JP5230485B2 - V belt type continuously variable transmission - Google Patents

Description

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

  Conventionally, as seen in, for example, Patent Document 1 (FIG. 2), as a V-belt type continuously variable transmission, it is supported by a drive pulley (3) supported by a primary shaft (1) and a secondary 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) housing case (100, 101), groove width variable mechanism (8) for changing the groove width of the drive pulley (3), and drive unit (500) for operating the groove width variable mechanism (8) And a V-belt type continuously variable transmission including a power transmission unit (12, etc.) for transmitting the power of the drive unit (500) to the groove width variable mechanism (8) is known.

JP 2006-022929 A

In the conventional V-belt type continuously variable transmission described above, the drive unit (500) that operates the groove width variable mechanism (8) is disposed outside the case (100, 101).
For this reason, the power transmission part (12 etc.) disposed between the output part of the drive unit (500) (gear 11D etc. (FIG. 4 of Patent Document 1)) and the groove width variable mechanism (8) is used as the case (100 , 101) and the drive unit (500), and it is difficult to ensure the sealability, particularly the sealability between the drive unit (500) and the power transmission unit (12, etc.).
SUMMARY OF THE INVENTION An object of the present invention is to provide a V-belt continuously variable transmission that solves the above-mentioned problems and that can easily ensure sealing performance, particularly sealing performance between the drive unit of the variable groove width mechanism and the power transmission unit. There is.

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 primary shaft, a driven pulley supported by a secondary shaft, and a suspension between the drive pulley and the driven pulley. Passed V-belt, case for housing the drive pulley, driven pulley, and V-belt, variable groove width mechanism for changing the groove width of the drive pulley and / or driven pulley, and operating this variable groove width mechanism A V-belt continuously variable transmission including a drive unit to be driven and a power transmission unit that transmits power of the drive unit to the groove width variable mechanism,
The drive unit and the power transmission unit are arranged in a line connecting the primary shaft and the secondary shaft in the case ,
The drive unit includes a motor unit in which a motor that is a drive source is accommodated, and an output shaft of the drive unit that is operated by power of the motor, and the output shaft is disposed in parallel with the primary shaft or the secondary shaft. ,
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 within the belt width of the V belt as viewed from the direction orthogonal to the output shaft. The motor unit is disposed outside the belt width, and the output shaft is disposed on a line connecting the primary shaft and the secondary shaft in the rotation locus of the V belt as viewed from the axial direction of the output shaft .
According to the V-belt type continuously variable transmission, the drive unit that operates the variable groove width mechanism and the power transmission unit that transmits the power of the drive unit to the variable groove width mechanism include the drive pulley, the driven pulley, Since it is disposed in the case that accommodates the V-belt, it is easy to reduce the size of the case while ensuring sealing performance. In particular, since the entire drive unit and the power transmission unit of the variable groove width mechanism are covered with the case, it is easy to ensure a sealing property between the drive unit and the power transmission unit. Furthermore, by disposing the drive unit and the power transmission portion between the primary shaft and the secondary shaft, the protrusion of the case can be suppressed and the case can be reduced in size.
The drive unit includes a motor unit in which a motor serving as a drive source is accommodated, and an output shaft of the drive unit that is operated by power of the motor, and the output shaft is parallel to the primary shaft or the secondary shaft. Since the arrangement is such that the drive unit and the primary shaft or the secondary shaft are easily brought close to each other, the power transmission unit that transmits the power of the drive unit to the groove width variable mechanism can be reduced in size. As a result, the V belt type continuously variable transmission can be reduced in size.
Moreover, placing the tip of the output axis than said motor portion protruding toward the V-belt side, at least a portion of the output shaft as viewed from a direction perpendicular to the output shaft in the belt width of the V-belt In addition, the motor unit is disposed outside the belt width, and the output shaft is disposed on a line connecting the primary shaft and the secondary shaft in the rotation trajectory of the V belt as viewed from the axial direction of the output shaft. than there, the following effects can be obtained in further. That is,
The tip of the output shaft of the drive unit is projected toward the V-belt side from the motor portion, and at least a part of the output shaft is disposed within the belt width of the V-belt as viewed from the direction orthogonal to the output shaft. As a result, the protrusion of the drive unit in the primary shaft direction can be reduced by an amount corresponding to the overlap between the belt width and the output shaft, and the V-belt continuously variable transmission can be reduced in size accordingly. In addition, since the motor unit of the drive unit is disposed outside the belt width, interference between the V belt and the motor unit can be reliably prevented, and at the same time, the output shaft can be positioned within the rotation path of the V belt as viewed from the axial direction of the output shaft. Since it is arranged on a line connecting the primary shaft and the secondary shaft, interference between the V belt and the output shaft when the V belt is bent can be prevented.
More preferably, the drive unit includes a reduction gear train that transmits the power of the motor to the output shaft. The reduction gear train is disposed outside the belt width of the V belt, and from the axial direction of the output shaft. Accordingly, the reduction gear train is configured to overlap the V belt.
With this configuration, even when the drive unit includes a reduction gear train, interference between the reduction gear train portion and the V belt can be prevented, and the reduction gear train is overlapped with the V belt as viewed from the axial direction of the output shaft. The V-belt continuously variable transmission can be reduced in size.

