JP5688482B2 - Continuously variable transmission structure - Google Patents

Description

  The present invention relates to a continuously variable transmission structure for a V-belt automatic transmission.

  2. Description of the Related Art Conventionally, as a continuously variable transmission structure for a V-belt automatic transmission, for example, a continuously variable transmission structure as shown in FIG. To explain with reference to the reference, the continuously variable transmission structure includes a fixed sheave (203), a movable sheave (207) movable relative to the fixed sheave (203), and the movable sheave (207). And an actuator (100) having an output rod (117) that moves forward and backward, and a continuously variable transmission for a V-belt automatic transmission in which a V-belt (211) is wound between sheaves (203, 207) The power of the output rod (117) is transferred to the movable sheave (207) through a fork member (300) which is a swinging member having a machine structure and having a pair of substantially “<”-shaped arms (301, 301). To communicate. The fork member (300) is supported so as to be swingable with respect to a shaft planted in an engine case (not shown).

JP 2009-79759 A

In the conventional continuously variable transmission structure described above, the power transmission member for transmitting the power of the output rod (117) to the movable sheave (207) is supported so as to be swingable with respect to the shaft implanted in the engine case. The fork member (300) is a swinging member having a pair of substantially “<”-shaped arm portions (301, 301), so that the fork member (300) can be assembled to the engine case. There was a difficulty in the space.
The problem to be solved by the present invention is to provide a continuously variable transmission structure capable of improving the assembling property and assembling space of a power transmission member for transmitting the power of an output rod to a movable sheave.

In order to solve the above problems, a continuously variable transmission structure according to the present invention includes a fixed sheave supported by a pulley shaft, a movable sheave movable with respect to the fixed sheave, and a movable sheave that moves forward and backward. In a continuously variable transmission structure for a V-belt automatic transmission that includes an actuator having an output rod and a V-belt is wound between the sheaves,
A transmission cover that covers the crankcase so as to accommodate the V-belt automatic transmission is provided inside, the actuator is attached to the transmission cover from the outside of the transmission cover, and the actuator is attached to the transmission cover. Arranged so that the output rod is parallel to the pulley shaft in an attached state,
A power transmission member held via a bearing with respect to the movable sheave, the power transmission member having a groove connected to a tip of the output rod;
The groove is a groove that opens in a direction orthogonal to the advancing / retreating direction of the output rod,
The output rod and the groove are connected by moving the tip of the output rod from the opening direction of the groove and engaging the tip with the groove.
According to this continuously variable transmission structure, the power transmission member that transmits the power of the output rod to the movable sheave is held via the bearing with respect to the movable sheave. Since it is not necessary to support the case, the assembling property and the assembling space can be improved.
Moreover, since the connection between the power transmission member and the tip of the output rod is made through the groove portion of the power transmission member, the assemblability can be further improved.
Further, since the groove portion is a groove portion that opens in a direction intersecting with the advancing / retreating direction of the output rod, power in both the advancing / retreating direction of the output rod can be transmitted to the movable sheave via the power transmission member. It is possible to smoothly perform the movement control.
The V-belt automatic transmission has a transmission cover that covers the crankcase, and the actuator is attached to the transmission cover, so that the actuator can be arranged on the opposite side of the crankcase with respect to the movable sheave. The degree of improvement is improved, and the actuator can be arranged close to the rotation center of the drive sheave. Therefore, the size of the continuously variable transmission structure can be further reduced.
Preferably, a space for enabling movement of the actuator for engaging the output rod with the groove is provided in the actuator mounting portion of the transmission cover.
Preferably, a second actuator is provided separately from the actuator (referred to as the first actuator), and the second actuator includes a plurality of centrifugal weights arranged around the rotation axis of the movable sheave and the centrifugal weights. And a cam member that moves the movable sheave to the centrifugal weight by the centrifugal force accompanying the rotation of the movable sheave.
With this configuration, the force to move the movable sheave by the second actuator increases in proportion to the square of the angular velocity of the movable sheave, so the force to move the movable sheave by the first actuator is reduced, The power consumption of one actuator can be suppressed.
Further, when the V-belt automatic transmission is disassembled, the cam member can prevent the centrifugal weight from falling off the movable sheave groove, so that the maintainability can be improved.
Desirably, a driven shaft as a drive shaft is provided in parallel with the pulley shaft, the V-belt is stretched between the pulley shaft and the driven shaft, and between the pulley shaft and the driven shaft. And arranging the actuator in
When viewed from the axial direction of the output rod, the output rod is arranged on a line connecting the pulley shaft and the driven shaft in the rotation locus of the V belt.
Preferably, the pulley shaft is disposed so as to be oriented in the vehicle width direction of the motorcycle.

