JP2010201988A - V-belt type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce inertia moment around a pivot shaft by arranging a driving unit adjacently to the pivot shaft on an outer periphery of a driving pulley. <P>SOLUTION: In this V-belt type continuously variable transmission, the pivot shaft 12 for oscillatably supporting a transmission case 40 on a vehicle body frame is arranged on an outer periphery of the driving pulley 60 from the viewpoint of an axis direction of the driving pulley 60, a motor shaft M2 of the driving unit 90 for operating a groove width variable mechanism is arranged in parallel with the pivot shaft 12, and the driving unit 90 is arranged to be adjacent to the pivot shaft 12 on the outer periphery of the driving pulley 60. The pivot shaft 12 is provided on an upper side and a front side of a crankshaft center. A cylinder 32 of an engine including a crankshaft is provided from a front part of the transmission case 40 toward the front. The driving unit 90 is arranged on a side of the cylinder 32. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a V-belt type continuously variable transmission.

Conventionally, for example, as seen in Patent Document 1 (FIG. 2), as a V-belt type continuously variable transmission, it is supported by a drive pulley (3) supported by a crankshaft (1) and a driven shaft (2). A driven pulley (4), a V belt (5) stretched between the driving pulley (3) and the driven pulley (4), the driving pulley (3), the driven pulley (4), and a V belt (5) A transmission case (100, 101) that houses the movable pulley (3B) in the drive pulley (3) is slid in the axial direction of the crankshaft (1), thereby forming a groove in the drive pulley (3). A drive having a groove width variable mechanism (8) for changing the width, a motor 10 as a drive source for operating the groove width variable mechanism (8), and an output unit (11D (FIG. 4)) driven by the motor 10 Unit (500) and this drive unit ( Power transmission unit for transmitting power said to groove width varying mechanism (8) 00) (12 etc.) and the V-belt type continuously variable transmission having a are known.
For example, as can be seen in Patent Document 2, there is known a V-belt type continuously variable transmission in which the shaft of a motor (91) that is a drive source for operating a variable groove width mechanism is arranged in parallel with a pivot shaft.

JP 2006-022929 A JP 2007-024240 A

In the conventional V-belt type continuously variable transmission described above, a motor or a drive unit including a motor, which is a drive source for operating the variable groove width mechanism, is disposed at a position away from the pivot shaft.
Therefore, there is a problem that the moment of inertia around the pivot axis tends to increase.
An object of the present invention is to provide a V-belt continuously variable transmission that solves the above-described problems and can reduce the moment of inertia around the pivot shaft.

