JPH07103302A - Variable speed pulley - Google Patents

Abstract

PURPOSE:To enlarge the rotation width of a movable sheave against an axis of rotation without requirement on rotation of the movable sheave against a fixed sheave when the movable sheave is rotated against the axis of rotation so as to enhance transfer capacity by axially removing the movable sheave by utilizing rotation force existing between the movable sheave and the axis of rotation so that a winding diameter of a belt in a pulley groove is changed. CONSTITUTION:A sleeve 8 is movably fitted around an axis of rotation 2. A fixed sheave 29 and a movable sheave 30 are fitted around the sleeve 8, respectively, wherein the fixed sheave 29 is neither axially relatively movable nor rotatable, and the movable sheave 30 is axially relatively movable and rotatable.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a speed change pulley in which a movable sheave moves axially relative to a fixed sheave on a rotary shaft to change a belt winding diameter of a pulley groove, and more particularly, a fixed sheave is fixed to a rotary shaft. The present invention relates to the improvement of the supporting structure.

[0002]

2. Description of the Related Art A speed change pulley of this type has a fixed sheave, which is non-rotatably supported by a boss portion, and a movable shaft, which is axially movable by the boss portion, with respect to a rotary shaft which is rotatably supported around an axis. A movable sheave supported is provided, and the belt is wound around a pulley groove formed between the sheaves. Further, the engaging portion provided on the back side of the movable sheave of the rotary shaft and the boss portion of the movable sheave,
A torque cam mechanism including a cam portion that engages with the engaging portion is provided, and the torque cam mechanism is used to move the movable sheave in the axial direction by utilizing the turning force between the movable sheave and the rotating shaft. Therefore, the one in which the belt winding diameter of the pulley groove is changed is generally known.

As the above-mentioned speed change pulley, for example, the same speed change pulley
A speed change pulley device, etc., in which the rotational speeds of the two speed change pulleys are arranged in parallel with each other and a V-belt is wound between both speed change pulleys to change the pulley ratio between the two speed change pulleys. Also used as. Further, in recent years, as disclosed in Japanese Patent Application Laid-Open No. 62-118159, a differential gear mechanism such as a planetary gear mechanism is incorporated in the speed change pulley device to rotate the output shaft steplessly in the forward and reverse directions. A compact continuously variable transmission that can be used has also been proposed. Such a continuously variable transmission is used, for example, in a small vehicle such as a lawn mower or an agricultural machine, and in such a case, further high output is required while being compact. Therefore, even in the above-mentioned speed change pulley,
It is up to the demand to be able to transmit a larger driving force.

[0004]

By the way, in order to increase the transmission capacity of the above-mentioned speed change pulley, it is necessary to increase the tension of the belt and to request the speed change pulley to have a belt thrust not defeated by the belt tension. For that purpose, it is necessary to increase the rotation width of the movable sheave with respect to the rotation shaft to increase the force for moving the variable pulley in the axial direction.

However, in the conventional speed change pulley, when the movable sheave rotates with respect to the rotation shaft, the movable sheave also rotates with respect to the fixed sheave, so that the movable sheave is interposed in the pulley groove between the both sheaves. The rotating belt works in the direction of restricting the relative rotation between the two pulleys, which causes a problem that it is difficult to sufficiently increase the rotation width of the movable sheave with respect to the rotation axis.

The present invention has been made in view of the above circumstances, and an object thereof is to move the movable sheave in the axial direction by utilizing the turning force between the movable sheave and the rotary shaft. In a speed change pulley configured to change the belt winding diameter of a pulley groove, when rotating a movable sheave with respect to a rotation shaft, rotation of the movable sheave with respect to a fixed sheave is unnecessary and rotation with respect to the rotation shaft of the movable sheave is unnecessary. The purpose is to allow a wide range of movement, and thus to increase the transmission capacity.

[0007]

To achieve the above object, in the invention of claim 1, when the movable sheave rotates with respect to the rotary shaft, the fixed sheave together with the movable sheave also rotates with respect to the rotary shaft. I was able to rotate the same body.

Specifically, according to the present invention, a rotary shaft rotatably supported around an axis, a fixed sheave supported by the rotary shaft at a boss portion, and a rotary shaft supported by the rotary shaft at the boss portion. A movable sheave that forms a pulley groove around which the belt is wound with the fixed sheave, and a movable sheave rear surface side portion of the rotary shaft and a boss portion of the movable sheave are provided. A speed change pulley provided with a torque cam mechanism that changes the belt winding diameter of the pulley groove by moving the movable sheave in the axial direction by relative rotation between them.

A sleeve is rotatably fitted on the rotary shaft. This sleeve has
The boss portion of the fixed sheave is externally fitted so as not to be relatively movable in the axial direction and non-rotatably, and the boss portion of the movable sheave is externally fitted to be relatively movable in the axial direction and relatively non-rotatable. Have been combined.

According to a second aspect of the present invention, in the above-mentioned first aspect, when the fixed sheave side end portion of the rotary shaft is rotatably supported by the bearing portion, the bearing portion is the sleeve fixed sleeve side end portion. It is configured to allow the radial movement of the section.

According to a third aspect of the present invention, in the second aspect of the invention, the bearing portion is configured to support the thrust load of the sleeve at its fixed sheave side end portion.

[0012]

With the above construction, in the invention of claim 1, when the movable sheave rotates about the rotary shaft, the fixed sheave is rotated together with the movable sheave through the sleeve. Therefore, relative rotation of the movable sheave with respect to the fixed sheave does not occur, and a situation in which the rotation operation of the movable sheave with respect to the rotation shaft is restricted by the belt wound around the pulley groove is avoided.
Therefore, the rotation width of the movable sheave with respect to the rotation shaft can be made large, which allows the torque cam mechanism to increase the force for moving the movable sheave in the axial direction. The transmission capacity of the pulley can be increased.

According to the invention of claim 2, when the belt is wound around the pulley groove between the fixed sheave and the movable sheave,
The tension of the belt causes both sheaves to slightly tilt in the direction in which the groove width of the pulley groove on the belt winding side increases. At the same time, the sleeve is pulled in the direction in which the tension of the belt acts, so that the clearance between the sleeve and the rotating shaft on which the belt is wound is reduced in the entire axial direction. At this time, the fixed sheave side end portion of the sleeve is allowed to move in the radial direction by the bearing portion that rotatably supports the fixed sheave side end portion of the rotating shaft. It is possible to avoid a situation in which the clearance of the portion corresponding to is not reduced as much as the clearance of the other portion due to the radial regulation of the bearing portion. As a result, the tilting postures of both sheaves differ due to variations in the clearance in the axial direction, and in particular, the clearance of the portion corresponding to the fixed sheave side end becomes larger than the clearance of the other portions in the axial direction. Contrary to the movable sheave, it is possible to avoid tilting toward the pulley groove side, and it is possible to suppress one-sided wear of the belt and fixed sheave due to such a difference in tilting posture.