The side view which shows the scooter type motorcycle as an example of the vehicle provided with the V-belt automatic transmission using one Embodiment of the continuously variable transmission structure which concerns on this invention. The side view of the power unit provided with the V belt automatic transmission in the same motorcycle. Partial omission III-III sectional drawing in FIG. FIG. 4 is a diagram showing an embodiment of a continuously variable transmission structure according to the present invention, and is a partially enlarged view of FIG. 3. It is a figure which shows the same embodiment, and the partial omission V arrow view in FIG. FIGS. 5A and 5B are diagrams showing the movable sheave 62, in which FIG. 5A is a front view, FIG. 5B is a cross-sectional view taken along line bb in FIG. Dd sectional drawing in (a). It is a figure which shows the bearing holder 65, (a) is a front view, (b) is bb sectional drawing in Fig. (A). It is a figure which shows the movable sheave holder 80, (a) is a front view, (b) is bb sectional drawing in Fig. (A), (c) is cc sectional drawing in Fig. (A). FIGS. 5A and 5B are diagrams showing a cam member 110, where FIG. 5A is a front view, FIG. 5B is a cross-sectional view taken along line bb in FIG. Omitted bottom view, (e) is a cross-sectional view taken along line ee in FIG. It is a figure which shows the connection member 130, (a) is a front view, (b) is a top view, (c) is cc sectional drawing in FIG. (B). It is a figure which shows the guide piece 140, (a) is a front view, (b) is bb sectional drawing in Fig. (A), (c) is cc sectional drawing in Fig. (A), (d) is a bottom face. Figure. It is a figure which shows the other stopper 42s, (a) is a front view, (b) is a left view, (c) is cc sectional drawing in figure (a). Operation explanatory drawing. (A) (b) is an operation explanatory view, respectively.

Embodiments of a continuously variable transmission structure according to the present invention will be described below with reference to the drawings.
A motorcycle 10 shown in FIG. 1 is a vehicle in which a power unit 20 is suspended from a body frame 11 around a pivot shaft 12 at a rear portion of a body frame 11 with a pivot shaft 12 and a rear cushion unit 13. 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 automatic 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 portion of the vehicle body frame 11, and the power of the engine 30 is transmitted to the rear wheels 15 </ b> R via the V-belt automatic transmission 50 in the transmission case 40. The power unit 20 also serves as a rear swing arm.

  As shown in FIGS. 2 and 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.

  As shown in FIG. 3, the crankshaft 31 c is rotatably supported by ball bearings 31 b and 31 b held by the crankcase 31, and a piston 32 p 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.

  As shown in FIG. 3, the V-belt automatic transmission 50 includes a drive pulley 60 supported by a primary shaft 51 that is a first pulley shaft and a driven pulley supported by a secondary shaft 52 that is a second pulley shaft. 70 and a V-belt 53 stretched between the driving pulley 60 and the driven pulley 70.

  As shown in FIGS. 4 and 5, the continuously variable transmission structure of this embodiment is used as a drive pulley 60 in the V-belt automatic transmission 50. The continuously variable transmission structure of this embodiment has a fixed sheave 61 and a movable sheave 62 movable relative to the fixed sheave 61, and a V belt 53 is wound around the sheaves 61 and 62. This is a continuously variable transmission structure for an automatic belt transmission.

This continuously variable transmission structure includes a first control mechanism CM1 having a first actuator 90 that moves the movable sheave 62, and a second control mechanism that moves the movable sheave 61 in cooperation with the first control mechanism CM1. And a second control mechanism CM2 having an actuator 100.
In the illustrated V-belt automatic transmission 50, the continuously variable transmission structure of this embodiment is used for the drive pulley 60, but it can also be used for the driven pulley 70 (see FIG. 3).
Hereinafter, the structure of the continuously variable transmission of this embodiment will be further described while explaining the configuration of the V-belt automatic transmission 50.

As shown in FIGS. 3 and 4, in this embodiment, the primary shaft 51 is constituted by one end of the crankshaft 31c described above.
The crankshaft 31c includes a large-diameter portion 51a supported at both ends by bearings 31b and 31b, which are bearing members, and a support portion for the movable sheave 62 in the drive pulley 60 that is provided on the large-diameter portion 51a via a stepped portion 51d. And a small-diameter portion 51b.
The primary shaft 51 is composed of a small-diameter portion 51b of the crankshaft 31c, and the primary shaft 51, that is, the support shaft of the drive pulley 60 is supported in a cantilevered state on the right case 40R.

As shown in FIG. 4, the drive pulley 60 is attached to a fixed sheave (fixed half) 61 that does not move in the axial direction of the primary shaft (pulley shaft) 51, and is movable in the axial direction with respect to the primary shaft 51 so as not to be relatively rotatable. The movable sheave (movable half) 62 is provided.
The first control mechanism CM1 and the second control mechanism CM2 are configured to slide the movable sheave 62 in the axial direction along the support portion 51b of the movable sheave 62 on the pulley shaft 51, so that the groove width of the pulley 60, that is, the fixed sheave 61, This is a mechanism for changing the distance from the movable sheave 62.

  The first control mechanism CM1 includes a movable sheave holder 80 that is held with respect to the movable sheave 62 via a bearing 64, and a power transmission unit T that transmits the power of the first actuator 90 to the movable sheave holder 80. ing. The power transmission unit T is disposed on the first actuator 90 side with respect to the rotation center 62 c of the movable sheave 62.

The bearing 64 is held by the movable sheave 62 via a bearing holder 65 (see FIG. 7), and the movable sheave holder 80 is supported by the movable sheave 62 via the bearing 64. A circlip 66 couples (locks) the bearing 64 and the movable sheave holder 80.
The power transmission unit T includes a connecting member 130 that connects the movable sheave holder 80 and the tip 91a of the output rod 91 of the first actuator 90.

