt-type continuously variable transmission housing portion side, and a rotation preventing member is supported on the outer surface side of the bottom portion of the clutch outer Therefore, when assembling the one-way clutch, the assembling work can be performed while visually checking the rotation preventing member and the regulating member, and the assemblability is further improved.

It is a partially cutaway plan view of the power unit of the first embodiment. It is a principal part enlarged view of FIG. FIG. 3 is a view taken along line 3-3 in FIG. 2. FIG. 4 is a cross-sectional view taken along line 4-4 of FIG. FIG. 5 is a sectional view taken along line 5-5 of FIG. It is a figure which compares and shows the connection and interruption | blocking rotation speed of a starting clutch and a transmission clutch. It is a figure for demonstrating the rotation speed change of the ring gear at the time of vehicle deceleration, a planet carrier, and a sun gear. It is sectional drawing corresponding to FIG. 2 of 2nd Embodiment. It is sectional drawing corresponding to FIG. 2 of 3rd Embodiment.

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

  The first embodiment of the present invention will be described with reference to FIGS. 1 to 7. First, in FIG. 1, the power unit P is mounted on a saddle-ride type vehicle, for example, a motorcycle, and is a power source. It comprises a certain air-cooled engine E and a power transmission device T that transmits power from the engine E to the rear wheels WR. The power transmission device T includes a belt-type continuously variable transmission 13 that transmits rotational power of a crankshaft 12 rotatably supported by a crankcase 11 of an engine E so that the rotational speed of the crankshaft 12 is continuously variable, and a transmission. A centrifugal start clutch 15 interposed between a shaft 14 and the belt-type continuously variable transmission 13, and a mechanical transmission 17A provided between the transmission shaft 14 and the axle 16 of the rear wheel WR; The mechanical transmission 17A includes a planetary gear mechanism 18 and a centrifugal transmission clutch 19 that switches the gear position of the planetary gear mechanism 18.

  The power transmission device T is connected to the crankcase 11 and extends rearward and is accommodated in a transmission case 20A disposed on the left side of the rear wheel WR. The transmission case 20A is the belt type Between the belt-type continuously variable transmission housing portion 23 that forms a belt-type continuously variable transmission housing chamber 21 that houses the continuously variable transmission 13 and the starting clutch 15, and the belt-type continuously variable transmission housing portion 23. A right-side cover member 24A fastened to the belt-type continuously variable transmission housing 23 so as to form a mechanical transmission housing chamber 22 for housing the mechanical transmission 17A.

  Referring to FIGS. 2 and 3 together, the belt-type continuously variable transmission accommodating portion 23 is connected to the crankcase 11 so as to be integrated with the case main body 25 and extends rearward, and covers the case main body 25 from the left side. And a left cover member 26 coupled to the case main body 25. An accommodation recess 27 is formed on the side surface of the belt-type continuously variable transmission housing portion 23 on the rear wheel WR side, that is, on the side surface of the rear portion of the case main body 25 on the rear wheel WR side, and the right cover member 24A Fastened to a fastening surface 28 formed on the case main body 25 so as to surround the open end of the housing recess 27 so as to cover the housing recess 27.

  The belt-type continuously variable transmission 13 is parallel to the crankshaft 12 and a drive pulley 30 provided at one end of the crankshaft 12 that enters the belt-type continuously variable transmission housing chamber 21 of the transmission case 20A. An endless V-belt 32 is wound around a driven pulley 31 that is rotatably supported by the transmission shaft 14 having a simple axis.

  The drive pulley 30 includes a fixed pulley half 33 fixed to the crankshaft 12 and a movable pulley half 34 that can be moved toward and away from the fixed pulley half 33. Is driven in the axial direction by a centrifugal force acting on a weight roller 36 disposed between the ramp plate 35 fixed to the crankshaft 12 and the movable pulley half 34.

  The driven pulley 31 surrounds the transmission shaft 14 coaxially and is fixed to a cylindrical inner cylinder 39 that is rotatably supported by the transmission shaft 14. A movable pulley half 38 that can be moved toward and away from the fixed pulley half 37 by being fixed to an outer cylinder 40 that coaxially surrounds the inner cylinder 39 so as to be capable of relative movement and relative rotation in the axial direction. The V belt 32 is wound between the fixed pulley half 37 and the movable pulley half 38. A torque cam mechanism 41 for applying an axial component force between the two pulley halves 37, 38 in accordance with the relative rotational phase difference between the movable pulley half 37 and the fixed pulley half 38 is provided with the inner cylinder 39 and the outer cylinder 39. The movable pulley half 38 provided between the cylinders 40 is elastically biased toward the fixed pulley half 37 by the coil spring 42.

  Referring also to FIG. 4, the starting clutch 15 is connected to the one end of the transmission shaft 14 and the inner part of the transmission shaft 14 so that the starting clutch 15 is connected in response to the engine speed exceeding a predetermined starting speed. A flange-shaped clutch outer 43 fixed to one end of the transmission shaft 14, a clutch inner 44 fixed to the inner cylinder 39, and a plurality of portions of the clutch inner 44. A centrifugal weight 45 that is pivotally supported through shafts 47, and each of the centrifugal weights 45, and clutch springs 46 that are provided between the clutch inners 44, are configured as a leading type. When the centrifugal force acting on each centrifugal weight 45... Exceeds the spring biasing force of each clutch spring 46. Is opened, and the tip of the centrifugal weight 45 is brought into contact with the inner periphery of the clutch outer 43 and frictionally engaged, whereby the inner cylinder 39, that is, the fixed pulley half 37, and the clutch outer 43, that is, the transmission shaft 14 are coupled. Connected. Such a leading type start clutch 15 operates in a direction in which the centrifugal weights 45... Engage with the clutch outer 43, so that clutch slip is small.

