TWI435009B - V-belt continuously variable transmission - Google Patents

Description

V-belt type stepless speed changer

The present invention relates to a V-belt type stepless speed changer.

Conventionally, for example, as shown in Patent Document 1 (Fig. 2), there is a V-belt type stepless speed changer including the following members: a drive pulley (3) supported by the main shaft (1); and a counter shaft (2) a driven pulley (4); a V-belt (5) mounted between the driving pulley (3) and the driven pulley (4); and the driving pulley (3) and the driven pulley (4) and the case (100, 101) of the V-belt (5); the groove width variable mechanism (8) for changing the groove width of the drive pulley (3); the groove width variable mechanism (8) The driving unit (500) is activated; and the power of the driving unit (500) is transmitted to the power transmitting unit (12, etc.) of the groove width variable mechanism (8).

[Previous Technical Literature] [Patent Literature]

[Patent Document 1] Japanese Patent Laid-Open Publication No. 2006-022929

In the above-described V-belt type stepless speed changer, the drive unit (500) in which the groove width variable mechanism (8) is actuated is disposed outside the casing (100, 101).

Therefore, it is difficult to cover the output portion (the gear 11D or the like (Fig. 4 of Patent Document 1)) and the groove width variable mechanism (8) disposed in the drive unit (500) by the case (100, 101) and the drive unit (500). In the power transmission portion (12, etc.) between them, it is difficult to ensure the sealing property, particularly the sealing between the driving unit (500) and the power transmitting portion (12, etc.).

An object of the present invention is to solve the above problems, and to provide a V-belt type stepless speed changer which is easy to ensure sealing property, particularly a sealability between a groove width adjusting mechanism and a drive unit and a power transmission portion.

In order to achieve the above object, the V-belt type stepless speed changer of the present invention comprises: a drive pulley supported on the main shaft; a driven pulley supported on the countershaft; and is disposed between the drive pulley and the driven pulley a V-belt; a casing for accommodating the driving pulley, the driven pulley and the V-belt; and a groove width variable mechanism for changing a groove width of the driving pulley and/or the driven pulley; a driving unit that operates the variable mechanism; and a power transmitting unit that transmits the power of the driving unit to the groove width variable mechanism; wherein the driving unit and the power transmitting unit are disposed in the casing to connect the main shaft and the counter shaft On the line.

According to the V-belt type stepless speed changer, the drive unit that operates the groove width variable mechanism and the power transmission unit that transmits the power of the drive unit to the groove width variable mechanism are disposed in the drive pulley, Since the driven pulley and the V-belt are inside the casing, it is easy to ensure the sealing property and to miniaturize the casing. In particular, since the drive unit and the power transmission unit of the groove width variable mechanism are entirely covered by the casing, the sealing property between the drive unit and the power transmission unit can be easily ensured. Further, by arranging the drive unit and the power transmission unit between the main shaft and the counter shaft, it is possible to suppress the protrusion of the casing and to reduce the size of the casing.

Preferably, the driving unit includes a motor portion that houses a motor as a driving source, and an output shaft of the driving unit that is actuated by the power of the motor, and the output shaft is held by the spindle or the counter shaft Parallel configuration.

According to this configuration, it is easy to bring the drive unit closer to the main shaft or the counter shaft, so that the power transmission unit that transmits the power of the drive unit to the groove width variable mechanism can be downsized. As a result, the V-belt type stepless speed changer can be miniaturized.

More preferably, the front end of the output shaft protrudes toward the V-belt side from the motor portion, and at least a part of the output shaft is disposed in the V as viewed from a direction orthogonal to the output shaft. In the belt width of the belt, the motor portion is disposed outside the belt width, and viewed from the axial direction of the output shaft, the output shaft is disposed in the rotation locus of the V-belt to connect the main shaft and the counter shaft. on-line.

According to this configuration, the following effects can be obtained. That is, the front end of the output shaft of the drive unit is protruded toward the V-belt side from the motor portion, and at least a part of the output shaft is disposed on the V-belt when viewed from a direction orthogonal to the output shaft. Within the width of the belt, the amount of protrusion of the drive unit toward the main axis can be reduced by the amount corresponding to the overlap of the belt width and the output shaft, and the V-belt stepless transmission can be miniaturized. Further, since the motor portion of the drive unit is disposed outside the belt width, it is possible to surely prevent the V-belt from interfering with the motor portion, and the output shaft is disposed in the V-belt rotation as viewed from the axial direction of the output shaft. The line connecting the main shaft and the counter shaft in the track prevents the V-belt from interfering with the output shaft when the V-belt is bent.