  The second control mechanism CM2 includes a second actuator 100. The second actuator 100 holds a plurality of centrifugal weights 101 arranged around the rotation axis of the movable sheave 62 and the centrifugal weight 101 between the movable sheave 62 and a centrifugal force accompanying the rotation of the movable sheave 62. The centrifugal weight 101 includes a cam member 110 that moves the movable sheave 62. Since the cam member 110 is composed of a ramp plate, the cam member 110 is also referred to as a ramp plate hereinafter.

As shown in FIG. 6, the movable sheave 62 has a boss portion 62b and a flange portion 62f, and a weight housing for accommodating the centrifugal weight 101 (see the phantom line) between the boss portion 62b and the flange portion 62f. A plurality of parts 62s (six in the figure) are provided in a radial manner.
A plurality of fixing portions 62c (three shown) having screw holes for fixing the bearing holder 65 (FIG. 7) are provided between the weight accommodating portions 62s.
Further, between the weight accommodating portions 62s, a guided member guided by a guide piece 140 (see the phantom line in FIG. 9 and FIGS. 11 and 4) mounted on the guide portion 110g of the lamp plate 110 (FIG. 9). A plurality of parts 62g (three shown in the figure) are provided.

  As shown in FIG. 7, the bearing holder 65 has a short cylindrical portion 65b, a flange portion 65f integrated with the short cylindrical portion 65b, and a plurality of (three in the figure) integrally provided inside the flange portion 65f. Part 65c. The bearing holder 65 is fixed to the movable sheave 62 by connecting the mounting portion 65c thereof to the fixing portion 62c of the movable sheave 62 described above with a bolt 65d (see FIG. 4). A bearing 64 (FIG. 4) is attached to the outer periphery of the cylindrical portion 65 b of the bearing holder 65. The bearing 64 is disposed around the centrifugal weight 101 of the second actuator 100.

As shown in FIG. 8, the movable sheave holder 80 has a ring part (short cylindrical part) 81 and an arm part 82 integrated with the ring part 81. As shown in FIG. 4, the ring portion 81 is fitted with the bearing 64, and the arm portion 82 is connected to the connecting member 130. A connection structure with the connection member 130 will be described later.
As shown in FIG. 8, the ring portion 81 has a flange portion 81 f for restricting movement in the axial direction with respect to the bearing 64 and a ring-shaped groove 81 g for mounting the circlip 66.

  As shown in FIG. 9, the lamp plate (cam member) 110 is a star-shaped plate (sheet metal member) as a whole, and extends radially from the central disc portion 111 and the disc portion 111. The same number (six as shown) of cam portions 112 that hold the centrifugal weight 101 between the movable sheave 62 and the weight accommodating portion 62s, and a fixed portion between the movable sheave 62 and the bearing holder 65 A recess 113 for escaping 62c and 65c and a guide portion 110g to which the guide piece 140 is attached and guides a guided portion 62g (see FIGS. 4 to 6) of the movable sheave 62 through the guide piece 140 are provided. Have.

The disc portion 111 is provided with a hole 111h through which the small diameter portion 51b of the pulley shaft 51 is inserted.
The guide part 110g has a U-shaped cutout 114 into which the guide piece 140 is fitted, and a rib 115 raised in a U shape to reinforce the periphery of the cutout 114.

  As shown in FIG. 11, the guide piece 140 is a synthetic resin part excellent in slipperiness, and is fitted to the guided portion 62 g (see FIGS. 4 to 6) of the movable sheave 62 so as to be slidable in the axial direction. It has a U-shaped main body 142 having a guide groove 141 having a U-shaped cross section, and a small flange portion 143 and a large flange portion 144 provided at both ends of the main body 142.

  The guide piece 140 has a small flange 143 in contact with the top surface of the rib 115 of the lamp plate 110 and a large flange portion 144 in contact with the back surface of the lamp plate 110 as indicated by phantom lines in FIG. The main body 142 is fitted into the notches 114 of the lamp plate 110 to be mounted on the three guide portions 110g of the lamp plate 110, respectively.

The drive pulley 60 having the lamp plate 110, the movable sheave 62, the movable sheave holder 80 and the like as described above can be assembled on the small-diameter portion 51b of the pulley shaft 51 as follows, for example.
Referring to FIG. 4, the movable sheave holder 80 is mounted on the outer periphery of the bearing 64 in advance, and both are engaged by the circlip 66, and the bearing holder 65 is mounted on the inner periphery of the bearing 64. Are coupled to the movable sheave 62 by a plurality of bolts 65d (only one is shown in FIG. 4), and a sleeve 67 is inserted into the boss portion 62b of the movable sheave 62 via an oil seal 62s and a collar 62c. Then, the centrifugal weight 101 is accommodated in each weight accommodating portion 62 s of the movable sheave 62, the guide piece 140 is attached to each guide portion 110 g of the lamp plate 110, and the guide groove 141 of the guide piece 140 is covered with the cover of the movable sheave 62. The movable sheave 62 and the lamp plate 110 are lightly coupled by fitting the guide portion 62g. Keep composing the assembly.

  First, the small diameter portion 51b is inserted into the hole 111h of the lamp plate 110 in the assembly, then the small diameter portion 51b is inserted into the sleeve 67 of the assembly, and the fixed sheave 61 is attached to the small diameter portion 51b. A double nut 68 is attached to the tip of the portion 51b, and the lamp plate 110, the sleeve 67, and the fixed sheave 61 are jointly fastened between the double nut 68 and the stepped portion 51d of the primary shaft 51 to reduce the diameter. It fixes on the part 51b. As a result, the drive pulley 60 is assembled on the small diameter portion 51 b of the pulley shaft 51.