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.

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, this motorcycle 10 is a vehicle in which a power unit 20 is suspended from a body frame 11 around a pivot shaft 12 by a pivot shaft 12 and a rear cushion unit 13 at a rear portion of the body frame 11. It is. 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 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 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. 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 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, the V-belt continuously variable transmission 50 is supported by a drive pulley 60 supported by a primary shaft 51 that is a first pulley shaft and a secondary shaft 52 that is a second pulley shaft. The driven pulley 70 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.

The variable groove width mechanism 80 (and therefore the power transmission unit 100 and the like) can be configured to change the groove width of the driven pulley 70 instead of the groove width of the drive pulley 60. It is also possible to change the groove width and the groove width of the driven pulley 70. Therefore, in the present application, “pulley shaft” means the first and / or second pulley shaft.
One of the features of the V-belt type continuously variable transmission 50 of this embodiment is that the drive unit 90 and the power transmission unit 100 are arranged in the case 40.
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 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, in this embodiment, 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 in 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 are provided (in this embodiment, three at equal pitches in the circumferential direction).

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 and from 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 substantially coincides with it. An end surface of the hole 65 in the circumferential direction forms a torque transmission surface 64. As described above, the axial 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 to the step 51d of the primary shaft 51 by the double nut 68. The pulley 61 is fastened together and fixed on the small diameter portion 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) serving as a drive source is accommodated, and the motor M that operates by the power of the motor M. The output shaft 91 of the drive unit 90 is provided, and the output shaft 91 is arranged in parallel with the primary shaft 51. When the groove width of the driven pulley 70 is changed by the drive unit 90, the output shaft 91 is arranged in parallel with the secondary shaft 52.
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 in the case 40 by fastening a gear case 94 containing the reduction gear train 92 to a mounting portion 41 (FIG. 3) provided in the case 40 with a screw 95. In this embodiment, the gear case 94 (that is, the drive unit 90) is covered with the side cover 40LC that forms a part of the left case 40L by being detachably attached to the left case 40L with the screw 42, whereby the drive unit 90 However, it is also possible to adopt a configuration in which the drive unit 90 and the power transmission unit 100 are accommodated in the case 40 by completely integrating the side cover 40LC with the left case 40L.

  As shown in FIG. 4, the distal end 91 a of the output shaft 91 protrudes toward the V belt 53 from the motor unit M <b> 1 of the drive unit 90, and at least a part of the output shaft 91 as viewed from the direction orthogonal to the output shaft 91. 91c is disposed within the belt width W of the V-belt. The motor unit M1 is disposed outside the belt width W. As shown in FIGS. 2 and 5, the output shaft 91 is disposed on a line L <b> 1 connecting the primary shaft 51 and the secondary shaft 52 in the rotation locus 53 i of the V belt 53 as viewed from the axial direction of the output shaft 91. is there. As shown in FIG. 4, the reduction gear train 92 is disposed outside the belt width W of the V belt 53, and as shown in FIG. 5, the reduction gear train 92 overlaps the V belt 53 when viewed from the axial direction of the output shaft 91. Arrange as follows.

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.