  The transmission shaft 14 to which the clutch outer 43 of the starting clutch 15 is fixed at one end in the axial direction is a cylindrical first bearing housing 49 provided in the case main body 25 in the belt type continuously variable transmission housing portion 23. The other end of the transmission shaft 14 is rotatably supported by a bottomed cylindrical second bearing housing 50 that is provided integrally with the right cover member 24A.

  Between the first bearing housing 49 and the transmission shaft 14, an annular seal member 51 and a first transmission shaft bearing which is a first transmission shaft bearing are sequentially arranged from the belt-type continuously variable transmission housing chamber 21 side. A ball bearing 52 is interposed, and a second transmission shaft is provided between the second bearing housing 50 of the right cover member 24A and the end of the transmission shaft 14 on the rear wheel WR side, that is, the other end. A second transmission shaft ball bearing 53, which is a bearing for the vehicle, is interposed.

  The transmission case 20A is rotatably supported by an intermediate shaft 54A that is spaced from the transmission shaft 14 in the longitudinal direction of the vehicle. In this embodiment, the intermediate shaft 54A is It arrange | positions with respect to the power transmission shaft 14 back and downward of a vehicle front-back direction.

  The case main body 25 is integrally provided with a bottomed cylindrical third bearing housing 55 that rotatably supports one end portion of the intermediate shaft 54A, and the right cover member 24A has the other end of the intermediate shaft 54A. A fourth bearing housing 56 having a bottomed cylindrical shape that rotatably supports the portion is integrally provided. Between the one end of the intermediate shaft 54A and the third bearing housing 55, a first intermediate shaft ball bearing 57, which is a first intermediate shaft bearing, is interposed, and the other end of the intermediate shaft 54A and the fourth A second intermediate shaft ball bearing 58 which is a second intermediate shaft bearing is interposed between the bearing housings 56.

  The axle 16 of the rear wheel WR has an axis parallel to the transmission shaft 14 and the intermediate shaft 54A and is disposed rearward and upward in the vehicle front-rear direction of the intermediate shaft 54A. A bottomed cylindrical fifth bearing housing 59 that rotatably supports one end portion of the rear wheel WR is integrally provided, and the right cover member 24A has a cylindrical shape that allows an intermediate portion of the axle 16 to freely pass therethrough. The sixth bearing housing 60 is integrally provided.

  A first axle ball bearing 61 is interposed between the fifth bearing housing 59 and one end of the axle 16, and the mechanical transmission accommodating chamber 22 is interposed between the sixth bearing housing 60 and the axle 16. In order from the side, an annular seal member 62 and a second axle ball bearing 63 are interposed.

  The transmission clutch 19 is arranged coaxially with the transmission shaft 14 that inputs the power from the engine E to the mechanical transmission 17A side via the belt-type continuously variable transmission 13 and the starting clutch 15; The planetary gear mechanism 18 is disposed coaxially with the intermediate shaft 54 </ b> A, and a clutch outer 80 that is an output member of the transmission clutch 19 is connected to a sun gear 68 that is one of the components constituting the planetary gear mechanism 18. Interlocked and linked.

  The planetary gear mechanism 18 rotatably supports a ring gear 65 to which power from the transmission shaft 14 is transmitted, a plurality of planetary gears 66 meshed with the ring gear 65, and the planetary gears 66. A planetary carrier 67 that is linked to and connected to the axle 16 of the wheel WR, and a sun gear 68 that is rotatably supported by the intermediate shaft 54A and meshes with the plurality of planetary gears 66. A first power transmission gear 69A for transmitting the power of the outer 80 to the sun gear 68 is connected to the sun gear 68 so as not to be relatively rotatable and is disposed coaxially with the intermediate shaft 54A, and is supported by the intermediate shaft 54A so as to be relatively rotatable. Is done.

  The ring gear 65 having a ring portion 72 coaxial with the intermediate shaft 54A surrounds the intermediate shaft 54A at a position adjacent to the inner ring of the first intermediate shaft ball bearing 57 and is rotatable relative to the intermediate shaft 54A. An outer tooth portion 73 that is fixed to a cylindrical boss member 70 to be supported and meshes with a gear 75 </ b> A provided integrally with the transmission shaft 14 is formed on the outer periphery of the ring portion 72. Inner teeth 74 that mesh with the planetary gears 66 are formed around the circumference.

  Between the boss member 70 to which the ring gear 65 is fixed and the inner ring of the second intermediate shaft ball bearing 58, a transmission cylinder shaft 76 surrounding the intermediate shaft 54A rotates relative to the intermediate shaft 54A. The sun gear 68 is fixed to one end of the transmission cylinder shaft 76 so as to be supported freely. An output gear 77 surrounding the transmission cylinder shaft 76 is supported on the transmission cylinder shaft 76 so as to be relatively rotatable. The planetary carrier 67 is connected to the ring gear 65 in the axial direction. A driven gear 78 is provided on the axle 16 so as to be sandwiched between them and fixed to the output gear 77 and meshing with the output gear 77.

  Referring also to FIG. 5, the transmission clutch 19 uses the gear 75 </ b> A provided integrally with the transmission shaft 14 so as to mesh with the ring gear 65 of the planetary gear mechanism 18 as a first transmission shaft. A clutch inner 79 which is disposed between the ball bearing 52 and the transmission shaft 14 so as to be relatively non-rotatable, and a clutch outer 80 which is supported by the transmission shaft 14 so as to be relatively rotatable. The clutch inner 79 is provided with centrifugal weights 81 pivotally supported by shafts 48 through shafts 48, and the centrifugal weights 81 and clutch springs 82 provided between the clutch inners 79. Composed.