  In the drive pulley 60 as described above, the ramp plate 110, the sleeve 67, and the fixed sheave 61 are fastened and fixed between the double nut 68 and the step portion 51d of the primary shaft 51. On the other hand, neither relative movement in the axial direction nor relative rotation around the axis is possible, and the pulley shaft 51 rotates.

The movable sheave 62 can be moved relative to the sleeve 67 in the axial direction and relatively rotated around the axis, but the guided portion 62g is mounted on the guide portion 110g of the clamped lamp plate 110. Further, since the guide piece 140 is fitted in the guide groove 141, relative rotation around the axis of the ramp plate 110, that is, relative rotation with respect to the pulley shaft 51 is impossible.
Therefore, the movable sheave 62 rotates with the pulley shaft 51 and can move in the axial direction of the pulley shaft 51.

The movable sheave holder 80 can be rotated relative to the movable sheave 62 via a bearing 64. Therefore, the movable sheave holder 80 can be in a non-rotating state around the pulley shaft 51.
On the other hand, in the movable sheave holder 80, one end of the bearing 64 abuts on the circlip 66 and a step 62h (see FIG. 6) of the flange 62f of the movable sheave 62, and the other end of the bearing 64 is the flange of the movable sheave holder 80. By abutting the portion 81 f and the flange portion 65 f of the bearing holder 65, relative movement in the axial direction is impossible with respect to the movable sheave 62.
Therefore, the movable sheave 62 can be similarly moved in the axial direction by moving the movable sheave holder 80 in the axial direction.
The movable sheave holder 80 has an arm portion 82 connected to the output rod 91 of the first actuator 90 by a connecting member 130, and is movable in the axial direction by driving the first actuator 90.

  As shown in FIGS. 4 and 5, the first actuator 90 is operated by a motor unit M1 (FIG. 4) in which a motor (servo motor) M (FIG. 5) serving as a drive source is housed, and the power of the motor M And an output rod 91 as an output section. The output rod 91 is arranged in parallel with the primary shaft 51. As shown in FIG. 5, the first actuator 90 is arranged so that the motor M is positioned above the line L <b> 1 connecting the primary shaft 51 and the secondary shaft 52.

  The first actuator 90 includes a reduction gear train 92 that transmits the power of the motor M to the output rod 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 rod 91 is formed in a cylindrical shape, and a ball screw (female screw) 91 b is formed on the inner surface thereof. The 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 rod 91 moves forward and backward in the axial direction (arrow X1, X2 direction in FIG. 4) according to the rotation direction.

The first actuator 90 is fixed to the case by fastening a gear case 94 containing the reduction gear train 92 to a mounting portion (not shown) provided in the case 40 with a screw 95. The first actuator 90 can be attached to the inside of the case 40 and accommodated in the case 40, or can be attached to the outside of the case 40.
The first actuator 90 is disposed around the second actuator 100.

  As shown in FIG. 4, the tip 91 a of the output rod 91 protrudes toward the V belt 53 from the motor portion M 1 of the first actuator 90, and at least the output rod 91 is viewed from the direction orthogonal to the output rod 91. A portion 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 rod 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 rod 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 with the V belt 53 when viewed from the axial direction of the output rod 91. Arrange as follows.

  As shown in FIG. 4, the first actuator 90 is disposed on the fixed sheave side, and the output rod 91 and the connecting member 130 are connected to the movable sheave holder 80 across the travel line of the V-belt 53.

As shown in FIGS. 4 and 5, the power transmission unit T is for transmitting the power of the first actuator 90 to the movable sheave holder 80, and has the connecting member 130.
As shown in FIGS. 4 and 8, the arm portion 82 of the movable sheave holder 80 integrally extends from one end portion of the ring portion 81 in the circumferential direction to the first actuator 90 side (right side in FIG. 4). The arm portion 82 is provided with a pair of convex portions 83, 83 facing the output rod 91 side of the first actuator 90.

  On the other hand, as shown in FIGS. 4, 5, and 10, the connecting member 130 includes a hook portion (hook structure) 133 having a U groove 131 connected to the tip 91 a of the output rod 91 by a pin 132, and the hook portion. 133 and a connecting part 134 extending toward the arm part 82 side of the movable sheave holder 80. The connecting portion 134 enters between the pair of convex portions 83 and 83 in the movable sheave holder 80, and the connecting portion 134 of the connecting member 130 and the pair of convex portions 83 and 83 are connected by the pin 84. . Thereby, the movable sheave holder 80 and the connecting member 130 are connected. The U-groove 131 is a U-groove that opens in a direction that intersects the advancing / retreating direction of the output rod 91.

With this configuration, when the hook portion 133 and the tip 91a of the output rod 91 are connected during assembly, or when the connection between the hook portion 133 and the distal end 91a of the output rod 91 is released during disassembly, the first actuator 90 is used as the clearance 41c with the case 40. Then, it is possible to easily connect / release the hook portion 133 and the tip 91a of the output rod 91 by rotating in the directions of arrows a and b to engage and disengage the hook portion 133 with the pin 132.
A clearance 41c that allows the actuator 90 to move to engage and disengage the hook portion 133 is provided in the attachment portion of the actuator 90 in the case 40.