According to the invention of claim 3, when the belt is wound around the pulley groove between the fixed sheave and the movable sheave,
Due to the tension of the belt, a component force is exerted on both sheaves in a direction in which they separate from each other. Then, the axial component force acting on the movable sheave is transmitted to the torque cam mechanism, and is converted into a predetermined operation between the movable sheave and the rotary shaft by the torque cam mechanism. At this time, the axial component force acting on the fixed sheave, that is, the thrust load of the sleeve is received by the bearing portion at the fixed sheave side end portion of the sleeve. This prevents the fixed sheave from moving in the axial direction, so that as the movable sheave moves in the axial direction,
Each belt winding diameter can be appropriately maintained.

[0015]

Embodiments of the present invention will be described below with reference to the drawings.

2 and 3 show the overall structure of a continuously variable transmission A according to an embodiment of the present invention. This transmission A has a combination of an engine E and drive wheels in vehicles such as lawn mowers and agricultural machines. It is arranged in the power transmission path between them.

2 and 3, reference numeral 1 denotes a casing of the continuously variable transmission A, which is one of the features of the present invention. The casing 1 is a first casing from the left side to the right side in FIG. It is divided into three parts, that is, a casing part to a third casing part, that is, first to third divided casings 1a to 1c. Then, inside the casing 1, a first rotating shaft 2 and a second rotating shaft 12 arranged parallel to each other in a substantially horizontal plane are rotatably supported.

The first rotary shaft 2 constitutes an input portion (input shaft) and is divided into a gear shaft portion 3 and a pulley shaft portion 4. One end (the left end in FIG. 2) of the gear shaft portion 3 is projected to the outside of the casing 1, while the other end is located between the first and second split casings 1a and 1b. A gear 5 having a boss portion 5a penetrating the second split casing 1b is concentrically welded to the other end of the same so as to rotate together. The middle portion of the gear shaft portion 3 is supported by the first split casing 1a, and the hollow boss portion 5a of the gear 5 is supported by the second split casing 1b via bearings 6 and 7, respectively. On the other hand, the pulley shaft portion 4 is arranged between the second and third split casings 1b and 1c, and one end portion (the left end portion in FIG. 2) of the pulley shaft portion 4 has a small diameter, It is fitted in the boss portion 5a of the gear 5 which is integral with the motor 3 so as to be rotatable and integrally removable. The other half of the pulley shaft portion 4 is a small diameter portion and is supported by the third split casing 1c via a bearing 10.

Similarly, the second rotary shaft 12 is also divided into a gear shaft portion 13 and a pulley shaft portion 14. As shown in FIGS. 1 and 4, the gear shaft portion 13 penetrates the second split casing 1b, one end (the left end in FIG. 2) of which is the first split casing 1a, and the middle portion is the second split casing. It is supported by 1b via bearings 15 and 16, respectively. On the other hand, the pulley shaft portion 14 includes the second and third split casings 1.
It is a tubular member arranged between b and 1c, and the other end of the gear shaft 13 is spline-coupled to the one end (the left end in FIG. 2) so as to be able to rotate and to be pulled out, and the other end is the first end. It is supported by the three-part casing 1c via a bearing 17. With this structure, the casing 1 is divided into the first and second divided casings 1a and 1b and the third divided casing 1c.
The rotary shafts 2 and 12 are divided into the gear shaft portions 3,
By splitting into 13 and the pulley shaft portions 4 and 14, the continuously variable transmission A is unitized into a planetary gear mechanism 19 and a shift pulley mechanism 27, which will be described later, and can be split into two.

As shown in FIGS. 13 and 14, a driven pulley 91 composed of a V pulley is rotatably attached to the end of the first rotary shaft 2 projecting from the casing 1, and the driven pulley 91 and the engine E are connected to each other. Between the drive pulley 92, which is a V pulley attached to the output shaft E1, is V
A belt 93 is wound around, and the power of the engine E is transmitted to the first rotating shaft 2 of the transmission A via the V belt 93.

A tension pulley 94 for pushing the loose side span of the V-belt 93 from the rear side is disposed between the pulleys 91 and 92, and the tension pulley 94 is rotatably attached to the tip shaft portion of the tension arm 95. The tension arm 95 is supported and the tension pulley 94 is attached to the belt 9
It is urged to rotate by a spring (not shown) in the direction of pushing 3. Further, an actuator 96 such as an air cylinder for rotating the tension arm 95 against the biasing force of a spring or the like in the direction opposite to the belt pressing direction is provided, and the tension pulley 94, the tension arm 95, the actuator 96, etc. A tension clutch 97 is configured to cut off the power transmission between the pulleys 91 and 92, that is, between the engine E and the transmission A by eliminating the thrust on the V-belt 93.

Further, a limit switch 98 for detecting that the continuously variable transmission A is in a neutral state by switching the operation lever 66 to a neutral position which will be described later.
Is provided, and the actuator 96 such as the air cylinder operates in response to a neutral detection signal from the limit switch 98. When the continuously variable transmission A is in neutral, the tension clutch 97 causes the engine E to shift gears. By interrupting the power transmission to the device A,
The transmission A is in a state of being drive-connected only to the wheel side.

In the casing 1, a planetary gear mechanism 19 as a differential gear mechanism arranged on the left end of the second rotary shaft 12 and both rotary shafts 2 and 12 are driven by a V-belt 38 so as to be shiftable. The transmission pulley mechanism 27 to be connected is housed.

The planetary gear mechanism 19 is, as shown in enlarged detail in FIG. 5, a second rotary shaft 12 formed on a gear shaft portion 13 located between the first and second divided casings 1a and 1b. A sun gear 20 as a gear element, a plurality of pinions 21, 21, ... That mesh with the sun gear 20, and bearings 24, 24 near the first split casing 1a of the gear shaft portion 13 of the second rotating shaft 12 described above. An output gear 22 (pinion carrier), which is rotatably supported and rotatably carries the pinions 21, 21, ..., and an output gear 22 (pinion carrier), which is arranged at the outermost periphery and has bearings 25, 25 on the gear shaft portion 13. And a ring gear 23 as a first gear element that is rotatably supported via a pinion and engages with the pinions 21, 21 ,. Ring gear 2
The outer circumference 3 is meshedly connected to the gear 5 on the first rotary shaft 2. The output gear 22 constitutes an output portion of the transmission A and is drivingly connected to driving wheels (not shown).

The speed change pulley mechanism 27 includes the first rotary shaft 2
The first transmission pulley 28 is disposed on the pulley shaft portion 4 between the second and third divided casings 1b and 1c. As shown in the enlarged detail of FIG. 1, the first transmission pulley 28 has a boss portion 29 on the pulley shaft portion 4 of the first rotating shaft 2.
a fixed sheave 29 in the form of a flange, which is provided so as to rotate integrally with and is not slidable, and the fixed sheave 2 attached to the pulley shaft portion 4.
9 and a flange-shaped movable sheave 30 slidably and relatively rotatably provided at the boss portion 30a. The pulley groove 3 is provided between the sheaves 29 and 30.
1 is formed. The boss portion 30 of the movable sheave 30
The a is integrally formed with the sheave body 30b by forging.