In order to achieve the above object, a V-belt type continuously variable transmission according to the present invention includes a drive pulley supported by a crankshaft, a driven pulley supported by a driven shaft, and a suspension between the drive pulley and the driven pulley. The groove width of the drive pulley is changed by sliding the passed V belt, the drive pulley, the driven pulley, and the transmission case containing the V belt, and the movable pulley in the drive pulley in the axial direction of the crankshaft. A V-belt type continuously variable transmission including a variable groove width mechanism, a motor that is a drive source for operating the variable groove width mechanism, and a drive unit having an output unit driven by the motor,
A pivot shaft for swingably supporting the transmission case with respect to the vehicle body frame is disposed on an outer periphery of the drive pulley when viewed from the axial direction of the drive pulley;
The motor shaft of the drive unit is disposed in parallel with the pivot shaft, and the drive unit is disposed adjacent to the pivot shaft on the outer periphery of the drive pulley.
According to this V-belt type continuously variable transmission, the drive unit that includes the motor and is heavier than the motor alone is disposed adjacent to the pivot shaft on the outer periphery of the drive pulley. Can be reduced. Reduction of the moment of inertia around the pivot axis improves the swingability of the transmission case that operates as a swing unit.
In the technique described in Patent Document 1, since the drive unit is disposed so that the motor shaft is orthogonal to the pivot shaft, it is difficult to make the drive unit adjacent to the pivot shaft. For example, by arranging the motor shaft of the drive unit in parallel with the pivot shaft, the drive unit can be adjacent to and close to the pivot shaft.
Preferably, the pivot shaft is provided above and in front of the crankshaft center when viewed from the axial direction of the crankshaft, and an engine cylinder having the crankshaft is provided from the front of the transmission case toward the front. The drive unit is arranged on the side of the cylinder.
With this configuration, the rotation range of the drive unit around the pivot axis can be prevented from exceeding the rotation range of the cylinder that also rotates around the pivot axis, or at least the drive unit of the drive unit exceeding the rotation range of the cylinder can be prevented. The amount of the rotation range can be reduced. Accordingly, it is possible to prevent the drive unit from interfering with a portion that does not rotate around the pivot axis, for example, a body frame or a storage box.
More preferably, the drive unit is fixed to a bracket provided on a side surface of the cylinder.
If comprised in this way, the support structure of a drive unit can be simplified.
Preferably, when viewed from the axial direction of the crankshaft, the pivot shaft is provided above and in front of the center of the crankshaft, and an output portion of the drive unit is provided on a vertical line passing through the crankshaft. A power transmission unit that transmits the power of the output unit to the groove width variable mechanism is provided on the line.
With this configuration, since the moment component due to gravity acting on the power transmission unit can be reduced, the motor and components in the drive unit can be reduced in size, and as a result, the drive unit and the entire V-belt type continuously variable transmission can be reduced in size. Can be achieved.

The side view which shows the scooter type motorcycle as an example using one Embodiment of the V-belt type continuously variable transmission which concerns on this invention. FIG. 3 is a side view of a power unit including a V-belt type continuously variable transmission in the motorcycle. Partial omission III-III sectional drawing in FIG. The elements on larger scale of FIG. FIG. 4 is a partially omitted V arrow view in FIG. 3. FIG. 3 is an exploded perspective view showing a main part of a torque transmission unit 110. The partial abbreviation plane sectional view showing a modification. The partial omission side view which shows another modification.

Embodiments of a V-belt type continuously variable transmission according to the present invention will be described below with reference to the drawings.
FIG. 1 is a side view showing a scooter-type motorcycle as an example using an embodiment of a V-belt continuously variable transmission according to the present invention, and FIG. 2 shows a V-belt continuously variable transmission in the motorcycle. FIG. 3 is a partially omitted III-III sectional view in FIG.
As shown in FIG. 1, the motorcycle 10 includes a pivot unit 12 and a rear cushion unit 13 at a rear portion of a body frame 11, and a power unit (swing unit) 20 can swing around the pivot shaft 12 with respect to the body frame 11. It is a vehicle suspended on. A front fork 14 is attached to the head pipe 11h so as to be steerable, and a front wheel 15F is attached to the lower end of the front fork 14. A steering handle 15 is attached to the top of the front fork 14.
The body frame 11 has a pair of left and right seat frames 11s (only one is shown) at the rear. A seat 16 on which the occupant sits is provided on the seat frame 11 s, and a storage box 17 that opens upward is provided below the seat 16. A fuel tank 18 is disposed behind the storage box 17.

  The power unit (swing unit) 20 includes an engine 30 as a drive source and a transmission case 40 provided behind the engine 30. The transmission case 40 incorporates a V-belt type continuously variable transmission 50 that transmits the driving force of the engine 30 to the rear wheels 15R. The power unit 20 is swingably attached to the rear end portion of the vehicle body frame 11, and the power of the engine 30 is transmitted to the rear wheel 15 </ b> R via the V-belt type continuously variable transmission 50 in the transmission case 40. Therefore, the power unit 20 also serves as a rear swing arm.