  Since the movable sheave holder 80 and the output rod 91 of the first actuator 90 are connected by the connecting member 130, when the output rod 91 of the first actuator 90 moves back and forth, the movable sheave holder 80 also moves in the same direction. As a result, the movable sheave 62 is also transferred in the same direction.

  The connecting member 130 is pivotally connected to the movable sheave holder 80 by a pin 84, but the movable sheave holder 80 contacts the contact portions 135 and 136 of the connecting member 130 to rotate the connecting member 130. Restricting portions 85 and 86 for restricting movement are provided (see FIG. 8).

  By connecting the movable sheave holder 80 and the output rod 91 via the connecting member 130, the degree of freedom of the arrangement position of the first actuator 90 with respect to the movable sheave holder 80 is improved. Depending on the arrangement position of the actuator 90, for example, as shown in FIG. 4, the position of the pin 84 that is the connection position of the movable sheave holder 80 and the connection member 130 may be offset with respect to the axis of the output rod 91.

Such an offset causes the connecting member 130 to rotate about the pin 84 when the output rod 91 advances and retracts. To prevent this rotation, the movable sheave holder 80 is not contacted with the connecting member 130. Restricting portions 85 and 86 that abut the contact portions 135 and 136 and restrict the rotation of the connecting member 130 are provided.
By providing such a restricting portion, the power transmission location between the connecting member 130 and the movable sheave holder 80 when the output rod 91 moves back and forth is set at the pin coupling position (84) and the restricting portion. Since it can disperse | distribute, the force to the direction which inclines the movable sheave holder 80 can be suppressed.

  The case 40 (shown is the right case 40R) is provided with stoppers 41s and 42s that define the moving range of the movable sheave holder 80. These stoppers 41 s and 42 s are provided in the immediate vicinity of the connecting portion (84) between the movable sheave holder 80 and the connecting member 130 when viewed from the rotation center (62 c) of the movable sheave holder 80.

  One stopper 41 s is integrally provided on the inner surface of the case 40, and is formed in a column shape that protrudes from the inner surface of the case 40 toward the arm portion 82 of the movable sheave holder 80 in parallel with the pulley shaft 51. . The stopper 41s abuts against one side surface 80b of the movable sheave holder 80, thereby preventing excessive movement of the movable sheave holder 80 in the arrow X1 direction.

  The other stopper 42s is for preventing excessive movement of the movable sheave holder 80 in the direction of the arrow X2, and can come into contact with the convex regulated portion 87 provided on the arm portion 82 of the movable sheave holder 80. A contact portion 42t (see FIG. 12) and a mounting portion 42c to the case 40 are provided. The stopper 42s is attached to the case 40 by fixing the attachment portion 42c with a bolt 42b to a columnar attachment portion 42 that protrudes from the inner surface of the case 40 in parallel with the pulley shaft 51.

Since the moving range of the movable sheave holder 80 (in this case, the sliding range in the directions of the arrows X1 and X2) is defined by the forward / backward moving range of the output rod 91 in the first actuator 90 using the servo motor M as a drive source, Usually, the movable sheave holder 80 does not contact the stoppers 41s and 42s.
However, the movable sheave holder 80 may try to move more than necessary (excessively) for some reason (for example, a failure of the control system of the first actuator 90). In order to prevent this, the stopper 41s, 42s is provided.

The second actuator 100 is configured as described above and operates as follows.
When the drive pulley 60 rotates and the rotation speed becomes a certain level or higher, a centrifugal force corresponding to the rotation speed acts on the centrifugal weight 101. Accordingly, the centrifugal weight 101 moves (or tries to move) away from the pulley shaft 51 in accordance with the rotational speed of the drive pulley 60. Here, the space S (see FIG. 4) formed by the weight housing portion 62s of the movable sheave 62 and the ramp plate 110, in which the centrifugal weight 101 is housed, becomes narrower as the distance from the pulley shaft 51 increases. The centrifugal weight 101 acts to widen the space S. The movable sheave 62 is movable in the axial direction while the lamp plate 110 is not movable in the axial direction. As a result, the movable sheave 62 is moved by the centrifugal weight 101.
The movement of the movable sheave 62 is regulated by the forward and backward movement of the output rod 91 in the first control mechanism CM1, that is, the first actuator 90.

As shown in FIG. 3, the secondary shaft 52, which is the driven shaft of the V-belt automatic 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 sheave (fixed half) 71 and a movable sheave (movable half) 72.
An endless V-belt 53 is stretched between the drive pulley 60 and the driven pulley 70 described above, and the rotation of the drive 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 sheave 72 in the driven pulley 70 is attached to the secondary shaft 52 so as to be movable in the axial direction. The movable sheave 72 is urged in a direction approaching the fixed sheave 71 by a coil spring 73 and moves in the axial direction in accordance with the tension acting on the V-belt 53. That is, when the movable sheave 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 is increased (see FIG. 13), it is wound around the driven pulley 70 accordingly. The tension applied to the V-belt 53 is increased when the V-belt 53 is pulled toward the drive pulley 60, and the movable sheave 72 of the driven pulley 70 is displaced in the direction of widening the groove by increasing this tension. The winding diameter of the V-belt 53 around 70 becomes smaller, and the secondary shaft 52 rotates at a high speed. When the movable sheave 62 of the drive 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 first actuator 90 is actuated by control by a control unit (not shown) and the output rod 91 protrudes in the arrow X1 direction and the movable sheave 62 slides in the X1 direction in FIG. 4, the distance between the fixed sheave 61 and the movable sheave 62 is increased. The diameter of the V-belt 53 around the drive pulley 60 becomes smaller and the diameter of the V-belt 53 around the driven pulley 70 becomes larger (the ratio of the belt becomes LOW) so that it can withstand high loads. Further, the rear wheel 15R is rotationally driven at a low speed. On the contrary, when the output rod 91 slides in the direction of the arrow X2 and the movable sheave 62 slides in the X2 direction (see FIG. 13), the distance between the fixed sheave 61 and the movable sheave 62 becomes narrow, and the driving pulley 60 of the V belt 53. As the winding diameter increases, the winding diameter of the V belt 53 around the driven pulley 70 decreases, and the rear wheel 15R is driven to rotate at a high speed.