On the other hand, a second speed change pulley 33 having the same diameter as that of the first speed change pulley 28 is provided on the pulley shaft portion 14 of the second rotary shaft 12. As shown in the enlarged detail of FIG. 4, the second speed change pulley 33 has the same structure as the first speed change pulley 28, and the boss portion 3 is provided on the pulley shaft portion 14 of the second rotary shaft 12.
4a, a flange-shaped fixed sheave 34 which is rotationally integrally and non-slidably key-joined, and the pulley shaft portion 14 of the movable sheave 30 facing the fixed sheave 29 of the first transmission pulley 28 with respect to the fixed sheave 34. A flange-shaped movable sheave 35 that is slidably and relatively rotatably coupled to the boss portion 35a so as to face each other in the opposite direction.
A pulley groove 36 is formed between the sheaves 34 and 35.

A V-belt 38, which is a block belt, is wound between the pulley groove 31 of the first speed change pulley 28 and the pulley groove 36 of the second speed change pulley 33. Each movable sheave 30,3
5 is moved toward and away from the fixed sheaves 29 and 34, respectively, to change the belt winding diameter of the pulleys 28 and 33. For example, when the movable sheave 30 of the first speed change pulley 28 is brought close to the fixed sheave 29 and the movable sheave 35 of the second speed change pulley 33 is separated from the fixed sheave 34, the belt winding diameter of the first speed change pulley 28 is changed. By making it larger than the second speed change pulley 33, the rotation of the first rotary shaft 2 is increased to the second speed.
The speed is increased and transmitted to the rotary shaft 12. On the other hand, conversely, when the movable sheave 30 of the first transmission pulley 28 is separated from the fixed sheave 29 and the movable sheave 35 of the second transmission pulley 33 is brought close to the fixed sheave 34, the first transmission pulley 28
By reducing the belt winding diameter and increasing the belt winding diameter of the second speed change pulley 33, the rotation of the first rotating shaft 2 is decelerated and transmitted to the second rotating shaft 12.

As shown in FIG. 1, the V-belt 38 has a pair of endless tensions in which a plurality of core wires are embedded in the upper and lower central portions of a shape-retaining layer made of fiber-reinforced rubber or fiber-reinforced plastic. Bands 39, 39 and fitting portions 40a, 40a for fitting the tension bands, respectively, are provided on the left and right side surfaces of the pulley 2
8 and 33, which are a plurality of substantially trapezoidal blocks 40, 40, ... Abuttable on the side surfaces of the pulley grooves 31, 36, and the upper and lower surfaces of the tension bands 39 and the fitting portions of the blocks 40. The blocks 40, 40, ... Are locked and fixed to the tension bands 39, 39 in the belt longitudinal direction by engaging the concavo-convex portions (not shown) formed on the upper and lower surfaces of the 40a so as to correspond to each other. For high load transmission,
It can withstand high lateral pressure.

Movable sheave 30 of the first transmission pulley 28
A torque cam mechanism 42 is arranged between the boss portion 30 a and the pulley shaft portion 4 of the first rotating shaft 2. As shown in FIGS. 6 to 8, the torque cam mechanism 42 is a torque pin 43 formed of a linear pin fixed to the first rotating shaft 2 so as to have a tip portion protruding from the outer peripheral surface and penetrating in the radial direction thereof.
And a torque ring 44 rotatably fitted to the protruding end of the torque pin 43, and the boss portion 3 of the movable sheave 30.
Torque cam holes 45, 45 penetratingly formed in the torque pin 43 and engaging with the torque ring 44 at the tip of the torque pin 43.
Consists of. The torque cam holes 45 are shown in FIGS.
As shown in FIG. 3, the one side wall has a predetermined lead angle θ1 with respect to the direction parallel to the axis of the rotary shaft 2.
The forward cam surface 45 inclined by (for example, θ1 = 26 °)
Similarly, a is formed on the other side wall with a reverse cam surface 45b that is inclined by the respective lead angles θ2 (for example, θ2 = 8 ° <θ1) smaller than the forward cam surface 45a. The torque cam mechanism 42 is actuated during each power transmission of A (vehicle) in the forward traveling state and the reverse traveling state, and the thrust on the belt 38 is applied in the opposite direction during the forward traveling and the reverse traveling. In order to obtain each movable sheave 30, 35, the fixed sheave 29, 34
It is designed to be pressed to the side.

On the pulley shaft portion 4 of the first rotary shaft 2, a drive mechanism for bringing the movable sheave 30 into and out of contact with the fixed sheave 29 on the rear side of the movable sheave 30 in the first transmission pulley 28. A first cam mechanism 47 is provided. As shown in FIG. 1, the cam mechanism 47 has a rotating cam 48, and the rotating cam 48 is fitted onto the boss portion 30a of the movable sheave 30 so as to cover the torque cam holes 45. On the cylindrical collar 51, the outer fitting is supported via a bearing 49 so as to be relatively rotatable and axially movable integrally. A pair of inclined cam surfaces 48a, 48a are formed on the end surface of the rotating cam 48 on the side opposite to the first transmission pulley 28 at equal angular intervals (180 ° intervals) in the circumferential direction, and the rotating lever is provided on the outer periphery. 50 is provided so as to rotate integrally.

A cylindrical fixed cam 51 as a cam follower integrally formed concentrically with the first rotary shaft 2 in the second split casing 1b is arranged on the rear side of the rotary cam 48. Rollers 52, 52 are rotatably supported by 51 so as to be in contact with the cam surfaces 48a of the rotating cam 48 and roll.

On the other hand, on the pulley shaft portion 14 of the second rotary shaft 12, the movable sheave 3 of the second speed change pulley 33 is provided.
The second cam mechanism 5 as a drive mechanism for bringing the movable sheave 35 into and out of contact with the fixed sheave 34 on the back side of
4 are provided. As shown in FIG. 6, the second cam mechanism 54 has a configuration similar to that of the first cam mechanism 47 and is rotatably and axially movable on the boss portion 35a of the movable sheave 35 via a bearing 55. It has a rotating cam 56 that is integrally fitted and supported. A pair of inclined cam surfaces 56a, 5a is provided on the end surface of the cam 56 opposite to the second speed change pulley 33.
6a are formed at equal angular intervals in the circumferential direction, and a turning lever 57 is provided on the outer circumference so as to integrally turn.

On the back side of the rotating cam 56, there is arranged a fixed cam 58 as a cam follower, which is formed by bulging the third divided casing 1c outwardly in a concentric cylindrical shape with the second rotary shaft 12, and this fixed Rollers 59, 59 that roll by contacting with the cam surfaces 56a of the rotating cam 56 are rotatably supported by the cam 58.

As shown in FIGS. 3 and 9, one end of a link 62 is connected to the tip of the rotating lever 50 of the first cam mechanism 47 via a pin 61, and the other end of the link 62 is the above-mentioned first. The rotation lever 57 of the two-cam mechanism 54 is connected to the tip of the rotation lever 57 via a pin 63.
7. Link mechanism 64 by link 62 and pins 61, 63
Is configured. By the interlocking mechanism 64, the cams 48, 56 of the cam mechanisms 47, 54 are interlocked with each other to rotate around the boss portions 30a, 35a of the movable sheaves 30, 35, and the rollers 52 are moved on the cam surfaces 48a, 56a. ，
By rolling 59, the movable sheaves 30 and 35 are moved in the axial direction to come into contact with and separate from the fixed sheaves 29 and 34, and the effective radii of the pulley grooves 31, 36, that is, the pulleys 28, 33. The belt winding diameter is variable, and the pulley ratio between the speed change pulleys 28 and 33 is changed.