More preferably, the driving unit includes a reduction gear set that transmits power of the motor to the output shaft, and the reduction gear set is disposed outside a belt width of the V-belt while viewed from an axial direction of the output shaft. Next, the reduction gear set overlaps with the V-belt.

According to this configuration, even in the case where the driving unit includes the reduction gear set, the interference between the reduction gear group portion and the V-belt can be prevented, and at the same time, viewed from the axial direction of the output shaft, the reduction gear set and the V-belt phase The overlap makes it possible to miniaturize the V-belt stepless speed changer.

Hereinafter, an embodiment of a V-belt type stepless speed changer according to the present invention will be described with reference to the drawings.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a side elevational view showing a scooter type two-turbine vehicle as an example of an embodiment of a V-belt type stepless speed changer according to the present invention, and Fig. 2 is a V-belt type stepless speed changer including the above-mentioned two-wheeled vehicle. A side view of the power unit, and FIG. 3 is a cross-sectional view of a portion III-III of FIG.

As shown in FIG. 1 , the two-wheeled motor vehicle 10 is at the rear of the frame 11 , and the power unit 20 is swingably suspended around the pivot 12 relative to the frame 11 by the pivot 12 and the rear shock absorber unit 13 . Vehicle. A front fork 14 is rotatably mounted to the front tube 11h, and a front wheel 15F is attached to the lower end of the front fork 14. A steering handle 15 is attached to the upper portion of the front fork 14.

The frame 11 has a pair of left and right mounts 11s (only one of which is shown) at the rear. A seat portion 16 for the passenger to straddle is provided on the seat frame 11s, and a storage box 17 that opens upward is provided below the seat portion 16. A fuel tank 18 is disposed behind the storage box 17.

The power unit 20 includes an engine 30 as a drive source and a gearbox 40 disposed behind the engine 30. A V-belt type stepless speed changer 50 that transmits the driving force of the engine 30 to the rear wheel 15R is built in the transmission 40. The power unit 20 is swingably attached to the rear end of the frame 11, and the power of the engine 30 is transmitted to the rear wheel 15R via the V-belt type stepless speed changer 50 in the transmission 40. Therefore, the power unit 20 doubles as a rear rocker arm.

As shown in FIG. 3, the engine 30 mainly includes a crankcase 31, a cylinder block 32, a cylinder head 33, and a cylinder head cover 34. A cylinder block 32 directed in a substantially horizontal direction is coupled to the front end of the crankcase 31, a cylinder head 33 is coupled to the front end of the cylinder block 32, and a cylinder head cover 34 is coupled to the front end of the cylinder head 33.

The crankshaft 31c is rotatably supported by the ball bearings 31b and 31b held in the crankcase 31, and the piston 32p is slidably provided in the cylinder block 32. The crankshaft 31c and the piston 32p are coupled by a link 32c, and the crankshaft 31c is rotated by the reciprocating movement of the piston 32p. The crank shaft 31c constitutes the following main shaft 51. An intake pipe 35 (FIG. 1) and an exhaust pipe 36 (FIG. 1) that communicate with the combustion chamber 33c are connected to the cylinder head 33. As shown in FIG. 2, a fuel supply device 35a and an air cleaner 35c are connected to the intake pipe 35. A muffler (not shown) is connected to the exhaust unit 36.

In Fig. 3, the component symbol 30p is a spark plug, and the component symbol 30c is a camshaft for a pneumatic valve which is disposed in the cylinder head cover 34 and is rotationally driven by the crankshaft 31c via the chain c. The component symbol 31g is attached to the crankcase cover. The 31e has a stator provided around the crankshaft 31c and a generator fixed to the rotor of the crankshaft 31c.

As shown in FIG. 3, the gearbox (also referred to simply as the case) 40 is a case that forms part of the power unit 20. The case 40 includes a right case 40R and a left case 40L coupled therewith. The right case 40R is integrally formed with the crank case 31 described above. A gear case cover 40C constituting a gear case (40G) that decelerates the rotation of the sub-shaft 52 and transmits it to the rear wheel shaft 55 is coupled to the rear portion of the right casing 40R.