Furthermore, in this embodiment, the first actuator 90 operates as follows under the control of the control unit. That is,
The first actuator 90 operates to generate a force in the same direction as the force to move the movable sheave 62 by the second control mechanism CM2 in the low rotation region of the movable sheave 62 in the drive pulley 60. In the high rotation region of the movable sheave 62, the movable sheave 62 operates so as to be resistant to the force to move the movable sheep 62 by the second control mechanism CM2.

  FIG. 14 is a graph showing an example of control of the first actuator 90, and is also an operation explanatory diagram of the first control mechanism CM1 and the second control mechanism CM2. (A) is a graph in the normal mode, and (b) is a graph in the sport mode. The mode is selected by a mode selection switch or a mode selection lever provided where it is easy for a driver on the vehicle to operate.

These graphs show the force (thrust (N)) for moving the movable sheave 62 on the left vertical axis, the rotational speed (rpm) of the crankshaft 31c (engine) on the right vertical axis, and the vehicle speed (km) on the horizontal axis. / H). The thrust is the direction in which the movable sheave 62 is moved toward the fixed sheave 61 (the direction in which the interval between both sheaves is narrowed (shift-up side)), and the arrow X2 direction in FIG.
In these graphs, the alternate long and short dash line (CM1) indicates the thrust by the first control mechanism CM1, that is, the first actuator 90, and the broken line (CM2) indicates the thrust by the second control mechanism CM2, that is, the centrifugal actuator 101, by the second actuator 100. , And solid lines (CM1 + CM2) respectively represent the thrusts of the resultant force.

In the normal mode, as shown in the graph (a), when the vehicle speed reaches about S1 (for example, about 20 km / h), the first actuator 90 is operated, and the thrust (about P3 by the second control mechanism CM2) is activated. (For example, about 600 N)) is added with a thrust (an intermediate value between P2 and P3 (for example, about 500 N)) by the first control mechanism CM1 to obtain a large total thrust (for example, an intermediate value between P5 and P6 (for example, about 1100 N)). This causes a quick shift up (the belt ratio is set to the high side), thereby improving fuel consumption.
When the vehicle speed exceeds about S3 (for example, about 60 km / h), the thrust by the second control mechanism CM2 gradually increases according to the engine speed, so that the total thrust (CM1 + CM2) is maintained constant. The thrust by the control mechanism CM1 is gradually reduced.
When the vehicle speed exceeds about S4 (for example, about 80 km / h), the thrust by the second control mechanism CM2 becomes too large according to the engine speed, so the thrust is canceled and the total thrust (CM1 + CM2) is kept constant. Therefore, the thrust by the first control mechanism CM1 (first actuator 90) is actuated to the minus side.

In the sport mode, as shown in the graph (b), the first actuator 90 is not operated until the vehicle speed reaches about S4 (for example, about 80 km / h). Therefore, thrust by the first control mechanism CM1 cannot be obtained until the vehicle speed reaches about S4 (CM1 + CM2 = CM2). For this reason, upshifting is suppressed (the belt ratio is maintained on the LOW side), and agile driving can be performed.
When the vehicle speed exceeds about S4, the thrust by the second control mechanism CM2 becomes too large according to the engine speed. Therefore, the first control is performed in order to cancel the thrust and keep the total thrust (CM1 + CM2) constant. The thrust by the mechanism CM1 (first actuator 90) is actuated to the minus side.