Further, as shown in FIG. 15, in the interlocking mechanism 64 of the speed change pulley mechanism 27, the second cam mechanism 54 is used.
One end of a rod 65 is connected to the tip of the rotating lever 57, and the other end of the rod 65 is connected to an operation lever 66 as a switching operation unit via a rod 67. The operating lever 66 swings back and forth around the swing axis between the forward maximum speed position, the neutral position, and the reverse maximum speed position, and its shift pattern changes from the reverse maximum speed position to the neutral position. Then, when the vehicle is moved to the forward maximum speed position, it is once moved in the direction perpendicular to the rotation direction at the neutral position. The rod 67 is connected to the end portion of the operating lever 66, and the switching mechanism of the operating lever 66 actuates the interlocking mechanism 64 to rotate the rotating arms 50 and 56 protruding from the rotating cams 48 and 56. By rotating 57 between the forward maximum speed position, the neutral position and the reverse maximum speed position (see FIG. 3) and changing the speed ratio of the speed change pulley mechanism 27, the planetary gear mechanism 1
Output gear 22 (output section) as a pinion carrier of 9
Is switched to the normal rotation state, the neutral state, or the reverse rotation state with respect to the first rotation shaft 2 (input portion) to change the speed. In the neutral state, the belt winding diameter of the first speed change pulley 28 is, for example, 108 mm, and the second speed change is performed. The belt winding diameter of each pulley 33 is, for example, 72 mm. Further, by setting the gear ratio for the planetary gear mechanism 19, the rotational speed of the ring gear 20 drivingly connected to the first rotating shaft 2 is increased in the forward drive state of the vehicle in which the output gear 22 is rotated in the reverse direction with respect to the first rotating shaft 2. The rotation speed of the sun gear 20 connected to the second rotating shaft 12 is higher than that of the sun gear 20.

Further, there is provided a dead zone 68 for making it impossible to transmit the operating force of the operating lever 66 to the interlocking mechanism 64. The dead zone 68 includes, for example, a pin member 69 provided on the side of the rod 65 opposite to the rotation lever 38,
An engaging portion 7 provided on the operating lever 66 side of the rod 67 and engaging with the pin member 69 in the longitudinal direction of the rod 67.
And an engaging member 71 in which 0 is formed, and the engaging portion 70
Is a long groove (or a long hole) that slidably engages the pin member 69 for a predetermined distance. When the operation lever 66 is in the neutral position by the relative movement of the pin member 69 at the engaging portion 70. The operating force of the operating lever 66 cannot be transmitted to the interlocking mechanism 64.

The first and second speed change pulleys 28,
A pair of spans 38a of a V-belt 38 stretched between 33,
A tension mechanism 73 is provided that automatically generates a thrust on the belt 38 by automatically pressing the span on the loose side of 38b outward from its inner surface to apply tension to the belt 38. As shown in the enlarged detail of FIG. 4, the tension mechanism 73 has a structure in which the second rotary shaft 12 is provided in the second split casing 1b.
A first tension arm 75 in which a boss portion 75a is rotatably supported via a collar 74 on a bearing portion that is concentrically provided around the boss portion 75 of the first tension arm 75.
a second tension arm 76 having a boss portion 76a rotatably supported on a, and the first tension arm 75 is attached to the boss portion 76a of the second tension arm 76.
Is formed with a notch 76b. As shown in FIG. 3, the first tension arm 75 extends toward the first rotating shaft 2 and the tip portion thereof is bent upward. Also,
As shown in enlarged detail in FIG. 10, the first tension arm 7
One end of a tension shaft 77 extending parallel to both rotary shafts 2 and 12 is attached and fixed to an intermediate portion of the tension shaft 7.
The other end of 7 is the pulley groove 3 in each speed change pulley 28, 33.
1, 36, and the other end of the V belt 3
A first tension pulley 78 capable of pressing one of the eight spans 38a (upper side in FIG. 3) from the inner surface is rotatably supported via a bearing 79. On the other hand, one end of a tension shaft 80 extending parallel to both the rotary shafts 2 and 12 is attached and fixed to the tip end portion of the second tension arm 76, and the other end of the tension shaft 80 is the pulley groove 31 in each of the speed change pulleys 28 and 33. , 36 part, and a second tension pulley 81 capable of pressing the other span (the lower side in the figure) of the V-belt 38 from the inner surface is rotated at the other end through a bearing (not shown). It is supported freely. The positions of the tension pulleys 78 and 81 are always set to the tension pulley 7 regardless of the axial movement of the belt 38 due to the gear shift.
The outer surfaces of the belts 81 and 81 come into contact with a part of the inner surface of the belt 38 and are set at positions where they can be pressed.

A spring attachment arm 82 extending upward is integrally attached to the boss portion 76a of the second tension arm 76, and between the tip of the spring attachment arm 82 and the tip of the first tension arm 75. Is a tension spring 8
3, the first tension arm 75 is rotated clockwise by the spring force of the tension spring 83 and the second tension arm 76 is rotated counterclockwise in FIG. The tension pulleys 78 and 81 press the inner surfaces of the spans 38a and 38b of the V-belt 38, respectively. The tension biasing force of the tension spring 83 with respect to the tension arms 75 and 76 causes the tension pulleys 78 and 81 to loosen the spans 38 a and 3 of the belt 38.
8b is set to be pressed with a tension larger than the maximum tension generated in the loose side spans 38a, 38b,
The belt thrust is generated by this tension.

Further, each of the tension pulleys 78, 8 described above
1 is externally fitted and fixed to the outer surface of the outer race of the bearing as shown in detail in FIGS. Both side surfaces of the cross section of the tension pulleys 78 and 81 are parallel to the side surfaces of the pulley grooves 31 and 36 of the speed change pulleys 28 and 33, whereby the inclination angle θ3 of the side surfaces of the tension pulleys 78 and 81 is equal to the pulley groove 31. , 36, and the axial length of the outer circumference of each tension pulley 78, 81 is smaller than the width of the inner surface of the belt 38. Also,
The tension pulleys 78, 81 are made of fiber reinforced resin mixed with polyamide fibers (specifically, for example, 66 nylon resin mixed with 30% of glass fibers). 、…
I try to reduce the contact noise to.

A sleeve is rotatably fitted on the rotary shaft. This sleeve has
The boss portion of the fixed sheave is externally fitted so as not to be relatively movable in the axial direction and non-rotatably, and the boss portion of the movable sheave is externally fitted to be relatively movable in the axial direction and relatively non-rotatable. Have been combined.