As shown mainly in FIG. 3, the engine 30 includes a crankcase 31, a cylinder block 32, a cylinder head 33, and a cylinder head cover 34. A cylinder block 32 oriented 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.
A crankshaft 31c is rotatably supported by ball bearings 31b and 31b held by the crankcase 31, and a piston 32p is slidably provided in the cylinder block 32. The crankshaft 31c and the piston 32p are connected by a connecting rod 32c, and the crankshaft 31c is rotated by the reciprocating motion of the piston 32p. The crankshaft 31c constitutes a primary shaft (drive shaft) 51 described later. An intake pipe 35 (FIG. 1) and an exhaust pipe 36 (FIG. 1) communicating with the combustion chamber 33c are connected to the cylinder head 33. As shown in FIG. 2, a fuel supply device 35 a and an air cleaner 35 c are connected to the intake pipe 35. A silencer (not shown) is connected to the exhaust device 36.

  In FIG. 3, 30p is an ignition plug, 30c is provided in the cylinder head cover 34, and is a camshaft for valve drive that is rotationally driven from the crankshaft 31c via the chain c, and 31g is around the crankshaft 31c in the crankcase cover 31e. Is a generator having a stator and a rotor fixed to the crankshaft 31c.

  As shown in FIG. 3, a transmission case (also simply referred to as a case) 40 is configured as a case that forms a part of the power unit 20 described above. The case 40 has a right case 40R and a left case 40L coupled thereto. The right case 40R is manufactured integrally with the crankcase 31. A gear box cover 40C constituting a gear box (40G) for reducing the rotation of the secondary shaft (driven shaft) 52 and transmitting it to the rear wheel shaft 55 is coupled to the rear portion of the right case 40R.

4 is a partially enlarged view of FIG. 3, and FIG. 5 is a partially omitted V arrow view of FIG.
As shown mainly in FIG. 3, a V-belt type continuously variable transmission 50 includes a drive pulley 60 supported by a primary shaft (drive shaft) 51 that is a first pulley shaft, and a secondary shaft that is a second pulley shaft. A driven pulley 70 supported by the (driven shaft) 52 and a V-belt 53 stretched between the driving pulley 60 and the driven pulley 70 are provided. The V belt type continuously variable transmission 50 includes a case 40 that houses the drive pulley 60, the driven pulley 70, and the V belt 53, and a groove width variable mechanism 80 that changes the groove width of the drive pulley 60 (see FIG. 4), a drive unit 90 for operating the variable groove width mechanism 80, and a power transmission unit 100 for transmitting the power of the drive unit 90 to the variable groove width mechanism 80.
Hereinafter, the configuration of the V-belt type continuously variable transmission 50 will be sequentially described.

As shown in FIGS. 3 and 4, in this embodiment, the drive shaft (primary shaft) 51 is constituted by the crankshaft 31c as described above.
The primary shaft 51 includes a large-diameter portion 51a that is supported at both ends by bearings 31b and 31b, which are bearing members, and a support portion for the movable pulley 62 in the drive pulley 60 that is provided on the large-diameter portion 51a via a step portion 51d. And a small-diameter portion 51b.

As shown in FIG. 4, the drive pulley 60 is provided with a groove width variable mechanism 80.
The drive pulley 60 includes a fixed pulley (fixed half) 61 that does not move in the axial direction of the primary shaft (pulley shaft) 51, and a movable pulley (movable half) that is movable in the axial direction with respect to the primary shaft 51 and is relatively non-rotatable. Body) 62.
The groove width variable mechanism 80 changes the groove width of the pulley 60, that is, the distance between the fixed pulley 61 and the movable pulley 62 by sliding the movable pulley 62 in the axial direction along the support portion 51 b of the movable pulley 62 in the pulley shaft 51. It is a mechanism to do.
The groove width variable mechanism 80 is provided on the torque transmission part 110 that is not rotatable relative to the pulley shaft 51 and the movable pulley 62, and the boss part 63 that transmits torque between the torque transmission part 110. And have.