  In the transmission clutch 19, the centrifugal force acting on the centrifugal weights 81 in response to the rotation of the clutch inner 79 rotating in the direction indicated by the arrow together with the transmission shaft 14 exceeds the spring biasing force of the clutch springs 82. When the centrifugal weights 81 are frictionally engaged with the inner periphery of the clutch outer 80, the clutch outer 80 rotates together with the transmission shaft 14 in a connected state. In addition, the speed change clutch 19 is such that the centrifugal weights 81 contact the clutch outer 80 from the side close to the shaft 48 and contact the clutch outer 80 so that the centrifugal weights 81 lick. Compared to slipping.

  As shown in FIG. 6, the connection rotational speed at which the shift clutch 19 is switched from the disconnected state to the connected state is set higher than the connected rotational speed at which the starting clutch 15 is switched from the disconnected state to the connected state, and the starting clutch 19 is connected. The shut-off speed at which the shut-off state is changed from the state to the shut-off state is set to be equal to or less than the shut-off speed at which the starting clutch 15 is brought into the shut-off state from the connected state (equal in this embodiment).

  As described above, when the connecting rotational speeds of the start clutch 15 and the transmission clutch 19 are made different, and the shut-off speed of the shift clutch 19 is made equal to or lower than the shut-off speed of the start clutch 15, at least the centrifugal weight 45 in both the clutches 14 and 19 is used. , 81 may be made different from each other as shown in FIGS. 4 and 5, and the connection rotational speed and the cutoff rotational speed can be set by making the positions of the center of gravity of the centrifugal weights 45, 81 different. . It can also be adjusted by changing the spring load of the clutch springs 46 and 82.

  The clutch outer 80 of the transmission clutch 19 has a bottom portion 80a and is formed in a bowl shape, and its open end is disposed toward the belt-type continuously variable transmission housing portion 23 side. The inner periphery of the bottom 80 a of the clutch outer 80 is fixed to a cylindrical cylinder 84 that is supported by the transmission shaft 14 via a needle bearing 83 so as to be relatively rotatable. The first power transmission gear 69A meshing with the second power transmission gear 85 formed in the portion is relatively non-rotatable to the other end portion of the transmission cylinder shaft 76 that is rotatably supported by the intermediate shaft 54A. Connected. That is, the first power transmission gear 69A for transmitting the power of the clutch outer 80 in the transmission clutch 19 to the sun gear 68 is connected to the sun gear 68 so as not to be relatively rotatable, and is disposed coaxially with the intermediate shaft 54A. Become.

  The ring gear 65 and the first power transmission gear 69A are arranged side by side in the axial direction of the intermediate shaft 54A. When viewed from the axial direction of the intermediate shaft 54A, the ring gear 65 and the first power transmission gear 69A are connected to the ring gear 65 and the first power transmission gear 69A. A part of the speed change clutch 19 is disposed between the ring gear 65 and the first power transmission gear 69A in the axial direction of the intermediate shaft 54A so as to partially overlap.

  Moreover, an output gear 77 that meshes with the driven gear 78 of the axle 16 so as to transmit power from the planetary carrier 67 to the axle 16 side, as viewed from a direction perpendicular to the axis of the intermediate shaft 54A. It is arranged between the ring gear 65 and the first power transmission gear 69A in the axial direction of the intermediate shaft 54A while overlapping with a part of the clutch 19.

  Further, at least one central portion of the planetary gear mechanism 18 and the first power transmission gear 69A is provided with first and second intermediate shaft ball bearings 57 provided between both end portions of the intermediate shaft 54A and the transmission case 20A. , 58 is provided with a first recess that accommodates at least a part of the ring gear 65. In this embodiment, a first intermediate shaft ball bearing 57 is provided at the center of the ring gear 65 of the planetary gear mechanism 18. Is formed, and a first recess 87 for receiving a part of the second intermediate shaft ball bearing 58 is formed at the center of the first power transmission gear 69A. .

  A hub 89 of the wheel 88 of the rear wheel WR is fixed to a protruding portion of the axle 16 from the transmission case 20 </ b> A, that is, the other end of the axle 16. The wheel 88 is formed by providing a plurality of spokes 91 between the hub 89 and a rim 90 to which a tire 93 is mounted. The spoke 91 is provided between the rim 90 and the hub 89. The second recess 92 is formed on the transmission case 20A side.

  Moreover, at least part of the second transmission shaft ball bearing 53 interposed between the end of the transmission shaft 14 on the rear wheel WR side and the transmission case 20A, in this embodiment, the second transmission shaft. A part of the ball bearing 53 for use is in the second recess 92 on the center side in the vehicle width direction of the rear wheel WR with respect to the imaginary straight line L connecting the end portions of the hub 89 and the rim 90 on the transmission case 20A side. Be contained.

  Referring to FIG. 3, the rotation direction of the clutch outer 80 in the transmission clutch 19 is regulated by a one-way clutch 94, and the one-way clutch 94 is disposed on the outer surface side of the bottom portion 80 a in the clutch outer 80. The belt type continuously variable transmission of the transmission case 20A from the right side cover member 24A side by enabling a plurality of supported rotation preventing members 95, 95... To be engaged with the rotation preventing members 95, 95. And a regulating member 96 attached to the accommodating portion 23.