As a feature of the present invention, as shown in FIG. 1, a sleeve 8 is rotatably fitted outside the pulley shaft portion 4 of the first rotating shaft. And this sleeve 8
In addition, the boss portion 29a of the fixed sheave 29 of the first speed change pulley 28 is externally fitted in a state in which the boss portion 29a of the fixed sheave 29 is relatively immovable in the axial direction and is relatively unrotatable by key connection, and the boss portion of the movable sheave 30 is 30a is externally fitted so as to be relatively movable in the axial direction and not relatively rotatable. The fixed sheave side end of the pulley shaft portion 4 is supported by a bearing 10 via a bush 9. On the other hand, the end portion of the sleeve 8 on the fixed sheave side is fitted to the large diameter portion 9a of the bush 9 but is not directly supported by the bearing 10 in the radial direction. The movement in the direction is allowed. Further, the bearing 10 is configured to support the thrust load of the sleeve 8 at the end portion on the fixed sheave side via the bush 9. The bush 9
The large diameter portion 9a covers the end of the sleeve 8 on the fixed sheave side in order to prevent scattering of the lubricating oil interposed between the bush 9 and the pulley shaft portion 4.

Next, the operation of the above embodiment will be described.

The on-vehicle engine E is drivingly connected to the first rotary shaft 2 of the continuously variable transmission A through the driving and driven pulleys 92, 91 and the V belt 93, and supports the pinions 21, 21, ... Of the planetary gear mechanism 19. Since the output gear 22 as a pinion carrier is drivingly connected to the drive wheels of the vehicle, the rotational power of the engine E is transmitted to the drive wheels after being speed-changed by the continuously variable transmission A. At this time, in the transmission A, the planetary gear mechanism 19 and the transmission pulley mechanism 27 are arranged in parallel in the power transmission path between the first rotary shaft 2 which is the input portion and the output gear 22 which is the output portion. During the operation of the transmission A, the power input from the first rotary shaft 2 is transmitted to the speed change pulley mechanism 27, the gear 5 on the first rotary shaft 2 and the planetary gear mechanism 19, and then the planetary gears. The power is output from the output gear 22 as a pinion carrier in the mechanism 19 as output power.

(At neutral) Specifically, when the operation lever 66 is positioned at the neutral position,
The output gear 22 of the planetary gear mechanism 19 has stopped rotating,
The continuously variable transmission A is in the neutral state and the engine E
Is not transmitted to the drive wheels, and the vehicle stops.

In this neutral state, the belt winding diameter of the first transmission pulley 28 of the transmission pulley mechanism 27 is, for example, 108 mm, the belt winding diameter of the second transmission pulley 33 is, for example, 72 mm, and the gear ratio is 0. At a predetermined value of 0.666, both the first and second speed change pulleys 28 and 33 are on the drive side (or the driven side).

At this time, the spring force of the tension spring 83 of the tension mechanism 73 causes the first tension arm 75 to move.
In the clockwise direction in FIG. 3 and the second tension arm 7
Since 6 is urged to rotate in the counterclockwise direction, the first tension pulley 78 moves the inner surface of the upper span 38a of the V-belt 38 in FIG. 3 when the operation lever 66 is in the neutral position. The second tension pulley 81 presses the inner surface of the lower span 38b with the same pressing force.

When the operating lever 66 is positioned at the neutral position, this is detected by the limit switch 98, and the actuator 96 such as the air cylinder in the tension clutch 97 is actuated in response to the neutral detection signal from the limit switch 98. Then
The tension arm 95 is rotated in the direction opposite to the direction in which the tension pulley 94 is pressed against the belt 93 against the biasing force of a spring or the like, and is pressed against the loose side span of the V belt 93 between the drive and driven pulleys 92 and 91. Is stopped, power transmission between the engine E and the transmission A is cut off,
The transmission A is connected only to the drive wheels.

At this time, in the speed change pulley mechanism 27, the fixed sheaves 29, 34 and the movable sheaves 30, 35 of the speed change pulleys 28, 33 are arranged so as to be located on the opposite sides with respect to the axial direction. Since the cam mechanisms 47 and 54 that bring the movable sheaves 30 and 35 into contact with and separate from the fixed sheaves 29 and 34 facing each other from the back side are linked by the interlocking mechanism 64, in the neutral state, both the transmission pulleys 28 and 33 will eventually move. Also on the drive side (or the driven side), the tension distribution of the belt 38 on both pulleys 28 and 33 is balanced, and the belt thrust forces are the same.

Then, in this neutral state,
Due to an external load from the driving wheels, the rotation of the output gear 22 with respect to the first rotating shaft 2 changes to the forward rotation side or the reverse rotation side even a little, and the belt winding diameter of one of the first or second speed change pulleys 28 and 33 changes to the other. More than two pulleys 2
8 and 33, the tension distribution of the belt 38 becomes unbalanced, and the belt thrust of the pulley 28 (or 33) on the side where the belt winding diameter is increased becomes smaller.
(Or 28), and the difference in the belt thrust increases as the load increases. This means that if the continuously variable transmission A changes from the true neutral state,
Due to the difference in the belt thrust, the winding diameter of the pulley 28 (or 33) on the side where the belt winding diameter is increased changes so as to be small, and a restoring force that automatically returns to the neutral state acts. Means that. In this embodiment, since the operation force transmission path from the operation lever 66 to the interlocking mechanism 64 is provided with the dead zone portion 68 for disabling the operation force of the operation lever 66 in the neutral state to the interlocking mechanism 64, When trying to return to the neutral state, the pin member 69 in the dead zone portion 68 freely moves at the engaging portion 70, and the restoration to the neutral state is not restricted. As described above, the continuously variable transmission A itself has a self-locking function to restore the neutral state. Therefore, if the tension clutch 97 cuts off the power on the input side (engine E side), the neutral state is stabilized. Therefore, the vehicle does not move carelessly and the stopping stability at the time of neutral can be improved.

Since the rotating levers 50 and 57 of the cam mechanisms 47 and 54 on the side of the speed change pulleys 28 and 33 are linked by the link 62, the speed change ratio of the speed change pulley mechanism 27 is changed by switching the operation lever 66. Can be changed to the output gear 22 of the planetary gear mechanism 19, that is, the output of the continuously variable transmission A in the normal rotation or reverse rotation state, and the rotation speed thereof can be increased.