FIG. 6 is an exploded perspective view showing a main part of the torque transmission unit 110.
As shown in FIGS. 4 to 6, the torque transmitting portion 110 includes a radial portion 111 extending in the radial direction of the pulley shaft 51, and an axial portion extending integrally with the radial portion 111 and extending in the axial direction. 112. The axial direction portion 112 is located on the outer side in the radial direction from the surface 63a of the movable pulley 62 facing the support portion 51b of the movable pulley 62 on the pulley shaft 51 (in this embodiment, the inner peripheral surface of the boss portion 63). Yes. A plurality of axial direction portions 112 (three in this embodiment at an equal pitch in the circumferential direction) are provided.

Although the torque transmission part 110 can be formed integrally with the primary shaft 51, in this embodiment, the torque transmission part 110 is constituted by a member separate from the pulley shaft 51 (this member is also referred to as a torque transmission member). It is.
The radial direction portion 111 of the torque transmitting portion 110 has a shape in which the disk-like portion 111a is radially extended at three locations in the radial direction, and the axial direction portion 112 is integrally formed at the tip of the extended portion. Yes.

The boss portion 63 of the movable pulley 62 is provided with a torque transmission surface 64 through which torque is transmitted to the axial direction portion 112 of the torque transmission portion 110. The torque transmission surface 64 can move relative to the axial portion 112 in the axial direction.
The boss portion 63 of the movable pulley 62 is provided with a hole 65 into which the axial portion 112 of the torque transmission portion 110 is inserted. The hole 65 has a fan-shaped cross section and corresponds to the cross section of the axial portion 112 and is substantially coincident. An end surface of the hole 65 in the circumferential direction forms a torque transmission surface 64. As described above, the axial direction portion 112 is positioned outside the inner peripheral surface 63a of the boss portion 63 in the radial direction while being inserted into the hole 65 of the boss portion 63.

Synthetic resin (for example, polyamide resin (for example, PA66) is mixed with a curing material (for example, carbon) between the axial direction portion 112 of the torque transmitting unit 110 and the torque transmission surface 64 of the boss portion 63 to obtain a desired hardness. The shock absorbing member 66 of the material) is provided.
The buffer member 66 is mounted on the inner side of the tip end portion of the axial direction portion 112 in the torque transmitting portion 110 and has a shape suitable for the tip end portion of the axial direction portion 112. The buffer member 66 shown in FIG. 6 includes a curved inner peripheral wall portion 66a, both side wall portions 66b and 66b, a bottom wall portion 66c, and a projection 66d protruding outward in the radial direction at the inner peripheral wall portion 66a. It is an integral molded product.

A hole 112d is provided in the axial direction portion 112 of the torque transmitting portion 110.
The buffer member 66 is configured such that the projection 66d of the inner peripheral wall portion 66a is fitted into the hole 112d of the axial direction portion 112, and the inner peripheral wall portion 66a is joined to the inside of the tip end portion of the axial direction portion 112 to thereby connect the axial direction portion 112. It is attached to the tip part of.
The axial portion 112 is inserted into the hole 65 of the boss portion 63 together with the buffer member 66 in a state where the buffer member 66 is mounted. In a state where the buffer member 66 is inserted into the hole 65, the outer surface 66 b 1 of the side wall portion 66 b of the buffer member 66 constitutes a torque transmission surface that contacts the torque transmission surface 64 of the boss portion 63.

  The buffer member 66 is slidable in the axial direction in the hole 65 of the boss portion 63 together with the axial portion 112, but the projection 66d of the buffer member 66 and the hole 112d of the axial portion 112 are engaged with each other. Even if the direction portion 112 slides, the buffer member 66 does not come off the axial direction portion 112.

  6 shows a configuration in which the buffer member 66 is mounted inside the tip end portion of the axial portion 112, the buffer member 66 may be mounted outside the tip portion of the axial portion 112. it can. Further, the buffer member 66 may not be mounted on the axial direction portion 112. In this case, the side surface of the axial direction portion 112 constitutes a torque transmission surface that contacts the torque transmission surface 64 of the boss portion 63. To do.