  The restricting member 96 has a pair of mounting arm portions 96 a and 96 a extending outward and is formed in a ring shape, and is cylindrical between the fastening surface 28 of the belt type continuously variable transmission housing portion 23. Are attached to the fastening surface 28 by bolts 98 from the right cover member 24A side.

  A plurality of, for example, twelve locking recesses 99, 99,... Are formed on the inner periphery of the restricting member 96 at equal intervals in the circumferential direction with an angle of, for example, 30 degrees between each other. The inclined surfaces 100, 100... Are formed between the respective locking recesses 99, 99... Formed so as to be located radially inward of the clutch outer 80 toward the front along the rotational direction indicated by the arrow 101. And are formed.

  On the other hand, on the outer surface of the bottom 80a of the clutch outer 80 of the transmission clutch 19, a plurality of, for example, four pivots 102, 102... Are planted at equal intervals in the circumferential direction. 102, the light-weight portions 95a, 95a having a constriction and the weight portions 95b, 95b having no constriction are positioned on both sides of the pivot shafts 102, 102, and so on. Is rotatably supported. In addition, the pivot shafts 102, 102... Are other when the pair of locking members 95, 95 at the axially symmetrical position of the bottom portion 80a are engaged with the locking recesses 99, 99 on the inner periphery of the regulating member 96. A pair of detent members 95, 95 are arranged on the bottom 80 a so as not to engage with the locking recesses 99, 99. In this embodiment, the axially symmetrical position of the bottom 80 a The angle between a pair of pivots 102 and 102 and the other pair of pivots 102 and 102 is 75 degrees.

  The anti-rotation members 95, 95... Are spring-biased so that the tips of the light weight portions 95a, 95a... Face the radially outward direction of the bottom portion 80a, and the weight portions 95b, 95b when the clutch outer 80 rotates. A centrifugal force acting radially outward of the bottom portion 80a acts on the ..., and the rotation preventing members 95, 95 ... come into contact with the stopper pins 106, 106 ... planted on the bottom portion 80a and rotate. Hold position.

  In such a one-way clutch 94, when a force that rotates the clutch outer 80 in the direction indicated by the arrow 107 opposite to the arrow 101 acts on the clutch outer 80, a pair of detent members 95 at the axially symmetrical position of the bottom 80a. , 95 engage with the locking recesses 99, 99 of the restricting member 96 to restrict the rotation of the clutch outer 80. When a force for rotating the clutch outer 80 in the direction indicated by the arrow 101 is applied, the engagement between the rotation preventing members 95, 95... And the regulating member 96 is released, and the clutch outer 80 is moved to the arrow 101. It will rotate in the direction shown by.

  In such a power transmission device T, when the rotational speed of the engine E becomes equal to or higher than the starting rotational speed, the starting clutch 15 is brought into a connected state, and rotational power is input from the transmission shaft 14 to the mechanical transmission 17A to change the speed. While the clutch inner 79 of the clutch 19 starts to rotate, the ring gear 65 meshed with the gear 75A provided on the transmission shaft 14 starts to rotate. In this case, the transmission clutch 19 is in the disconnected state until the rotational speed of the transmission shaft 14 reaches the rotational speed at which the transmission clutch 19 is connected. Due to the rotation of the ring gear 65, a force on the side rotating in the opposite direction to the ring gear 65 acts on the sun gear 68 via the planetary gears 66. The sun gear 68 is linked to and coupled to the clutch outer 80 of the transmission clutch 19 through the transmission cylinder shaft 76, the first power transmission gear 69A, the second power transmission gear 85, and the cylinder 84. From the above, the clutch outer 80 of the transmission clutch 19 is subjected to a force that rotates in the direction opposite to the rotation direction of the transmission shaft 14, and the rotation of the clutch outer 80 is restricted by the one-way clutch 94. The sun gear 68 is also held stationary. Therefore, each planetary gear 66... Rotates around the stationary sun gear 68 together with the planetary carrier 67, and the output gear 77 and the driven gear from the planetary carrier 67 that rotates at a rotational speed decelerated from the rotational speed of the transmission shaft 14. Rotational power is transmitted to the axle 16 of the rear wheel WR via the gear 78. That is, the gear position of the mechanical transmission 17A is “LOW”.

  When the rotational speed of the transmission shaft 14 further increases and the transmission clutch 19 is connected, the restriction by the one-way clutch 94 is released and the clutch outer 80 of the transmission clutch 19 rotates together with the transmission shaft 14, and the planetary gear mechanism 18 has the sun gear 68. Will rotate in the same direction as the ring gear 65, and there will be no rotational difference between the gears in the planetary gear mechanism 18, and the gear stage of the mechanical transmission 17 </ b> A will be “HIGH”. In addition, such shift stage switching in the mechanical transmission 17A occurs when the gear ratio in the belt-type continuously variable transmission 13 is low.

  Next, the operation of the first embodiment will be described. The rotational speed at which the transmission clutch 19 is connected is set higher than the rotational speed at which the start clutch 15 is connected, and the transmission clutch 19 is disconnected. Since the rotational speed is set to be equal to or lower than the rotational speed at which the starting clutch 15 is disconnected, the starting clutch is used when the vehicle decelerates while enabling power transmission fully utilizing both gear ratios before and after the gear change by the planetary gear mechanism 18. 15 can be prevented from being disengaged prior to 15, so that the feeling of idling during deceleration can be suppressed, and the engine brake must be sufficiently applied until the start clutch 19 is disengaged. It can be applied to. Moreover, it is not necessary to use a dedicated part such as a one-way clutch for engine braking, the increase in the number of parts can be avoided, and the power transmission device T can be configured compactly, which is suitable for a motorcycle that is a saddle-ride type vehicle. It can be set as a power transmission device.