(At the time of forward movement) That is, when the operation lever 66 is positioned at the forward movement position from the neutral state, the operation lever 66 is connected to the rotation lever 57 on the outer circumference of the rotation cam 56 of the second cam mechanism 54. Therefore, in the state of switching to the forward position, the cam 56 moves around the boss portion 35a of the movable sheave 35 in the second transmission pulley 33 while rolling the cam rollers 59, 59 on the cam surfaces 56a, 56a, respectively. Rotate in one direction. As a result, the cam surface 56a is pushed by the roller 59 and the cam 56
Moves on the second rotary shaft 12, and the movable sheave 35, which is integrated with the cam 56 via the bearing 55, moves in the same direction to approach the fixed sheave 34. As a result, the second speed change pulley 33 is closed and the belt winding diameter is increased from 72 mm in the neutral state to a maximum of 120 mm. Due to the increase in the belt winding diameter, the V-belt 38 is pulled toward the second speed change pulley 33 side. To be

At the same time, the operating lever 66 is
Is switched to the forward position, the second speed change pulley 33
In synchronization with the movement of the movable sheave 35 of the first cam mechanism 47.
Of the second cam mechanism 5 on the first rotary shaft 2.
It rotates in the same direction as the cam 56 of No. 4. The rotation of the cam 48 eliminates the pressing force on the cam roller 52.
Therefore, the tension of the belt 38 moving to the side of the second speed change pulley 33 causes the cam 48 and the bearing 49 thereof to move.
The movable sheave 30 connected through the fixed sheave 2
The sheaves 29 and 30 are moved away from each other, and the first transmission pulley 28 is opened by the separation of the sheaves 29 and 30 to reduce the belt winding diameter from 108 mm in the neutral state to a minimum of 60 mm. As a result, the belt winding diameter of the second speed change pulley 33 becomes larger than that of the first speed change pulley 28, and the rotation of the second rotary shaft 12 is accelerated to increase the first speed.
It is transmitted to the rotary shaft 2. With this gear ratio, the output gear 22 as the pinion carrier rotates in the reverse rotation state with respect to the first rotation shaft 2, and the output power of the engine E drives the drive wheels to rotate in the forward direction of the vehicle, so that the gear ratio is increased. By changing the position to the maximum speed position, the rotational speed of the output gear 22 in the forward rotation direction, that is, the forward speed can be increased.

At this time, the input power is set as a drive power path through the gear 5 and the ring gear 23 of the planetary gear mechanism 19 to the output gear 22, and the sun gear 20 of the planetary gear mechanism 19 to the second rotary shaft 12 or. Speed change pulley mechanism 27
Is transmitted as a circulating power route. That is, generally, the frequency of use of the vehicle in the forward drive state is higher than that in the reverse drive, and since the speed change pulley mechanism 27 serves as the circulation power route during the forward drive, the drive power of the belt 38 is high frequently over a long period of time as a whole. It is possible to transmit a circulating power smaller than that, and it is possible to reduce the transmission load of the belt 38 even at the time of high output in a forward state where it is frequently used.

When the speed change pulley mechanism 27 is in the circulating power path, the second speed change pulley 33 is the driving side pulley, while the first speed change pulley 28 is the driven side pulley, and the belt 38 has the upper side in FIG. The span 38a of the V belt 3 is on the loose side, but the first tension pulley 78 is
8, both tension arms 75 and 76 are urged to rotate in opposite directions by the tension spring 83 so that the second tension pulley 81 presses the upper span 38a and the second tension pulley 81 presses the lower span 38b. The second tension pulley 81 pressing the inner surface of the tension side span 38b moves to the upper side in FIG. 3, and the second tension arm 76 rotates clockwise, whereby the tension spring 83 is extended. Accordingly, the first tension arm 75 also rotates clockwise, and the first tension pulley 78 presses the inner surface of the upper span 38a with a predetermined pressing force in FIG. , Belt tension is obtained. Both tension arms 75 and 76 are rotationally biased in the opposite directions by the biasing force of the tension spring 83 of the tension mechanism 73, and the tension pulleys 78 and 81 at the tips of the tension arms 75 and 76 are respectively attached to the inner surfaces of the loose side spans 38a and 38b of the belt 38. The tension is applied to the belt 38 by this pressure, but since this tension is larger than the maximum tension generated in the loose side spans 38a, 38b, this belt tension causes the pulley 2 of the belt 38 to move.
A wedge effect is generated on the wheels 8 and 33 to generate thrust, and this thrust transmits power between the pulleys 28 and 33 via the belt 38.

Further, the boss portion 30a of the movable sheave 30 of the first speed change pulley 28 and the pulley shaft portion 4 of the first rotating shaft 2 are arranged.
A torque cam mechanism 42 is provided between the torque cam mechanism 42 and the torque cam mechanism 45, and forward and backward cam surfaces 45a and 45b are formed on both side walls of each torque cam hole 45 of the torque cam mechanism 42. When the movable sheave 30 and the first rotating shaft 2 rotate relative to each other due to the transmission load of the movable sheave 3, the forward cam surface 45a of each torque cam hole 45 comes into contact with the torque ring 44 at the tip of the torque pin 43.
0 is pushed in the axial direction and moves away from the fixed sheave 29, and the movement of the movable sheave causes the first cam mechanism 4 to move.
7 rotation cam 48, interlocking mechanism 64 and second cam mechanism 54
The movable sheave 35 of the second speed change pulley 33 is pressed toward the fixed sheave 34 side via the rotating cam 56, and the thrust of the speed change pulley 33 with respect to the belt 38 can be increased.

On the other hand, when the operation lever 66 is positioned at the reverse position, the cam 48 of the first cam mechanism 47 causes the cam 48 of the first cam mechanism 47 to move to each of the cam surfaces 4 when the control lever 66 is positioned at the reverse position.
While rotating the cam roller 52 on the 8a, the cam roller 52 rotates in the other direction around the boss portion 30a of the movable sheave 30 of the first transmission pulley 28. As a result, the cam surface 48a is pushed by the roller 52 and the cam 48 moves on the first rotary shaft 2, and the movable sheave 30 that is integral with the cam 48 moves in the same direction and approaches the fixed sheave 29. . As a result, the first speed change pulley 28 is closed and the belt winding diameter is increased from 108 mm in the neutral state to a maximum of 120 mm. Due to the increase in the belt winding diameter, the V-belt 38 is pulled toward the first speed change pulley 28 side. To be

Further, the cam 56 of the second cam mechanism 54 is moved to the second position as the operation lever 66 is switched to the reverse position.
The rotary shaft 12 is rotated in the same other direction as the cam 48 of the first cam mechanism 47. The rotation of the cam 56 eliminates the pressing force on the cam roller 59. Therefore, the first
Due to the tension of the belt 38 that moves to the speed change pulley 28 side,
The cam 56 and the movable sheave 35 connected thereto via the bearing 55 move on the second rotary shaft 12 in the direction away from the fixed sheave 34, and the separation of the sheaves 32, 33 opens the second transmission pulley 33. The belt winding diameter is reduced from 72 mm in the above neutral state to a minimum of 60 mm. As a result, the belt winding diameter of the first speed change pulley 28 becomes larger than that of the second speed change pulley 33.
The rotation of the rotary shaft 2 is accelerated and transmitted to the second rotary shaft 12. With this gear ratio, the output gear 22 rotates in the first direction.
When the drive wheel is rotated in the reverse direction of the vehicle by the output power of the engine E and the gear ratio is changed to the reverse maximum speed position, the rotational speed of the output gear 22 in the reverse direction, that is, The reverse speed can be increased.

At this time, contrary to the above-described forward movement, the input power is driven by the path from the speed change pulley mechanism 27 or the second rotary shaft 12 to the sun gear 20 of the planetary gear mechanism 19 as the drive power path. From the output gear 22 as the pinion carrier to the pinion 21, 21 ,.
3 and the gear 5 are transmitted to the first rotary shaft 2 as a circulating power route.
Is a driving power path, a large driving power acts on the V-belt 38, which may reduce its durability. However, as described above, the frequency of use of the vehicle in the reverse drive state is generally lower than that in the forward drive. Since the V-belt 38 is low, a high transmission load is applied to the V-belt 38 for only a short time, and the durability of the belt 38 is not significantly reduced.