  5 and 6, 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 51 b of the pulley shaft 51. As shown in FIG. 4, a double nut 68 is attached to the tip of the small diameter portion 51b, and the torque transmission member 110, the cylindrical member 67, and the fixed member are fixed between the double nut 68 and the step portion 51d of the primary shaft 51. The pulley 61 is fastened together and fixed on the small diameter part 51b. That is, the torque transmission member 110 is fixed to the pulley shaft 51 so as not to rotate relative to each other by the radial portion 111 being sandwiched between the one end 67a of the cylindrical member 67 and the stepped portion 51d. The fixed pulley 61 is fixed to the pulley shaft 51 so as not to rotate relative to the pulley shaft 51 by being sandwiched between the other end 67 b of the cylindrical member 67 and the double nut 68.

As described above, the movable pulley 62 is attached to the pulley shaft 51 so as not to rotate relative to the pulley shaft 51 and to be slidable by inserting the axial direction portion 112 of the torque transmitting portion 110 into the hole 65 of the boss portion 63.
As shown in FIGS. 4 and 5, an engaging member 120 is disposed on the outer periphery of the boss portion 63 of the movable pulley 62 to slide the movable pulley 62. The engaging member 120 will be described in detail later together with the power transmission unit 100.

As shown in FIGS. 4 and 5, the drive unit 90 includes a motor unit M1 (FIG. 4) in which a motor (servo motor) M (FIG. 5) as a drive source is housed, An output shaft 91 that forms an output portion of the drive unit 90 is provided, and the output shaft 91 is arranged in parallel with the primary shaft 51.
The drive unit 90 includes a reduction gear train 92 that transmits the power of the motor M to the output shaft 91. A ball screw (male screw) 93 is concentrically coupled to the gear 92e at the final stage of the reduction gear train 92. The base side of the output shaft 91 is formed in a cylindrical shape, and a ball screw (female screw) 91 b is formed on the inner surface thereof, and this female screw 91 b is screwed into the ball screw (male screw) 93. Therefore, when the ball screw 93 rotates through the reduction gear train 92 by driving 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) according to the rotation direction.

The drive unit 90 is fixed to the transmission case 40 by tightening a gear case 94 containing the reduction gear train 92 to a mounting portion 41 (FIG. 3) provided in the transmission case 40 with a screw 95.
As shown in FIGS. 2 and 5, in this embodiment, the drive pulley 60 is viewed from the axial direction of the drive pulley 60 with respect to the pivot shaft 12 that supports the transmission case 40 so as to be swingable with respect to the vehicle body frame 11. The motor shaft M2 of the drive unit 90 is disposed parallel to the pivot shaft 12, and the drive unit 90 is disposed adjacent to and adjacent to the pivot shaft 12 on the outer periphery of the drive pulley 60.

  The pivot shaft 12 is provided above and in front of the center of the crankshaft 51 when viewed from the axial direction of the crankshaft 51 (31c), and a cylinder (such as a cylinder block 32) of the engine 30 including the crankshaft 51 is provided in the transmission case 40. The drive unit 90 is arranged on the side of the cylinder.

2, 3, and 5, the drive unit 90 is fastened and fixed to the mounting portion 41 provided on the transmission case 40 with screws 95, but is provided on the side surface of the cylinder, for example, as shown in FIG. 7. It can also be set as the structure fixed to the bracket 37. FIG.
If comprised in this way, the support structure of the drive unit 90 can be simplified.
In FIG. 7, 32 b is a bracket fixing portion provided on the side portion of the cylinder block 32. The bracket 37 has a base portion 37b fixed to the fixing portion 32 with screws (not shown), and a plurality (three in the drawing) column portions 37c provided from the base portion 37b to the side. Then, the drive unit 90 is fastened and fixed to the front end of the column portion 37c with a screw 95.

  The pivot shaft 12 can be provided above and behind the center of the crankshaft 51 when viewed from the axial direction of the crankshaft 51 (31c), as indicated by a virtual line 12 ′ in FIG. As indicated by 12 ″, it can also be provided below and in front of the center of the crankshaft 51.