  Here, with respect to changes in the rotational speeds of the ring gear 65, the planetary carrier 67, and the sun gear 68 in the planetary gear mechanism 18 when the vehicle is decelerated, the transmission clutch 19 is in the disconnected state with respect to the rotational speed ND that is in the disconnected state of the starting clutch 15. Referring to FIG. 7, the rotational speed is changed in three stages of the rotational speeds NC1, NC2, and NC3 that are sequentially increased so that NC1> NC2> NC3> ND. The planetary carrier 67 continues coasting as the rotational speed of the planetary gear mechanism 18 in the integrally rotating state reaches the shutoff rotational speeds NC1, NC2 and NC3 of the speed change clutch 19, but the sun gear 68 increases and the ring gear 65 The engine brake is pulled and the rotational speed decreases, so that the rotational speed of the ring gear 65 becomes the disconnected state of the start clutch 15. Drops to rotational speed ND, rotation of the ring gear 65 is increased Hayashi, rotation of the sun gear 68 is decelerated, will converge to the rotation of the planet carrier 67. As apparent from the change in the rotational speed shown in FIG. 7, the gear ratio in the planetary gear mechanism 18 becomes closer as the cutoff rotational speed of the transmission clutch 19 becomes closer to the cutoff rotational speed ND of NC1 → NC2 → NC3 and the starting clutch 15. Change is less. In other words, according to the present invention, by setting the rotational speed at which the transmission clutch 19 is disengaged to be close to or less than the rotational speed at which the start clutch 15 is disengaged, it is possible to suppress the idling feeling during deceleration.

  At this time, the difference between the rotational speed at which the transmission clutch 19 is in the disconnected state and the rotational speed at which the start clutch 15 is in the disconnected state is set so that the vehicle speed difference caused by the rotational speed difference is 25 km / h or less. Preferably, the speed is reduced by bringing the rotational speed at which the shift clutch 19 is in the disconnected state and the rotational speed at which the start clutch 15 is in the disconnected state close to each other so as to suppress the vehicle speed difference to 25 km / h or less. It is possible to effectively suppress the feeling of running at the time.

  Further, since the speed change clutch 19 has a centrifugal weight 81... And is configured as a trailing type, the speed change feeling can be made smooth and connected to the rotational speed at which the speed change clutch 19 is in a disconnected state. It is easy to increase the range of the rotational speed difference from the rotational speed that is in the state, and it is possible to easily approach the rotational speed at which the starting clutch 15 is disconnected only on the disconnected side.

  Moreover, in order to make the connecting rotational speeds of the start clutch 15 and the transmission clutch 19 different and to make the shut-off speed of the shift clutch 19 equal to or lower than the shut-off speed of the start clutch 15, at least the centrifugal weights 45, 81 in both the clutches 14, 19 Since the shapes of the centrifugal weights 45 and 81 are different from each other, the center of gravity positions of the centrifugal weights 45 and 81 can be made different, and the connection rotational speeds of the transmission clutch 19 and the start clutch 15 are made different. It is easy to set the rotation speed to be equal to or less than the rotation speed at which the start clutch 15 is disconnected.

  A transmission clutch 19 is arranged coaxially with the transmission shaft 14 for inputting power from the engine E to the mechanical transmission 17A side via the belt-type continuously variable transmission 13 and the starting clutch 15. A planetary gear mechanism 18 is disposed in the vehicle front-rear direction with an interval therebetween and an intermediate shaft 54A having an axis parallel to the transmission shaft 14 is rotatably supported by the transmission case 20A, and is disposed coaxially with the intermediate shaft 54A. Since the clutch outer 80, which is the output member of the transmission clutch 19, is linked to and connected to the sun gear 68, the transmission clutch 19 and the planetary gear mechanism 18 are displaced in the vehicle front-rear direction, and the planetary gear mechanism 18 and the transmission clutch 19 The mechanical transmission 17A is made compact in the direction along the axis of the transmission shaft 14 as compared with the configuration in which is disposed coaxially with the transmission shaft 14. By mounting this power transmission device T on a saddle-ride type vehicle such as a motorcycle, it becomes easy to secure a bank angle of the vehicle, and a power transmission device T suitable for a saddle-ride type vehicle can be obtained. .

  The clutch inner 79 of the transmission clutch 19 is connected to the transmission shaft 14 so as not to rotate relative thereto, the clutch outer 80 of the transmission clutch 19 is supported to be rotatable relative to the transmission shaft 14, and the planetary gear mechanism 18 is A ring gear 65 to which power from the transmission shaft 14 is transmitted, a plurality of planetary gears 66 meshing with the ring gear 65, and the planetary gears 66 are rotatably supported on the axle 16 of the rear wheel WR. A planetary carrier 67 that is linked and connected, and a sun gear 68 that is rotatably supported by the intermediate shaft 54A and meshes with the plurality of planetary gears 66, and transmits the power of the clutch outer 80 to the sun gear 68. The first power transmission gear 69A is connected to the sun gear 68 in a relatively non-rotatable manner and is arranged coaxially with the intermediate shaft 54A. Even if the switch 19 and the planetary gear mechanism 18 are arranged so as to be displaced in the vehicle longitudinal direction, the output from the planet carrier 67 linked and connected to the axle 16 of the rear wheel WR is transmitted to the disengagement / disengagement of the transmission clutch 19. The speed can be changed by changing the rotational speed of the sun gear 68 according to the contact state, and the gear stage of the mechanical transmission 17A can be easily switched. Further, by adjusting the gear ratio between the transmission shaft 14 and the ring gear 65 of the planetary gear mechanism 18 and the gear ratio between the first power transmission gear 69A and the clutch outer 80, the output (transmission ratio) from the planetary carrier 67 is obtained. It can be easily changed.