According to the continuously variable transmission structure as described above, the following operational effects can be obtained.
(A) The movable sheave holder 80 held to the movable sheave 62 via the bearing 64 and the distal end portion 91a of the output rod 91 are coupled by a coupling member 130 having a U groove 131 coupled to the distal end portion 91a. Therefore, the power transmission member that transmits the power of the output rod 91 to the movable sheave 62 can be constituted by the movable sheave holder 80 and the connecting member 130.
Unlike the fork member (300) in the prior art described above, the power transmission members 80 and 130 do not need to be supported by the engine case, so that the assembling property and the assembling space can be improved.
In addition, the connection between the connecting member 130 and the tip of the output rod 91 is made through the U groove 131 of the connecting member 130, so that the assembling property can be further improved.
(B) Since the actuator 90 is disposed on the fixed sheave 61 side, and the output rod 91 and the connecting member 130 are connected to the movable sheave holder 80 across the travel line of the V-belt 53, the V-belt which tends to become a dead space. The inner space 53i of the travel line can be used effectively. Therefore, the continuously variable transmission structure can be reduced in size.
(C) The connecting member 130 is connected to the movable sheave holder 80 at one end portion (arm portion 82) in the circumferential direction of the movable sheave holder 80 and has a hook structure that forms the U groove 131. Therefore, the connecting member 130 and the output rod 91 can be easily assembled / disassembled through the opening of the U-shaped groove 131 of the hook structure.
(D) Since the U-groove 131 of the connecting member 130 is a U-groove that opens in a direction crossing the advancing / retreating direction of the output rod 91, the power in both the advancing / retreating direction of the output rod 91 is transmitted to the movable sheave 80 via the connecting member 130. Can communicate. For this reason, the movement control of the movable sheave 80 in both directions can be performed smoothly.
(E) The V-belt automatic transmission 50 includes a left case 40L that is a transmission cover that covers the crankcase 31, and an actuator 90 is attached to the transmission cover 40L so that the movable sheave 62 is opposite to the crankcase 31. The actuator 90 can be arranged on the For this reason, the degree of freedom of arrangement is improved, and the actuator 90 can be arranged close to the rotation center 62 c of the drive sheave 62. Therefore, the size of the continuously variable transmission structure can be further reduced.
(F) By disposing the actuator 90 close to the rotation center 62c of the drive sheave 62, the actuator 90 can be disposed close to the pivot shaft 12, so that the unsprung load can be reduced.
(G) The connecting member 130 is rotatably connected to the movable sheave holder 80 by a pin 84, and the movable sheave holder 80 is in contact with the connecting member 130 to restrict the rotation of the connecting member. 86 is provided, the connecting member 130 and the movable sheave holder 80 can be easily connected by pin coupling, and the power transmission location between the connecting member 130 and the movable sheave holder 80 can be determined by pin coupling. Since the position and the restricting portions 85 and 86 can be dispersed, the force in the direction in which the movable sheave holder 80 is tilted can be suppressed.
(H) The stoppers 41 s and 42 s that restrict the movement of the movable sheave holder 80 in the axial direction are immediately close to the connection portion between the movable sheave holder 80 and the connecting member 130 when viewed from the rotation center (62 c) of the movable sheave holder 80. Therefore, the torsional force acting on the movable sheave holder 80 when the movable sheave holder 80 abuts against the stoppers 41s and 42s can be reduced, and one function portion of the stopper is arranged in an integrated manner. Can be miniaturized.

(I) A first control mechanism CM1 having a first actuator 90 for moving the movable sheave 62, and a second actuator 100 having a second actuator 100 for moving the movable sheave 62 in cooperation with the first control mechanism CM1. 2, the movable sheave 62 is moved in cooperation with the first control mechanism CM1 having the first actuator 90 and the second control mechanism CM2 having the second actuator 100. Made by work.
For this reason, when the power for moving the movable sheave 62 is increased, the power is transmitted to the first control mechanism CM1 having the first actuator 90 and the second control mechanism CM2 having the second actuator 100. (See, for example, FIG. 14A).
Therefore, compared to the conventional structure in which the movable sheave is moved by a single actuator and a single control mechanism, even when the power for moving the movable sheave 62 is increased, the load on each actuator 90, 100 is reduced. Therefore, the size of each of the actuators 90 and 100 can be suppressed, and the size of the V-belt automatic transmission 50 can be reduced as a whole.
Moreover, the durability of each actuator can be improved by suppressing the load on each actuator 90, 100.
Further, the weight of the centrifugal weight 101 of the second actuator 100 is set so that the required maximum thrust of the first actuator 90 is substantially equal in both the normal mode and the sports mode (see FIGS. 14A and 14B). Since (about -P2 to P2) is set, the first actuator 90 and the second actuator 100 can be reduced in size.
(J) The first actuator 90 is driven by electric power, and the second actuator 100 is driven by a centrifugal force accompanying the rotation of the movable sheave 62. That is, one actuator 100 is centrifuged by utilizing the rotation of the movable sheave 62. Because it is driven by force, energy consumption can be reduced by suppressing the power consumption of the continuously variable transmission structure as a whole.
(K) Since the first actuator 90 is arranged around the second actuator 100, both the actuators 90, 100 are arranged compactly around the rotation shaft 51 of the pulley 60, and the first actuator 90 Arrangement freedom can be improved.
(L) Since the first actuator 90 is disposed at the inner peripheral position of the V-belt 53, the V-belt inner peripheral space 53i that tends to become a dead space can be effectively used.
(M) The second actuator 100 holds a plurality of centrifugal weights 101 arranged around the rotation axis 62 c of the movable sheave 62 and the centrifugal weight 101 between the movable sheave 62, and rotates the movable sheave 62. Since the centrifugal weight 101 includes the cam member 110 that moves the movable sheave 62 by the accompanying centrifugal force, the force that moves the movable sheave 62 by the second actuator 100 is proportional to the square of the angular velocity of the movable sheave 62. To increase.
Therefore, it is possible to reduce the force for moving the movable sheave 62 by the first actuator 90 and further suppress power consumption (see, for example, the range of vehicle speeds S3 to S4 km / h in FIG. 14A).
Further, when the V-belt automatic transmission 50 is disassembled, the cam member 110 can prevent the centrifugal weight 101 from dropping from the weight accommodating portion 62s of the movable sheave 62, so that maintainability can be improved.
(N) The first control mechanism CM1 includes a movable sheave holder 80 that is held with respect to the movable sheave 62 via a bearing 64, and a power transmission unit T that transmits the power of the first actuator 90 to the movable sheave holder 80. The power transmission unit T is disposed on the first actuator 90 side with respect to the rotation center 62c of the movable sheave 62. Therefore, the power transmission unit T is reduced in size, and the continuously variable transmission structure and V The automatic belt transmission can be reduced in size.
(O) Since the bearing 64 is arranged around the centrifugal weight 101, the bearing 64 can be arranged using the outer peripheral space of the centrifugal weight 101, and the first control mechanism CM 1 having the first actuator 90 and the first control mechanism CM 1 Despite the provision of the second control mechanism CM2 having the second actuator 100, the continuously variable transmission structure and the V-belt automatic transmission device can be prevented from being enlarged in the axial direction.
(P) The first actuator 90 attempts to move the movable sheep 62 by the second control mechanism CM2 in the low rotation region of the movable sheave 62 (see, for example, the region of N3 to N7 rpm in FIG. 14A). The movable sheave 62 is moved in the high rotation region (see, for example, the region of N7 rpm or higher in FIG. 14A) in the high rotation region of the movable sheave 62. Acts to resist resistance to force.
Accordingly, in the low rotation region of the movable sheave 62, the movable sheep 62 moves by the force in the same direction by the first control mechanism CM1 and the second control mechanism CM2, and therefore the movable sheep 62 is smoothly moved by both control mechanisms. Can be moved to.
On the other hand, in the high rotation region of the movable sheave, the first actuator 90 operates so as to become a resistance against the force to move the movable sheep 62 by the second control mechanism CM2. Excessive movement of the movable sheep by the control mechanism CM2, that is, excessive shift operation can be suppressed.
(Q) Since a plurality of centrifugal weights 101 are distributed around the rotation center 62 c of the movable sheave 62, the distortion of the movable sheave 62 with respect to the inclination of the movable sheave 62 due to the belt reaction force received by the half circumference portion of the movable sheave 62, The load on one actuator 90 can be reduced.