4 is a partial enlarged view of FIG. 3, and FIG. 5 is a view showing a partial V arrow of FIG.

As shown in FIG. 3, the V-belt type stepless speed change machine 50 mainly includes a drive pulley 60 supported by a main shaft 51 as a first pulley shaft, and a driven pulley supported as a counter shaft 52 of the second pulley shaft. 70; and a V-belt 53 mounted between the drive pulley 60 and the driven pulley 70. Further, the V-belt type stepless speed changer 50 includes a casing 40 that houses the drive pulley 60, the driven pulley 70, and the V-belt 53; and the groove width of the groove width of the drive pulley 60 can be changed. The variable mechanism 80 (FIG. 4); the drive unit 90 that activates the groove width variable mechanism 80; and the power of the drive unit 90 is transmitted to the power transmission unit 100 of the groove width variable mechanism 80.

Further, the groove width variable mechanism 80 (the power transmission unit 100 or the like may be omitted) may be configured to change the groove width of the driven pulley 70 instead of changing the groove width of the drive pulley 60, or may be configured to change the drive belt. The groove width of the wheel 60 and the groove width of the driven pulley 70. Therefore, in the present case, the term "belt axle" means the first and/or second pulley shaft.

One of the features of the V-belt type stepless speed changer 50 of the present embodiment is that the drive unit 90 and the power transmission unit 100 are disposed in the casing 40.

Hereinafter, the configuration of the V-belt type stepless speed change machine 50 will be described in order.

As shown in Figs. 3 and 4, in the present embodiment, the main shaft 51 is constituted by the crank shaft 31c as described above.

The main shaft 51 includes a large diameter portion 51a supported by both ends of the bearings 31b and 31b as bearing members, and a movable pulley 62 provided in the large diameter portion 51a via the step portion 51d and constituting the driving pulley 60. The small diameter portion 51b of the portion.

As shown in Fig. 4, in the present embodiment, a groove width varying mechanism 80 is provided in the drive pulley 60.

The drive pulley 60 includes a fixed pulley (fixed half) 61 that is not movable in the axial direction of the main shaft (the pulley shaft) 51, and a movable pulley that is movable in the axial direction with respect to the main shaft 51 but cannot be relatively rotated. (movable half) 62.

The groove width varying mechanism 80 is a mechanism for changing the groove width of the pulley 60, that is, changing the fixing band, by sliding the movable pulley 62 in the axial direction along the support portion 51b of the movable pulley 62 in the pulley shaft 51. The wheel 61 is spaced from the movable pulley 62.

The groove width varying mechanism 80 includes a torque transmitting portion 110 that is relatively rotatable relative to the pulley shaft 51, and a hub portion 63 that is provided to the movable pulley 62 and that transmits torque between the torque transmitting portion 110.

FIG. 6 is an exploded perspective view showing a main part of the torque transmitting unit 110.

As shown in FIGS. 4 to 6, the torque transmitting portion 110 includes a radial direction portion 111 extending in the radial direction of the pulley shaft 51, and an axial direction portion 112 integrally provided with the radial direction portion 111 and extending in the axial direction. The axial direction portion 112 is located further in the radial direction than the opposing surface of the movable portion of the movable pulley 62 with the support portion 51b of the movable pulley 62 of the pulley 51 (in the present embodiment, the inner peripheral surface of the hub portion 63) 63a. At the office. A plurality of axial direction portions 112 are provided (three in the circumferential direction at equal intervals in the present embodiment).

The torque transmitting portion 110 may be formed integrally with the main shaft 51. However, in the present embodiment, the torque transmitting portion 110 is constituted by another member (also referred to as a torque transmitting member) that is separated from the pulley shaft 51.

The radial direction portion 111 of the torque transmitting portion 110 has a shape in which the disk-shaped portion 111a is radially extended in three directions, and the axial direction portion 112 is integrally formed at the front end of the extended portion.

The hub portion 63 of the movable pulley 62 is provided with a torque transmitting surface 64 that transmits torque between the axial direction portion 112 of the torque transmitting portion 110. The torque transmitting surface 64 is relatively movable in the axial direction with respect to the axial direction portion 112.