  In addition, an outer tooth portion 73 that meshes with a gear 75A provided on the transmission shaft 14 is formed on the outer periphery of the ring portion 72 included in the ring gear 65, and an inner tooth portion 74 that meshes with the planetary gears 66. Therefore, power transmission is performed by the outer teeth 73 and the inner teeth 74 formed on the outer periphery and inner periphery of the ring portion 72 included in the ring gear 65, respectively. The axial transmission of the mechanical transmission 17A can be made compact.

  The ring gear 65 and the first power transmission gear 69A are arranged side by side in the axial direction of the intermediate shaft 54A, and a part of the ring gear 65 and the first power transmission gear 69A is seen from the axial direction of the intermediate shaft 54A. Part of the transmission clutch 19 is disposed between the ring gear 65 and the first power transmission gear 69A in the axial direction of the intermediate shaft 54A so that the ring gear 65 extends in the direction along the axis of the intermediate shaft 54A. The transmission clutch 19 and the first power transmission gear 69A can be arranged in a compact manner, and the mechanical transmission 17A can be made compact in the direction along the axis of the intermediate shaft 54A to ensure a sufficient bank angle of the vehicle. Further, the shaft interval between the transmission shaft 14 and the intermediate shaft 54A can also be reduced.

  Further, a driven gear 78 of the rear wheel WR is provided, and an output gear 77 that meshes with the driven gear 78 so as to transmit power from the planet carrier 67 to the axle 16 side is provided with the intermediate shaft 54A. The intermediate shaft 54A is disposed between the ring gear 65 and the first power transmission gear 69A in the axial direction of the intermediate shaft 54A while overlapping with a part of the transmission clutch 19 when viewed from a direction orthogonal to the axis of the intermediate shaft 54A. The ring gear 65, the output gear 77, the transmission clutch 19 and the first power transmission gear 69A are arranged more compactly in the direction along the axis of the mechanical transmission 17A, and the mechanical transmission 17A is made more compact in the direction along the axis of the intermediate shaft 54A. be able to.

  Further, at least one central portion of the planetary gear mechanism 18 and the first power transmission gear 69A is provided with first and second intermediate shaft ball bearings 57 provided between both end portions of the intermediate shaft 54A and the transmission case 20A. , 58 is provided with a first recess that accommodates a part of at least one of them, and in this embodiment, a first intermediate shaft is provided at the center of the end plate portion 71 of the ring gear 65 in the planetary gear mechanism 18. A first recess 86 that accommodates a part of the ball bearing 57 is formed, and a first recess 87 that accommodates a part of the second intermediate shaft ball bearing 58 is formed at the center of the first power transmission gear 69A. Therefore, a part of the planetary gear mechanism 18 and the first power transmission gear 69A is arranged in the space around the first and second intermediate shaft ball bearings 57, 58. It possible, it is possible to reduce the weight of with more compact mechanical transmission 17A in the axial direction of the intermediate shaft 54A.

  Further, a hub 89 of the wheel 88 of the rear wheel WR is fixed to the projecting portion of the axle 16 from the transmission case 20A, and a second recess 92 opened between the hub 89 and the rim 90 toward the transmission case 20A. The rim 90 and the hub 89 are connected by a plurality of spokes 91, so as to form a second, and a second wheel interposed between the end of the transmission shaft 14 on the rear wheel WR side and the transmission case 20A. At least a part (a part in this embodiment) of the transmission shaft ball bearing 53 of the rear wheel WR is more than the imaginary straight line L connecting the end of the hub 89 and the rim 90 on the transmission case 20A side. Since it is housed in the second recess 92 on the center side in the vehicle width direction, the transmission shaft 14 can be arranged closer to the rear wheel WR side, and the power transmission device T is enlarged on the outer side in the vehicle width direction. The bank angle to avoid can be easily ensured.

  Further, the transmission case 20A houses a belt-type continuously variable transmission 13 provided between the engine E and the transmission shaft 14, and a belt-type continuously variable transmission in which a housing recess 27 is formed on the side surface on the rear wheel WR side. The housing recess 27 is covered so as to form a mechanical transmission housing chamber 22 for housing the mechanical transmission 17A between the machine housing 23 and the belt-type continuously variable transmission housing 23. A right-hand cover member 24A fastened to the belt-type continuously variable transmission housing 23, and a rotation-preventing member 95 supported by a clutch outer 80 having a bottom portion 80a in the transmission clutch 94 and having a bottom shape; 95. A restricting member 96 constituting a one-way clutch 94 that restricts the rotation direction of the clutch outer 80 in cooperation with 95... Engages with the non-rotating members 95, 95. It is attached to the belt type continuously variable transmission housing 23 from the right cover member 24A side as possible, and the detent members 95, 95... And the regulating member 96 are connected to the right cover member 24A and the belt type continuously variable transmission. Since the right cover member 24A is disposed on the side of the right cover member 24A with respect to the fastening surface 28 of the housing portion 23, when the right cover member 24A is removed from the belt type continuously variable transmission housing portion 23, the rotation preventing members 95, 95. The member 96 is disposed outside the fastening surface 28, and assembly is facilitated. In addition, since the rotation preventing members 95, 95... Are supported on the outer surface side of the bottom 80a of the clutch outer 80 arranged with the open end facing the belt type continuously variable transmission housing 23, the one-way clutch 94 is assembled. Sometimes, the assembly work can be performed while visually checking the anti-rotation members 95, 95... And the regulating member 96, and the assemblability is further improved.