  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.

31c: Crankcase, 40: Transmission case, 40L: Left case (transmission cover), 41s, 42s: Stopper, 50: V-belt automatic transmission, 51: Pulley shaft, 53: V-belt, 60: Drive pulley ( (Continuously variable transmission structure), 61: fixed sheave, 62: movable sheave, 64: bearing, 80: movable sheave holder, 84: pin, 85, 86: restricting section, 90: first actuator, 91: output rod 91 CM1: first control mechanism, CM2 second control mechanism, T: power transmission unit, 100: second actuator, 101: centrifugal weight, 110: cam member, 130: coupling member, 131: U groove.

Claims (5)

A fixed sheave (61) supported by the pulley shaft (51), a movable sheave (62) movable relative to the fixed sheave (61), and an output rod that moves forward and backward to move the movable sheave (62) And a continuously variable transmission structure for a V-belt automatic transmission in which a V-belt (53) is wound between the sheaves (61) and (62).
A transmission cover (40L) that covers the crankcase (31) so as to house the V-belt automatic transmission therein is provided, and the actuator is attached to the transmission cover (40L) from the outside of the transmission cover (40L). (90) is installed, and the output rod (91) is arranged in parallel with the pulley shaft (51) in a state where the actuator (90) is attached to the transmission cover (40L),
The movable sheave (62) is provided with a power transmission member (T) held via a bearing (64), and the power transmission member (T) is connected to a tip end portion (91a) of the output rod (91). Groove part (131)
The groove (131) is a groove (131) that opens in a direction orthogonal to the advancing / retreating direction of the output rod (91),
The output rod (91) is moved by moving the distal end portion (91a) of the output rod (91) from the opening direction of the groove portion (131) and engaging the distal end portion (91a) with the groove portion (131). And the groove (131) are connected to each other, and the continuously variable transmission structure.   A space (41c) that allows movement of the actuator (90) for engaging the output rod (91) with the groove (131) at the mounting portion of the actuator (90) in the transmission cover (40L). The continuously variable transmission structure according to claim 1, wherein the continuously variable transmission structure is provided.   In addition to the actuator (90), a second actuator (100) is provided, and the second actuator (100) includes a plurality of centrifugal weights (101) arranged around the rotation axis of the movable sheave (62). And a cam member that holds the centrifugal weight (101) between the movable sheave (62) and moves the movable sheave (62) to the centrifugal weight (101) by the centrifugal force accompanying the rotation of the movable sheave (62). 110), the continuously variable transmission structure according to claim 1 or 2. A driven shaft (52) disposed parallel to the pulley shaft (51) as a drive shaft is provided, and the V-belt (53) is stretched between the pulley shaft (51) and the driven shaft (52). And disposing the actuator (90) between the pulley shaft (51) and the driven shaft (52),
When viewed from the axial direction of the output rod (91), the output rod (91) is connected to the pulley shaft (51) and the driven shaft (52) in the rotation locus (53i) of the V-belt (53). The continuously variable transmission structure according to any one of claims 1 to 3, wherein the continuously variable transmission structure is disposed on a line (L1).   The continuously variable transmission structure according to any one of claims 1 to 4, wherein the pulley shaft (51) is arranged so as to be oriented in the vehicle width direction of the motorcycle (10).

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