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) The drive unit 90 that operates the variable groove width mechanism 80 and the power transmission unit 100 that transmits the power of the drive unit 90 to the variable groove width mechanism 80 include the drive pulley 60, the driven pulley 70, and the V belt 53. Therefore, it is easy to reduce the size of the case 40 while ensuring the sealing performance. In particular, since the entire drive unit 90 and the power transmission unit 100 of the variable groove width mechanism 80 are covered with the case 40, it is easy to ensure a sealing property between the drive unit 90 and the power transmission unit 100. Become. Furthermore, by disposing the drive unit 90 and the power transmission unit 100 between the primary shaft 51 and the secondary shaft 52, the protrusion of the case 40 can be suppressed, and the case 40 can be reduced in size.
(B) The drive unit 90 includes a motor unit M1 in which a motor M as a drive source is accommodated, and an output shaft 91 of the drive unit 90 that is operated by the power of the motor M. The output shaft 91 is a primary shaft 51. Or since it is arrange | positioned in parallel with the secondary axis | shaft 52, it becomes easy to bring the drive unit 90 and the primary axis | shaft 51 or the secondary axis | shaft 52 close. Therefore, the power transmission unit 100 that transmits the power of the drive unit 90 to the groove width variable mechanism 80 can be reduced in size. As a result, the V belt type continuously variable transmission 50 can be reduced in size.
(C) The tip 91a of the output shaft 91 of the drive unit 90 is protruded toward the V-belt 53 side from the motor portion M1, and at least a part 91c of the output shaft 91 is viewed from the direction orthogonal to the output shaft 91. Since the belt 53 is disposed within the belt width W, the protrusion of the drive unit 90 in the direction of the primary shaft 51 can be reduced by an amount corresponding to the overlap between the belt width W and the output shaft 91. The step transmission 50 can be reduced in size. Moreover, since the motor unit M1 of the drive unit 90 is disposed outside the belt width W, interference between the V belt 53 and the motor unit M1 can be reliably prevented, and at the same time the output shaft 91 is viewed from the axial direction of the output shaft 91. Since it is arranged on a line connecting the primary shaft 51 and the secondary shaft 52 in the rotation locus 53i of the V belt 53, it is possible to prevent interference between the V belt 53 and the output shaft 91 when the V belt 53 is bent. it can.
(D) The drive unit 90 includes a reduction gear train 92 that transmits the power of the motor M to the output shaft 91. The reduction gear train 92 is disposed outside the belt width W of the V belt 53, and the axis of the output shaft 91 Since the speed reduction gear train 92 is overlapped with the V belt 53 as viewed from the direction, even when the drive unit 90 includes the speed reduction gear train 92, interference between the speed reduction gear train and the V belt 53 can be prevented, and the output shaft The V-belt continuously variable transmission 50 can be reduced in size by the amount of the reduction gear train 92 overlapped with the V-belt 53 as viewed from the axial direction 91.

  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.

  31b Bearing part, 40 Transmission case, 50 V belt type continuously variable transmission, 51 Primary shaft, 51a Large diameter part, 51b Support part (small diameter part), 51d Step part, 52 Secondary shaft, 53 V belt, 60 Drive pulley , 62 Movable pulley, 63 Boss part, 63a Opposing 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 Deceleration Gear train, 100 Power transmission part, 110 Torque transmission part, 111 Radial part, 112 Axial part, 120 Engaging member, 121 Engaging part, 130 Connecting member, 133 Connecting part.

Claims (2)

A driving pulley supported by the primary shaft; a driven pulley supported by a secondary shaft arranged in parallel to the primary shaft; a V-belt stretched between the driving pulley and the driven pulley; A case housing a pulley, a driven pulley, and a V-belt, a groove width variable mechanism for changing a groove width of the drive pulley and / or the driven pulley, a drive unit for operating the variable groove width mechanism, A V-belt type continuously variable transmission including a power transmission unit that transmits power to the groove width variable mechanism;
The drive unit and the power transmission unit are arranged in a line connecting the primary shaft and the secondary shaft in the case ,
The drive unit includes a motor unit in which a motor that is a drive source is accommodated, and an output shaft of the drive unit that is operated by power of the motor, and the output shaft is disposed in parallel with the primary shaft or the secondary shaft. ,
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 within the belt width of the V belt as viewed from the direction orthogonal to the output shaft. The motor unit is arranged outside the belt width, and the output shaft is arranged on a line connecting the primary shaft and the secondary shaft in the rotation trajectory of the V belt when viewed from the axial direction of the output shaft. Belt type continuously variable transmission. The drive unit includes a reduction gear train that transmits the power of the motor to the output shaft. The reduction gear train is disposed outside the belt width of the V belt, and the reduction gear is viewed from the axial direction of the output shaft. V-belt type continuously variable transmission according to claim 1, characterized in that the column was overlapped with the V-belt.

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