  The second embodiment of the present invention will be described with reference to FIG. 8, but the parts corresponding to the first embodiment are only shown with the same reference numerals, and the detailed description is as follows. Omitted.

  The transmission case 20B includes a belt-type continuously variable transmission housing portion 23 that forms a belt-type continuously variable transmission housing chamber 21 that houses the belt-type continuously variable transmission 13 and the starting clutch 15, and the belt-type continuously variable transmission. The mechanical transmission 17B is housed between the belt-type continuously variable transmission housing 23 and the right cover member 24B.

  The transmission clutch 19 provided in the mechanical transmission 17B is disposed coaxially with the transmission shaft 14 by opening the open end of the hook-shaped clutch outer 80 provided in the transmission clutch 19 to the side opposite to the rear wheel WR. Further, the regulating member 96 of the one-way clutch 94 that regulates the rotation direction of the clutch outer 80 in the transmission clutch 19 is a belt-type continuously variable transmission housing portion behind the fastening surface 28 of the belt-type continuously variable transmission housing portion 23. 23 is fastened.

  An intermediate shaft 54B disposed at an interval in the vehicle front-rear direction with respect to the transmission shaft 14 is rotatably supported on the transmission case 20B, and a first power transmission gear fixed to the intermediate shaft 54B is supported. A second power transmission gear 85 meshing with 69B is provided on a cylinder 84 rotatably supported on the transmission shaft 14 via a needle bearing 83, and the clutch outer 80 of the transmission clutch 19 is connected to the cylinder body. 84 is fixed.

  The planetary gear mechanism 18 is arranged coaxially with the intermediate shaft 54B, and its ring gear 65 is a gear 75B fixed to the transmission shaft 14 between the second power transmission gear 84 and the second transmission shaft 53. And the sun gear 68 is fixed to the intermediate shaft 54B, and the planetary carrier 67 is supported on the intermediate shaft 54B via a needle bearing 120 so as to be rotatable relative to the intermediate shaft 54B. Fixed to the output gear 77.

  Also according to the second embodiment, the transmission clutch 19 and the planetary gear mechanism 18 are arranged so as to be shifted in the vehicle front-rear direction, and the planetary gear mechanism 18 and the transmission clutch 19 are arranged coaxially with the transmission shaft 14. The mechanical transmission 17B can be made compact in the direction along the axis of the transmission shaft 14 compared with the above, and the bank angle of the vehicle is secured by installing this power transmission device in a saddle-ride type vehicle such as a motorcycle. Therefore, a power transmission device suitable for a saddle-ride type vehicle can be obtained.

  As a third embodiment of the present invention, as shown in FIG. 9, the transmission clutch 19 provided in the mechanical transmission 17C has an open end of a hook-like clutch outer 80 provided in the transmission clutch 19 at the rear wheel WR side. And may be arranged coaxially with the transmission shaft 14.

  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. Is possible.

DESCRIPTION OF SYMBOLS 13 ... Belt type continuously variable transmission 14 ... Transmission shaft 15 ... Starting clutch 16 ... Axle 17A, 17B, 17C ... Mechanical transmission 18 ... Planetary gear mechanism 19 ... Transmission clutches 20A, 20B ... transmission case 22 ... mechanical transmission housing chamber 23 ... belt type continuously variable transmission housing 24 ... right cover member 27 serving as a cover member ... housing recess 28 ... Fastening surfaces 45, 81 ... Centrifugal weight 53 ... Transmission shaft ball bearings 54A, 54B ... intermediate shafts 57, 58 ... Intermediate shaft bearings for intermediate shafts Ball bearing 65 ... Ring gear 66 ... Planetary gear 67 ... Planetary carrier 68 ... Sun gear 69A, 69B ... First power transmission gear 72 as a power transmission gear ... Ring part 73- ..Outer teeth 7 ... inner teeth 75A, 75B ... gear 77 ... output gear 78 ... driven gear 79 ... clutch inner 80 ... clutch outer 80a ... bottom 87 ... first recess 88 ... Wheel 89 ... Hub 90 ... Rim 91 ... Spoke 92 ... Second recess 94 ... One-way clutch 95 ... Non-rotating member 96 ... Restricting member E ... -Engine L ... Virtual straight line WR ... Rear wheel

Claims (11)