A hole 65 into which the axial direction portion 112 of the torque transmitting portion 110 is inserted is provided in the boss portion 63 of the movable pulley 62. The hole 65 has a sector shape in a cross section and substantially coincides with a cross section of the axial direction portion 112. The end surface of the hole 65 in the circumferential direction is formed as a torque transmitting surface 64. The axial direction portion 112 is located outside the inner peripheral surface 63a of the hub portion 63 in the radial direction in a state where it has been inserted into the hole 65 of the boss portion 63.

Between the axial direction portion 112 of the torque transmitting portion 110 and the torque transmitting surface 64 of the hub portion 63, a synthetic resin (for example, a polyacetamide resin (for example, PA66) is mixed with a hardened material (for example, carbon). A cushioning member 66 of a material requiring hardness.

The cushioning member 66 is attached to the inner side of the front end portion of the axial direction portion 112 of the torque transmitting portion 110, and has a shape conforming to the front end portion of the axial direction portion 112. The cushioning member 66 shown in Fig. 6 is an integrally molded product including a curved inner peripheral wall portion 66a, two side wall portions 66b and 66b, a bottom wall portion 66c, and a projection 66d that protrudes outward in the radial direction from the inner peripheral wall portion 66a.

A hole 112d is provided in the axial direction portion 112 of the torque transmitting portion 110.

The cushioning member 66 fits the projection 66d of the inner peripheral wall portion 66a into the hole 112d of the axial direction portion 112, and the inner peripheral wall portion 66a is engaged to the inner side of the front end portion of the axial direction portion 112, thereby being attached to the front end portion of the axial direction portion 112. .

The axial direction portion 112 is inserted into the hole 65 of the hub portion 63 together with the cushioning member 66 in a state where the cushioning member 66 is attached. In a state where the cushioning member 66 has been inserted into the hole 65, the outer side surface 66b1 of the side wall portion 66b of the cushioning member 66 constitutes a torque transmitting surface that abuts against the torque transmitting surface 64 of the boss portion 63.

The cushioning member 66 is slidable in the axial direction together with the axial direction portion 112 in the hole 65 of the hub portion 63, but since the projection 66d of the cushioning member 66 is engaged with the hole 112d of the axial direction portion 112, even the axial direction portion 112 The sliding member 66 is also not detached from the axial direction portion 112.

6 shows a configuration in which the cushioning member 66 is attached to the inner side of the end portion before the axial direction portion 112. However, the cushioning member 66 may be attached to the outer side of the end portion before the axial direction portion 112. Further, the cushion member 66 may be attached not to the axial direction portion 112. In this case, the side surface of the axial direction portion 112 constitutes a torque transmitting surface that abuts against the torque transmitting surface 64 of the hub portion 63.

In Fig. 5 and Fig. 6, the reference numeral 67 is a cylindrical member. The cylindrical member 67 is inserted into the boss portion 63 of the movable pulley 62 and attached to the small diameter portion 51b of the pulley shaft 51. As shown in FIG. 4, a double nut 68 is attached to the front end of the small diameter portion 51b, and the torque is transmitted between the small diameter portion 51b and the step portion 51d of the main shaft 51 by the double nut 68. The member 110, the cylindrical member 67, and the fixed pulley 61 are fixed to the small diameter portion 51b. In other words, the radial direction portion 111 is sandwiched between one end portion 67a of the cylindrical member 67 and the step portion 51d, and the torque transmission member 110 is fixed so as not to be rotatable with respect to the pulley shaft 51. Further, the fixed pulley 61 is sandwiched between the other end portion 67b of the cylindrical member 67 and the double nut 68, and is fixed so as not to be rotatable with respect to the pulley shaft 51.

The movable pulley 62 is inserted into the hole 65 of the hub portion 63 as described above, and is attached so as not to be rotatable relative to the pulley shaft 51 but slidable.

As shown in FIGS. 4 and 5, an engaging member 120 for sliding the movable sheave 62 is disposed on the outer circumference of the boss portion 63 of the movable sheave 62. The engaging member 120 will be described in detail below together with the power transmitting unit 100.

As shown in FIGS. 4 and 5, the drive unit 90 includes a motor portion M1 (FIG. 4) in which a motor (servo motor) M (FIG. 5) as a drive source is housed; and the motor M is actuated by the power of the motor M. An output shaft 91 of the drive unit 90; the output shaft 91 is disposed in parallel with the spindle 51. Further, in the case where the groove width of the driven pulley 70 is varied by the drive unit 90, the output shaft 91 and the counter shaft 52 are arranged in parallel.