As shown in FIGS. 4 and 5, the power transmission unit 100 is for transmitting the power of the drive unit 90 to the groove width variable mechanism 80, and includes the engaging member 120 and the connecting member 130. Yes. The engaging member 120 and the connecting member 130 are coupled by a screw 131. The connecting member 130 is coupled to the output shaft 91 with a screw 132. Therefore, when the output shaft 91 advances and retracts, the engaging member 120 and the connecting member 130 also advance and retract together.
As shown in FIG. 4, the connecting portion 133 of the connecting member 130 with the output shaft 91 is connected to the tip surface 91 e of the output shaft 91.

  As shown in FIG. 5, the engaging member 120 has 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 is fixed to the outer periphery of the boss portion 63 of the movable pulley 62 so as not to slide in the axial direction of the boss portion 63. Similarly, an engagement ring 122 is fixed to the outer periphery of the bearing 69 so as not to slide in the axial direction. A ring-shaped engagement groove 123 is provided on the outer periphery of the engagement ring 122, and the engagement portion 121 of the engagement member 120 is engaged with the engagement groove 123. Thus, in the illustrated example, the engaging portion 121 of the engaging member 120 is indirectly engaged with the boss portion 63 of the movable pulley 62 (via the engaging ring 122 and the bearing 69). It is also possible to directly engage the joint portion 121 with the boss portion 63.

  As shown in FIG. 4, the engaging portion 121 is connected 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. Adjacent to each other. That is, the engaging part 121 is arranged as close as possible to the bearing part 31b. The engaging portion 121 is preferably engaged with the boss portion 63 of the movable pulley 62 at at least two positions facing each other across the pulley shaft 51. In this embodiment, the engaging portion 121 is related to the pulley shaft 51 ( In other words, they are engaged at two points symmetrically with respect to the rotation center of the boss portion 63.

When the pivot shaft 12 is provided above and in front of the center of the crankshaft 51 when viewed from the axial direction of the crankshaft 51 (31c), for example, as shown in FIG. May be provided on a vertical line passing through the crankshaft 51, and a power transmission unit 100 for transmitting the power of the output unit 91 to the groove width variable mechanism 80 may be provided on the vertical line. The constituent members of the power transmission unit 100 are as described above.
With this configuration, since the moment component caused by gravity acting on the power transmission unit 100 can be reduced, the motor M, the motor shaft, the reduction gear train 92, and the support unit thereof in the drive unit 90 can be downsized. As a result, the drive unit 90 and the V-belt type continuously variable transmission 50 as a whole can be reduced in size.

As shown in FIG. 3, the secondary shaft 52 that is the driven shaft of the V-belt type continuously variable transmission 50 is rotatably supported by the left case 40L of the case 40 and the gear box cover 40C. A driven pulley 70 is provided on the secondary shaft 52 via a centrifugal clutch 54.
The driven pulley 70 includes a fixed pulley (fixed half) 71 and a movable pulley (movable half) 72. An endless V-belt 53 is stretched between the driving pulley 60 and the driven pulley 70, and the rotation of the driving pulley 60 is transmitted to the driven pulley 70. When the rotational speed of the driven pulley 70 exceeds the predetermined rotational speed, the centrifugal clutch 54 provided between the driven pulley 70 and the secondary shaft 52 is connected, and the secondary shaft 52 starts to rotate.

A gear train (gear box) 40G that decelerates the rotation of the secondary shaft 52 and transmits it to the rear wheel shaft 55 includes a gear 52g provided on the secondary shaft 52, a large-diameter gear 141 that meshes with the gear 52g, and the large gear. A small gear 142 having a smaller diameter than 141 and rotating with the large gear 141 and a large gear 143 meshing with the small gear 142 are provided. The large gear 143 is attached to the rear wheel shaft 55 so as not to be relatively rotatable.
Therefore, the rotation of the secondary shaft 52 is decelerated and transmitted to the rear wheel shaft 55, and the rear wheel 15R (FIG. 1) attached to the rear wheel shaft 55 is driven.