In this reverse drive state, the first speed change pulley 28 becomes the drive side pulley, the second speed change pulley 33 becomes the driven side pulley, and the lower span 38b of the belt 38 in FIG. Become. At this time as well, since both tension arms 75 and 76 are urged to rotate in the opposite directions by the tension springs 83, the first tension pulley 78 that presses the inner surface of the tension side span 38a in the same manner as described above. 3, the first tension arm 75 rotates counterclockwise, and the second tension arm 76 also rotates counterclockwise by the spring force of the tension spring 83.
The second tension pulley 81 presses the inner surface of the lower span 38b in FIG. 3 on the loose side of the belt 38 with a predetermined pressing force, whereby the belt tension can be obtained.

In this reverse drive state, when the movable sheave 30 of the first shift pulley 28 and the first rotary shaft 2 rotate relative to each other due to the transmission load of the shift pulley mechanism 27, the reverse cam surface 45b of each of the torque cam holes 45 described above. Comes into contact with the torque ring 44 at the tip of the torque pin 43 to move the movable sheave 30 in the axial direction in the direction toward the fixed sheave 29, and the movement of the movable sheave 30 causes the belt 3 in the first transmission pulley 28 to move.
The thrust on 8 can be increased.

Therefore, in this embodiment, as described above, the planetary gear is set so that the rotational speed of the ring gear 23 is always higher than the rotational speed of the sun gear 20 on the forward side, which is frequently used in the forward or reverse drive state of the vehicle. Since the gear ratio to the mechanism 19 is set, the frequency with which a small circulating power is transmitted to the belt 38 of the speed change pulley mechanism 27 is increased and the frequency with which a large driving power is transmitted to the belt 38. Therefore, the load on the belt 38 can be reduced, and the forward / reverse rotation state of the continuously variable transmission A can be easily obtained without a separate forward / reverse rotation mechanism.

Further, the boss portion 30 of the movable sheave 30, 35 in each of the transmission pulleys 28, 33 of the transmission pulley mechanism 27.
a, 35a, the rotation cam 48 of each cam mechanism 47, 54,
56 is supported via bearings 49 and 55, and the rotary levers 50 and 57 on the outer circumferences of both rotary cams 48 and 56 are connected by one link 62. Therefore, when shifting the speed of the shift pulley mechanism 27, A force acts on the cam surfaces 48a, 56a of the rotating cams 48, 56 from the rollers 52, 59 supported by the fixed cams 51, 58 in a direction perpendicular to the cam surfaces 48a, 56a, and the rotary shafts 2, 12 of this force are applied. When the perpendicular component force in the orthogonal direction acts at right angles to the line connecting the axis of the rotating shafts 2 and 12 and the connecting point to the link 62, the axis of the rotating shafts 2 and 12 and the connecting point to the link 62 are Despite the change in the pulley ratio, a cam rotation reaction force that is perpendicular to the line connecting the lines and that is opposite to the above-mentioned right angle component force is generated, and this cam rotation reaction force is generated by the rotation cams 48, 56.
Boss 30 of movable sheave 30, 35 supporting
a, 35a, the boss portion 30 at the center position in the range in which the belt 38 of the pulleys 28, 33 is wound.
It acts so as to press a and 35a. That is, the cam rotation reaction force on the boss portions 30a and 35a is
When the movable sheaves 30 and 35 receive thrust from the belt 38, the movable sheaves 30 and 35 are moved by the clearances in the sliding portions between the rotary shafts 2 and 0a and 35a.
12 acts to generate a moment in the direction opposite to the moment acting in the tilting direction, and the original moment is offset by this moment and becomes smaller, and the inner circumference of the boss portions 30a, 35a of the movable sheaves 30, 35 rotates. Axis 2,
12 The surface pressure distribution on the outer circumference is dispersed in the axial direction, and the sliding resistance of the boss portions 30a and 35a is reduced. The rotation cam 4 of the thrust generated by the belt corresponds to the decrease in the sliding resistance.
Load applied to fixed points by 8,56 (that is, extraction thrust)
Is increased, in other words, the belt-generated thrust is transmitted to the rotating cams 48 and 56 as extraction thrust without great resistance. And when changing the pulley ratio,
Since the difference between the belt-generated thrust and the take-out thrust is the load (operating force) required for the gear shifting operation, the larger the take-out thrust is, the conversely the smaller the operating force is required. As a result, the resistance at the time of shifting to the neutral state due to the thrust balance of the belt 38 between the transmission pulleys 28 and 33 in the transmission pulley mechanism 27 becomes small, and the neutral state is smoothly adjusted, so that the neutral state is further improved. It can be held stably.

The first tension pulley 78 is the upper span 38a of the V-belt 38 shown in FIG. 3, and the second tension pulley 81 is the lower span 38b of the V-belt 38.
Both tension arms 7 so that
5, 76 are urged to rotate in the reverse direction by a tension spring 83,
Since the pressing force to the loose side span 38b (or 38a) is obtained by the return of the tension side span 38a (or 38b) of the belt 38, the tension of the belt 38 is increased as described above when switching between forward and reverse. Both tension pulleys 7
While keeping the distance between 8 and 81 constant, the slack side span can be automatically pressed, and stable belt tension can be obtained.

Moreover, since the tension arms 75 and 76 are urged to rotate by using the tension springs 83, there is no fear that the springs will buckle as when using compression springs, and a proper spring constant can be obtained. It is also possible to stabilize the belt tension. Incidentally, in this way, both spans 38 of the belt 38 are
The inner surfaces of a and 38b are respectively tension pulleys 78 and 81.
Instead of pressing with a pair of tension pulleys, the pair of tension pulleys are arranged so that the back surfaces of the spans 38a and 38b of the belt 38 can be pressed, and the tension arms supporting the tension pulleys are rotated in the belt pressing direction by tension springs. A biasing force may be applied.

Further, the above-mentioned two tension pulleys 7
The axial length of each circumferential surface of each of the pulleys 8, 81 is smaller than the width of the inner surface of the belt 38, and the tension pulleys 78, 8
1 is arranged between both spans 38a and 38b of the belt 38 and presses the respective spans 38a and 38b from the inner surface side to give a belt thrust, so that the span 38 between the spans 38a and 38b of the belt 38 is The tension pulleys 78 and 81 can be arranged using the dead space, and the transmission A can be made compact.

Moreover, each of the tension pulleys 78, 8 described above
The inclination angle of one side is the pulley groove 3 of the speed change pulleys 28 and 33.
Since the cross-section angles of the pulleys 1 and 36 are the same, the tension pulleys 78 and 81 correspond to the pulley grooves 3 of the speed change pulleys 28 and 33.
Even if it moves into the inside of 1, 36, it does not interfere with the side surfaces of the pulley grooves 31, 36, and the tension pulleys 78, 81 having a large outer diameter are used to make the spans 38a, 3 of the belt 38.
While reducing the bending rate of 8b, the axial distance between both rotary shafts 2 and 12 is shortened, and both rotary shafts 2 and 1 in transmission A are
2 can be made compact in the direction between the axes.