The drive unit 90 includes a reduction gear set 92 that communicates the power of the motor M to the output shaft 91. A ball screw (external thread) 93 is concentrically connected to the last stage gear 92e of the reduction gear set 92. The base side of the output shaft 91 is formed in a cylindrical shape, and a ball screw (internal thread) 91b is formed on the inner surface thereof, and the internal thread 91b is screwed to the ball screw (external thread) 93. Therefore, when the ball screw 93 is rotated via the reduction gear train 92 by the driving of the motor M, the output shaft 91 moves forward and backward in the axial direction (the directions of the arrows X1 and X2 in Fig. 4) in accordance with the rotation direction.

The drive unit 90 is fixed in the casing 40 by fastening the gear case 94 in which the reduction gear set 92 is housed by the screw 95 to the attachment portion 41 (FIG. 3) provided in the casing 40. In the present embodiment, the gear case 94 (ie, the drive unit 90) is covered by the side cover 40LC, and the drive unit 90 is housed in the case 40. The side cover 40LC is detachably mounted by screws 42. Although the left case 40L is formed in one part of the left case 40L, the side cover 40LC and the left case 40L may be completely integrated, and the drive unit 90 and the power transmission unit 100 may be housed in the case 40.

As shown in FIG. 4, the front end 91a of the output shaft 91 protrudes toward the V-belt 53 side toward the motor portion M1 of the drive unit 90, and at least the output shaft 91 is viewed from a direction orthogonal to the output shaft 91. A portion 91c is disposed within the belt width W of the V-belt. The motor portion M1 is disposed outside the belt width W. As shown in FIGS. 2 and 5, the output shaft 91 is disposed on the line L1 connecting the main shaft 51 and the counter shaft 52 in the rotation locus 53i of the V-belt 53 as viewed in the axial direction of the output shaft 91. As shown in FIG. 4, the reduction gear set 92 is disposed outside the belt width W of the V-belt 53, and as shown in FIG. 5, the reduction gear set 92 and the V-belt 53 are held as viewed from the axial direction of the output shaft 91. Overlapping configuration.

As shown in FIGS. 4 and 5 , the power transmission unit 100 is configured to transmit the power of the drive unit 90 to the groove width variable mechanism 80 , and includes the engagement member 120 and the connection member 130 . The engaging member 120 and the connecting member 130 are coupled by a screw 131. The joint member 130 is coupled to the output shaft 91 by a screw 132. Therefore, when the output shaft 91 moves forward and backward, the engaging member 120 and the connecting member 130 also move forward and backward together with the output shaft 91.

As shown in FIG. 4, the connection part 133 of the connection member 130 connected to the output shaft 91 is connected to the front end surface 91e of the output shaft 91.

As shown in FIG. 5, the engaging member 120 includes an engaging portion 121 that indirectly engages with the boss portion 63 of the movable pulley 62 to slide the movable pulley 62. As shown in FIG. 4, a bearing 69 that cannot slide in the axial direction of the hub portion 63 is fixed to the outer circumference of the boss portion 63 of the movable pulley 62. An engagement ring 122 that cannot slide in the axial direction is fixed to the outer periphery of the bearing 69. An annular engagement groove 123 is formed on the outer circumference of the engagement ring 122, and the engagement portion 121 of the engagement member 120 is engaged with the engagement groove 123. As described above, in the drawing, the engaging portion 121 of the engaging member 120 is indirectly engaged (via the engaging ring 122 and the bearing 69) to the boss portion 63 of the movable pulley 62, but the engaging portion 121 may be directly Engaged in the hub portion 63.

As shown in FIG. 4, the engaging portion 121 is adjacent to the bearing portion 31b between the movable pulley 62 and the bearing portion 31b that supports the pulley shaft 51 to which the movable pulley 62 is attached, in the axial direction of the movable pulley 62. And configuration. That is, the engaging portion 121 is disposed as close as possible to the bearing portion 31b. Preferably, the engaging portion 121 is engaged with the boss portion 63 of the movable pulley 62 at at least two portions facing each other with the pulley shaft 51 interposed therebetween. In the present embodiment, the engaging portion 121 is coupled to the axle portion. 51 (that is, the center of rotation of the hub portion 63) is held in a point symmetrical manner at two locations.