  The movable pulley 72 in the driven pulley 70 is attached to the secondary shaft 52 so as to be movable in the axial direction. The movable pulley 72 is urged in a direction approaching the fixed pulley 71 by a coil spring 73, and moves in the axial direction according to the tension acting on the V belt 53. That is, when the movable pulley 62 of the driving pulley 60 is displaced in the direction of narrowing the groove width and the winding diameter of the V belt 53 around the driving pulley 60 increases, the V belt wound around the driven pulley 70 correspondingly. 53 is pulled toward the drive pulley 60 and the tension acting on the V-belt 53 is increased. With this increase in tension, the movable pulley 72 of the driven pulley 70 is displaced in the direction of increasing the groove width, and the V-belt to the driven pulley 70 is increased. The winding diameter of 53 becomes small and the secondary shaft 52 rotates at high speed. When the movable pulley 62 of the driving pulley 60 is displaced in the direction of widening the groove width, the operation is reversed, and the secondary shaft 52 rotates at a low speed.

  When the drive unit 90 operates under the control of a control unit (not shown) and the output shaft 91 protrudes in the direction of the arrow X1 in FIG. 4 and the movable pulley 62 slides in the X1 direction, the distance between the fixed pulley 61 and the movable pulley 62 increases. As a result, the winding diameter of the V belt 53 around the driving pulley 60 decreases and the winding diameter of the V belt 53 around the driven pulley 70 increases, so that the rear wheel 15R is driven to rotate at a low speed so that it can withstand high loads. The Rukoto. Conversely, when the output shaft 91 slides in the direction of the arrow X2 and the movable pulley 62 slides in the X2 direction, the distance between the fixed pulley 61 and the movable pulley 62 becomes narrow, and the winding diameter of the V belt 53 around the drive pulley 60 is reduced. Becomes larger and the winding diameter of the V-belt 53 around the driven pulley 70 becomes smaller, and the rear wheel 15R is rotationally driven at a high speed.

According to the V-belt type continuously variable transmission 50 as described above, the following operational effects can be obtained.
(A) A pivot shaft 12 that supports the transmission case 40 in a swingable manner with respect to the vehicle body frame 11 is disposed on the outer periphery of the drive pulley 60 when viewed from the axial direction of the drive pulley 60, and the motor shaft M2 of the drive unit 90 is disposed. Is disposed in parallel with the pivot shaft 12 and the drive unit 90 is disposed adjacent to the pivot shaft 12 on the outer periphery of the drive pulley 60, so that the drive unit 90 including the motor M and heavier than the motor alone is driven. The outer periphery of the pulley 60 is disposed adjacent to the pivot shaft 12.
Therefore, the moment of inertia around the pivot shaft 12 can be reduced. Reduction of the moment of inertia around the pivot shaft 12 is a swing arm that supports the rear wheel 15R, and improves the swingability of the transmission case 40 that operates as a swing unit.
In the technique described in Patent Document 1, since the drive unit is arranged so that the motor shaft is orthogonal to the pivot shaft, it is difficult to make the drive unit adjacent to the pivot shaft. According to the above, by arranging the motor shaft M2 of the drive unit 90 in parallel with the pivot shaft 12, the drive unit 90 can be adjacent to and close to the pivot shaft 12.
(B) As viewed from the axial direction of the crankshaft 51, the pivot shaft 12 is provided above and forward of the center of the crankshaft, and the cylinder (32, etc.) of the engine 30 including the crankshaft is forwarded from the front of the transmission case 40. Since the drive unit 90 is disposed on the side of the cylinder, the rotation range of the drive unit 90 around the pivot shaft 12 exceeds the rotation range of the cylinder that also rotates around the pivot shaft 12. Or at least the amount of rotation range of the drive unit 90 exceeding the rotation range of the cylinder as shown in the figure can be reduced. When viewed from the axial direction of the pivot shaft 12, the overlap portion of the drive unit 90 with the cylinder does not exceed the rotation range of the cylinder that rotates about the pivot shaft 12. Since it is a part other than the overlapping part and is a little part compared to the overlapping part, the amount of the rotation range of the drive unit 90 exceeding the rotation range of the cylinder should be reduced. It becomes.
Therefore, according to this embodiment, it is possible to prevent the drive unit 90 from interfering with a portion that does not rotate around the pivot shaft 12, for example, the vehicle body frame 11 and the storage box 17 shown in FIG. In other words, the capacity of the storage box 17 can be increased accordingly.
(C) As described above, when the drive unit 90 is fixed to the bracket 37 provided on the side surface of the cylinder, the support structure of the drive unit 90 can be simplified.
(D) As described above, when viewed from the axial direction of the crankshaft 51, the pivot shaft 12 is provided above and in front of the center of the crankshaft 51, and the output portion 91 of the drive unit 90 passes vertically through the crankshaft 51. If the power transmission unit 100 is provided on the line and the power transmission unit 100 that transmits the power of the output unit 91 to the variable groove width mechanism 80 is provided on the vertical line, the moment component due to gravity acting on the power transmission unit 100 can be reduced. Therefore, the motor and components in the drive unit 90 can be reduced in size, and as a result, the drive unit 90 and the V-belt type continuously variable transmission 50 as a whole can be reduced in size.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and can be appropriately modified within the scope of the gist of the present invention.