  A belt-type continuously variable transmission (13) that transmits power from the engine (E) so that its rotational speed can be continuously changed, and the belt-type continuously variable transmission (13) and transmission shaft (14). A centrifugal start clutch (15) provided between the planetary gear mechanism (18) and the planetary gear mechanism (18) provided between the transmission shaft (14) and the rear wheel (WR) axle (16). A mechanical transmission (17A, 17B, 17C) including a centrifugal transmission clutch (19) for changing the gear position, and the rotational speed at which the transmission clutch (19) is connected is that of the start clutch (15). In a power transmission device for a saddle-ride type vehicle that is set to be higher than the number of revolutions in a connected state, the number of revolutions in which the transmission clutch (19) is in a disengaged state is the number of revolutions in which the start clutch (15) is in a disengaged state. Near , Or a power transmission device for a saddle type vehicle, characterized in that it is set to less.   The difference between the rotational speed at which the transmission clutch (19) is disengaged and the rotational speed at which the start clutch (15) is disengaged is such that the difference in vehicle speed caused by the rotational speed difference is 25 km / h or less. The power transmission device for a saddle-ride type vehicle according to claim 1, wherein the power transmission device is set.   The power transmission device for a saddle-ride type vehicle according to claim 1 or 2, wherein the transmission clutch (19) includes a centrifugal weight (81) and is configured to be a trailing type.   The start clutch (15) and the shift clutch (19) each having a centrifugal weight (45, 81) are configured so that at least the shape of the centrifugal clutch (45, 81) is the start clutch (15) and the shift clutch ( 19. The power transmission device for a saddle-ride type vehicle according to claim 1, wherein the power transmission device is configured differently from 19).   A clutch inner (79) of the transmission clutch (19) is connected to the transmission shaft (14) so as not to rotate relative to the transmission shaft (14), and a clutch outer (80) of the transmission clutch (19) can rotate relative to the transmission shaft (14). The intermediate shaft (54A, 54B) having an axis parallel to the transmission shaft (14) and spaced from the transmission shaft (14) in the vehicle front-rear direction is disposed in the transmission case (20A, 20B), the planetary gear mechanism (18), which is rotatably supported by the intermediate shaft (54A, 54B), and a ring gear (65) to which power from the transmission shaft (14) is transmitted. , A plurality of planetary gears (66) meshing with the ring gear (65), and planet carriers that are linked to and coupled to the axle (16) of the rear wheel (WR) by rotatably supporting these planetary gears (66). ( 7) and a sun gear (68) meshing with the plurality of planetary gears (66), and the power transmission gears (69A, 69B) for transmitting the power of the clutch outer (80) to the sun gear (68) The transmission shaft (14) is connected to the sun gear (68) so as not to rotate relative to the intermediate shaft (54A, 54B) and between the clutch outer (80) and the transmission case (20A, 20B). The power transmission device for a saddle-ride type vehicle according to any one of claims 1 to 4, further comprising a one-way clutch (94) that allows rotation in the forward rotation direction.   Outer teeth (73) meshing with gears (75A, 75B) provided on the transmission shaft (14) are formed on the outer periphery of the ring portion (72) included in the ring gear (65), and the planetary gear (66). The power transmission device for a saddle-ride type vehicle according to claim 5, wherein an inner tooth portion (74) meshing with the inner ring portion (72) is formed on an inner periphery of the ring portion (72).   The ring gear (65) and the power transmission gear (69A) are arranged side by side in the axial direction of the intermediate shaft (54A), and the ring gear (65) and the power transmission are viewed from the axial direction of the intermediate shaft (54A). A part of the speed change clutch (19) is disposed between the ring gear (65) and the power transmission gear (69A) in the axial direction of the intermediate shaft (54A) so as to partially overlap the gear (69A). The power transmission device for a saddle-ride type vehicle according to claim 5 or 6.   A driven gear (78) is provided on the axle (16), and an output gear (77) meshing with the driven gear (78) so as to transmit power from the planet carrier (67) to the axle (16) side. ) Overlaps with a part of the transmission clutch (19) when viewed from the direction orthogonal to the axis of the intermediate shaft (54A), and the ring gear (65) and the power in the axial direction of the intermediate shaft (54A). The power transmission device for a saddle-ride type vehicle according to any one of claims 5 to 7, wherein the power transmission device is disposed between the transmission gears (69A).   A pair of intermediate shaft bearings (at a center portion of at least one of the planetary gear mechanism (18) and the power transmission gear (69A)) provided between both ends of the intermediate shaft (54A) and the transmission case (20A) ( A power transmission device for a saddle-ride type vehicle according to any one of claims 5 to 8, further comprising a first recess (87) that accommodates at least a part of at least one of (57, 58). .   A hub (89) of the wheel (88) of the rear wheel (WR) is fixed to a protruding portion of the axle (16) from the transmission case (20A), and between the hub (89) and the rim (90). The rim (90) and the hub (89) are connected by a plurality of spokes (91) so as to form a second recess (92) opened on the transmission case (20A) side, and the transmission shaft ( 14) at least a part of the transmission shaft bearing (53) interposed between the rear wheel (WR) side end of the transmission wheel and the transmission case (20A), the hub (89) and the rim (90). Is housed in the second recess (92) on the vehicle width direction center side of the rear wheel (WR) with respect to the imaginary straight line (L) connecting the end portions on the transmission case (20A) side. Power of saddle riding type vehicle according to any one of claims 5 to 9 Reach equipment.   The transmission case (20A) accommodates the belt-type continuously variable transmission (13) and the starting clutch (15), and a belt-type in which a housing recess (27) is formed on the side surface on the rear wheel (WR) side. A mechanical transmission accommodating chamber (22) for accommodating the mechanical transmission (17A) is formed between the continuously variable transmission accommodating portion (23) and the belt type continuously variable transmission accommodating portion (23). The cover-like clutch outer having a bottom portion (80a) is formed by a cover member (24) that covers the housing recess (27) and is fastened to the belt-type continuously variable transmission housing portion (23). (80) is disposed on the belt-type continuously variable transmission housing (23) side with its open end and is supported on the outer surface side of the bottom (80a) of the clutch outer (80). (95) in cooperation with the one wake The restricting member (96) constituting the switch (94) can engage the detent member (95) so that the belt type continuously variable transmission housing (23) from the cover member (24) side. The detent member (95) and the restricting member (96) are attached to the cover member (24) and the fastening surface (28) of the belt-type continuously variable transmission housing (23). The power transmission device for a saddle-ride type vehicle according to any one of claims 5 to 11, wherein the power transmission device is disposed on a side of (24).

Images