As shown in FIG. 3, the sub-shaft 52 as a driven shaft of the V-belt type stepless speed changer 50 is rotatably supported by the left case 40L and the gear case cover 40C of the case 40. The counter pulley 52 is provided with a driven pulley 70 via a centrifugal clutch 54.

The driven pulley 70 includes a fixed pulley (fixed half) 71 and a movable pulley (movable half) 72. An annular V-belt 53 is provided on the drive pulley 60 and the driven pulley 70 for transmitting the rotation of the drive pulley 60 to the driven pulley 70. When the number of revolutions of the driven pulley 70 exceeds the predetermined number of revolutions, the centrifugal clutch 54 provided between the driven pulley 70 and the counter shaft 52 is brought into a connected state, and the counter shaft 52 starts to rotate.

The gear set (gearbox) 40G that decelerates the rotation of the countershaft 52 and transmits it to the rear axle 55 includes: a gear 52g disposed on the countershaft 52; a large diameter gear 141 meshing with the gear 52g; and a diameter smaller than the large gear a pinion 142 that rotates together with the large gear 141; and a large gear 143 that meshes with the pinion 142. The large gear 143 is attached to the rear wheel shaft 55 so as not to be rotatable relative thereto.

Therefore, the rotation of the counter shaft 52 is decelerated and transmitted to the rear wheel shaft 55, and is driven to be mounted on the rear wheel shaft 55 to the rear wheel 15R (Fig. 1).

The movable pulley 72 of the driven pulley 70 is mounted to be movable in the axial direction with respect to the counter shaft 52. The movable pulley 72 is biased toward the fixed pulley 71 by the coil spring 73, and moves in the axial direction in accordance with the tension acting on the V-belt 53. That is, if the movable pulley 62 of the drive pulley 60 is displaced in the direction in which the groove width is reduced, and the winding diameter of the V-belt 53 with respect to the drive pulley 60 is increased, the V-belt 53 wound around the driven pulley 70 is formed. When pulled toward the side of the drive pulley 60, the tension acting on the V-belt 53 becomes large, and by the increase of the tension, the movable pulley 72 of the driven pulley 70 is displaced in the direction in which the groove width is expanded, and the V-belt 53 is displaced. As the winding diameter of the driven pulley 70 becomes smaller, the counter shaft 52 rotates at a high speed. When the movable pulley 62 of the drive pulley 60 is displaced in the direction in which the groove width is expanded, the opposite operation is performed, and the counter shaft 52 is rotated at a low speed.

The drive unit 90 is actuated by the control of the control unit (not shown). When the output shaft 91 protrudes in the direction of the arrow X1 and the movable pulley 62 slides in the X1 direction in FIG. 4, the fixed pulley 61 and the movable pulley 62 are spaced apart. Further, the winding diameter of the V-belt 53 with respect to the drive pulley 60 becomes small, and the winding diameter of the V-belt 53 with respect to the driven pulley 70 becomes large, and the rear wheel 15R is rotationally driven at a low speed, so as to withstand high. load. On the contrary, if the output shaft 91 slides in the direction of the arrow X2 and the movable pulley 62 slides in the X2 direction, the interval between the fixed pulley 61 and the movable pulley 62 becomes narrow, and the winding diameter of the V-belt 53 with respect to the drive pulley 60 becomes At the same time, the winding diameter of the V-belt 53 with respect to the driven pulley 70 becomes small, and the rear wheel 15R is rotationally driven at a high speed.

According to the V-belt type stepless speed changer 50 as described above, the following effects can be obtained.

(a) The drive unit 90 that activates the groove width variable mechanism 80 and the power transmission unit 100 that transmits the power of the drive unit 90 to the groove width variable mechanism 80 are disposed in the drive drive pulley 60 and are driven. Since the pulley 70 and the V-belt 53 are inside the casing 40, the sealing property can be easily ensured and the casing 40 can be miniaturized. In particular, since the drive unit 90 and the power transmission unit 100 of the groove width variable mechanism 80 are entirely covered by the casing 40, the sealing property between the drive unit 90 and the power transmission unit 100 can be easily ensured. Further, by disposing the drive unit 90 and the power transmission unit 100 between the main shaft 51 and the sub-shaft 52, the protrusion of the casing 40 can be suppressed, and the size of the casing 40 can be reduced.