  12 Pivot shaft, 31b Bearing part, 40 Transmission case, 50 V belt type continuously variable transmission, 51 Crankshaft, 51a Large diameter part, 51b Support part (small diameter part), 51d Step part, 52 Drive shaft, 53 V belt , 60 drive pulley, 62 movable pulley, 63 boss, 63a facing surface, 64 torque transmission surface, 66 buffer member, 67 cylindrical member, 70 driven pulley, 80 groove width variable mechanism, 90 drive unit, 91 output shaft, 91a tip Surface, 92 reduction gear train, 100 power transmission part, 110 torque transmission part, 111 radial direction part, 112 axial direction part, 120 engagement member, 121 engagement part, 130 connection member, 133 connection part.

Claims (4)

Accommodates a drive pulley supported by the crankshaft, a driven pulley supported by the driven shaft, a V-belt stretched between the driving pulley and the driven pulley, and the driving pulley, the driven pulley, and the V-belt. A transmission case, a variable groove width mechanism for changing the groove width of the drive pulley by sliding the movable pulley in the drive pulley in the axial direction of the crankshaft, and a drive source for operating the variable groove width mechanism. A V-belt continuously variable transmission including a motor and a drive unit having an output unit driven by the motor,
A pivot shaft for swingably supporting the transmission case with respect to the vehicle body frame is disposed on an outer periphery of the drive pulley when viewed from the axial direction of the drive pulley;
A V-belt type continuously variable transmission characterized in that a motor shaft of the drive unit is disposed in parallel with the pivot shaft, and the drive unit is disposed adjacent to the pivot shaft on the outer periphery of the drive pulley.   The pivot shaft is provided above and in front of the crankshaft center when viewed from the axial direction of the crankshaft, the engine cylinder having the crankshaft is provided from the front of the transmission case to the front, and the drive 2. The V-belt type continuously variable transmission according to claim 1, wherein the unit is disposed on a side of the cylinder.   The V-belt type continuously variable transmission according to claim 2, wherein the drive unit is fixed to a bracket provided on a side surface of the cylinder.   When viewed from the axial direction of the crankshaft, the pivot shaft is provided above and in front of the center of the crankshaft, and the output portion of the drive unit is provided on a vertical line passing through the crankshaft, on the vertical line, The V-belt type continuously variable transmission according to any one of claims 1 to 3, further comprising a power transmission unit that transmits power from an output unit to the groove width variable mechanism.

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