(b) The drive unit 90 includes: a motor portion M1 that houses the motor M as a drive source; and an output shaft 91 of the drive unit 90 that is actuated by the power of the motor M; and the output shaft 91 is coupled to the spindle 51 or The counter shafts 52 are kept in parallel, so that the drive unit 90 can be easily brought close to the main shaft 51 or the counter shaft 52. Therefore, the power transmission unit 100 that transmits the power of the drive unit 90 to the groove width variable mechanism 80 can be miniaturized. As a result, the V-belt type stepless speed change machine 50 can be miniaturized.

(c) the front end 91a of the output shaft 91 of the drive unit 90 is protruded toward the V-belt 53 side toward the motor portion M1, and at least a portion 91c of the output shaft 91 is viewed from a direction orthogonal to the output shaft 91. It is disposed in the belt width W of the V-belt 53, so that the amount of protrusion of the driving unit 90 toward the main shaft 51 can be reduced by the amount corresponding to the overlapping portion of the belt width W and the output shaft 91, and the V-belt can be made. The stepless speed change machine 50 is miniaturized. Further, since the motor portion M1 of the drive unit 90 is disposed outside the belt width W, the interference between the V-belt 53 and the motor portion M1 can be surely prevented, and the output shaft 91 is viewed from the axial direction of the output shaft 91. Since the main shaft 51 and the counter shaft 52 are connected to each other in the rotation locus 53i of the V-belt 53, the V-belt 53 and the output shaft 91 can be prevented from interfering when the V-belt 53 is bent.

(d) The drive unit 90 is configured to include a reduction gear set 92 that transmits the power of the motor M to the output shaft 91, and the reduction gear set 92 is disposed outside the belt width W of the V-belt 53 while being from the axis of the output shaft 91. When viewed in the direction, the reduction gear set 92 overlaps with the V-belt 53, so that even in the case where the drive unit 90 includes the reduction gear set 92, the reduction gear group portion can be prevented from interfering with the V-belt 53, and the output shaft can be prevented. When viewed in the axial direction of 91, since the reduction gear set 92 overlaps with the V-belt 53, the V-belt stepless transmission 50 can be miniaturized.

The embodiment of the present invention has been described above, but the present invention is not limited to the above embodiment, and modifications may be appropriately made within the scope of the gist of the invention.

10. . . Two-wheeled vehicle

11. . . Frame

11h. . . Front tube

11s. . . Mounts

12. . . Pivot

13. . . Rear shock absorber unit

14. . . Fork

15. . . Steering handle

15F. . . Front wheel

15R. . . rear wheel

16. . . Seat

17. . . storage box

18. . . Fuel tank

20. . . Power unit

30. . . engine

30c. . . Camshaft for pneumatic valve

30p. . . Mars plug

31. . . Crank axle box

31b. . . Bearing department

31c. . . Crankshaft

31e. . . Crank axle cover

31g. . . generator

32. . . cylinder block

32c. . . link

32p. . . piston

33. . . Cylinder head

33c. . . Combustion chamber

34. . . Cylinder head cover

35. . . Intake pipe

35a. . . Fuel supply device

35c. . . air purifier

36. . . Exhaust

40. . . Gearbox

40C. . . Gear box cover

40G, 94. . . Gearbox

40L. . . Left box

40LC. . . Side cover

40R. . . Right box

41. . . Installation department

42, 95, 131, 132. . . Screw

50. . . V-belt type stepless speed changer

51. . . Spindle

51a. . . Large diameter department

51b. . . Support Department (small diameter department)

51d. . . Step difference

52. . . Secondary shaft

52g. . . gear

53. . . V-belt

53i. . . Within the rotation track

54. . . Centrifugal clutch

55. . . Rear axle

60. . . Drive pulley

61, 71. . . Fixed pulley

62, 72. . . Movable pulley

63. . . Hub

63a. . . Opposite face

64. . . Torque communication surface

65, 112d. . . hole

66. . . Cushion member

66a. . . Inner peripheral wall

66b. . . Two side walls

66b1. . . Outer side

66c. . . Bottom wall

66d. . . Protrusion

67. . . Cylinder member

67a. . . One end of the cylindrical member 67

67b. . . The other end of the cylindrical member 67

68. . . Double nut

69. . . Bearing

70. . . Driven pulley

73. . . Coil spring

80. . . Groove width variable mechanism

90. . . Drive unit

91. . . Output shaft

91a. . . Front end face

91b. . . Ball screw (internal thread)

91c. . . At least a portion of the output shaft 91

91e. . . Front end face

92. . . Reduction gear set

92e. . . Last gear

93. . . Ball screw (external thread)

100. . . Power transmission department

110. . . Torque transmission department

111. . . Radial direction part

111a. . . Circular plate

112. . . Axis direction part

120. . . Engaging member

121. . . Clamping department

122. . . Snap ring

123. . . Engagement slot

130. . . Connecting member

133. . . Linkage

141. . . Large diameter gear

142. . . gear

143. . . big gear

c. . . Chain

L1. . . line

M. . . motor

M1. . . Motor department

W. . . Belt width

X1, X2. . . arrow

Fig. 1 is a side view showing a scooter type two-turbine vehicle as an example of an embodiment of a V-belt type stepless speed changer according to the present invention.

2 is a side view of a power unit including a V-belt type stepless speed changer in the above two-wheeled vehicle.

Figure 3 is a cross-sectional view taken along the line III-III of Figure 2;

Figure 4 is a partial enlarged view of Figure 3.

Fig. 5 is a view showing a partial V arrow of Fig. 3 omitted.

FIG. 6 is an exploded perspective view showing a main part of the torque transmitting unit 110.

20. . . Power unit

30. . . engine

30c. . . Camshaft for pneumatic valve

30p. . . Mars plug

31. . . Crank axle box

31b. . . Bearing department

31c. . . Crankshaft

31e. . . Crank axle cover

31g. . . generator

32. . . cylinder block

32c. . . link

32p. . . piston

33. . . Cylinder head

33c. . . Combustion chamber

34. . . Cylinder head cover

40. . . Gearbox

40C. . . Gear box cover

40G, 94. . . Gearbox

40L. . . Left box

40LC. . . Side cover

40R. . . Right box

41. . . Installation department

42, 95. . . Screw

50. . . V-belt type stepless speed changer

51. . . Spindle

51a. . . Large diameter department

52. . . Secondary shaft

52g. . . gear

53. . . V-belt

54. . . Centrifugal clutch

55. . . Rear axle

60. . . Drive pulley

70. . . Driven pulley

71. . . Fixed pulley

72. . . Movable pulley

73. . . Coil spring

90. . . Drive unit

92. . . Reduction gear set

100. . . Power transmission department

120. . . Engaging member

130. . . Connecting member

141. . . Large diameter gear

142. . . gear

143. . . big gear

c. . . Chain

M1. . . Motor department

Claims (3)

A V-belt type stepless speed change machine comprising: a driving pulley supported on a main shaft; a driven pulley supported on a counter shaft disposed in parallel with the main shaft; and being mounted on the driving pulley and the driven pulley a V-belt; a casing for accommodating the driving pulley, the driven pulley and the V-belt; and a groove width changing mechanism for changing a groove width of the driving pulley and/or the driven pulley; a drive unit that is actuated by a variable mechanism; and a power transmission unit that transmits the power of the drive unit to the groove width variable mechanism; the V-belt type stepless speed changer is characterized in that the drive unit and the power transmission unit a drive line disposed between the main shaft and the counter shaft, wherein the drive unit includes a motor portion that houses a motor as a drive source, and an output shaft of the drive unit that is actuated by the power of the motor, and the output The shaft is arranged in parallel with the above-mentioned main shaft or counter shaft. The V-belt type stepless speed changer according to the first aspect of the invention, wherein the front end of the output shaft protrudes toward the V-belt side from the motor portion, and is viewed from a direction orthogonal to the output shaft. At least a part of the output shaft is disposed in a belt width of the V-belt, and the motor portion is disposed outside the belt width, and the output shaft is disposed in a V-shape when viewed from an axial direction of the output shaft. The rotation path of the belt connects the above-mentioned main shaft and the sub-axis. For example, the V-belt type stepless speed changer of claim 2, wherein The driving unit includes a reduction gear set that transmits power of the motor to the output shaft, the reduction gear set is disposed outside a belt width of the V-belt, and the reduction gear set is viewed from an axial direction of the output shaft. It overlaps with the above V-belt.