Further, the positions of the tension pulleys 78 and 81 are irrespective of the axial movement of the belt 38 due to the gear shift,
Since the outer surfaces of the tension pulleys 78, 81 are always in contact with a part of the inner surface of the belt 38 and can press it, the width of the tension pulleys 78, 81 is equal to the width of the belt 3 as described above.
8 is smaller than the width of the inner surface, and the belt 38 moves axially along the side surface of the pulley grooves 31, 36 on the side of the fixed sheaves 29, 34 while the winding diameter is changed by opening and closing the speed change pulleys 28, 33. Even tension pulleys 78, 8
1 does not deviate from the position of the belt 38 in the axial direction so that the loose side spans 38a and 38b cannot be pressed.
8 can be pressed stably.

Further, the tension pulleys 78, 81
Is made of a fiber reinforced resin mixed with polyamide fibers, wear of the block V-belt 38 due to contact with the tension pulleys 78, 81 can be reduced, and the blocks 40, 40, ... Even if the block belt 38 is on, each block 4
It is possible to reduce the hitting sound when 0 comes into contact with the tension pulleys 78 and 81 intermittently, and to reduce noise.

First shift pulley 28 of shift pulley mechanism 27
Since the boss portion 30a of the movable sheave 30 is subjected to high surface pressure by the torque cam mechanism 42, the boss portion 30a and the sheave body 30b are forged instead of being cast.
Since and are integrally formed, compared with the case where both are separately manufactured and then welded to be integrated, the roundness of the movable sheave 30 can be improved by eliminating welding distortion, and high load transmission can be achieved. The runout of the V-belt 38 that is performed can be reduced, its wear can be suppressed, and reliability can be improved.

Movable sheave 30 of the first speed change pulley 28
A torque cam mechanism 42 is provided between the boss portion 30a of the first rotating shaft 2 and the pulley shaft portion 4 of the first rotating shaft 2, and the torque cam holes 45 of the torque cam mechanism 42 are provided with forward and backward cam surfaces 45a and 45b. Since they are respectively formed, the movable sheaves 30 and 35 are fixed by the torque cam mechanism 42 not only when the vehicle moves forward but also when the vehicle moves backward.
The belt thrust can be increased by moving it axially to the side.

At this time, on the forward side, the pulley ratio of the speed change pulley mechanism 27 is in the Lo state in which the belt winding diameter of the first speed change pulley 28 is smaller than that of the second speed change pulley 33.
The belt thrust difference between the driving side pulley and the driven side pulley becomes large, while the pulley ratio of the speed change pulley mechanism 27 becomes Hi on the reverse side.
In this state, the belt thrust difference between the drive side driven pulley 28 and the driven side pulley 33 becomes small, but the lead angle of the forward cam surface 45a in each of the torque cam holes 45 is the reverse cam surface 4
Since it is set to be larger than the lead angle θ2 of 5b, it is possible to obtain an appropriate belt thrust in accordance with the characteristics of the belt thrust difference at the time of traveling in the forward and backward directions.

In addition, the torque pin 43 of the torque cam mechanism 42 is diametrically penetrated by the pulley shaft portion 4 of the second rotary shaft 12, and the torque ring 44 is supported by the tip protrusions on both sides thereof. The verticality of 43 itself can be increased, and it is possible to prevent one-sided contact of the torque ring 44 with the cam surfaces 45a and 45b of the torque cam hole 45.

Further, the pinions 21, 21, ... In the planetary gear mechanism 19 are output gears 22 on the second rotary shaft 12.
Since the output gear 22 is drivingly coupled to the drive wheels, the output gear 22 can also be used as a pinion carrier to reduce the number of parts, and the pinion carrier as an output portion can be mounted on the second rotary shaft 12. The length of the second rotating shaft 12 can be shortened as compared with the case of being connected to the drive wheel side, and the continuously variable transmission A can be made compact in the axial direction.

Further, the casing 1 of the continuously variable transmission A is divided into three first to third divided casings 1a, 1b and 1c, and the first and second rotary shafts 2 and 12 are respectively the first.
And the gear shaft portions 3, 13 located between the second split casings 1a and 1b, and the second and third split casings 1b and 1c.
It is divided into two parts in the axial direction into the pulley shaft parts 4 and 14 located between them, and the planetary gear mechanism 19 and the gear 5 are respectively provided on the gear shaft parts 3 and 13, and the speed change pulley mechanism 27 is provided on the pulley shaft parts 4 and 14. Since they are arranged, the continuously variable transmission A can be unitized into each arrangement portion of the transmission pulley mechanism 27 and the planetary gear mechanism 19 and can be divided into two parts. Therefore, when inspecting or repairing, for example, the belt 38 of the speed change pulley mechanism 27 or exchanging parts of the planetary gear mechanism 19, the remaining parts of both units may be left as they are and only the necessary side unit may be removed and disassembled. , Maintenance and inspection of parts and steel pipes can be performed easily.

A sleeve 8 on the side of the gear shaft 3 and a bush 9 on the side opposite to the gear shaft 3 are provided in the small diameter portion of the half portion of the pulley shaft 4 of the first rotary shaft 2 on the side of the speed change pulley mechanism 27.
Are fitted to each other, the fixed sheave 29 of the first speed change pulley 28 is supported on the sleeve 8, and the bush 9 is supported by the third divided casing 1c via the bearing 10, so that the fixed sheave 29 is supported. The partial sleeve 8 is separated from a bush 9 for supporting the bearing 10. Therefore, when an axial load is applied to the fixed sheave 29 from the V belt 38, the fixed sheave 29 faces inward with the position of the bearing 10 as a fulcrum, that is, the outer peripheral edge of the fixed sheave 29, as in the case of the non-separated structure. Is the pulley groove 31
The belt 38 can be prevented from tilting toward the side.
One-sided wear of the fixed sheave 29 can be suppressed.

Furthermore, the sleeve 8 is externally fitted on the pulley shaft portion 4 to which the torque pin 43 of the torque cam mechanism 42 is attached in the first rotating shaft 2, and the first shift pulley 28 is fixed and fixed on the sleeve 8. Since both the movable sheaves 29 and 30 are fitted and supported, the force exerted by the belt 38 on the fixed and movable sheaves 29 and 30 is the same as when the fixed sheave 29 is directly keyed to the pulley shaft portion 4. The relative rotation between the movable sheave 30 and the pulley shaft portion 4 of the first rotating shaft 2 is not impaired by the action, and the movable sheave 30 and the pulley shaft of the first rotating shaft 2 are obtained while the belt thrust is obtained by both sheaves 29 and 30. The relative rotation with respect to the portion 4 can be enabled, and the operation of the torque cam mechanism 42 can be favorably ensured.

Moreover, since the torque cam mechanism 42 is provided on the side of the first speed change pulley 28 that is the driven side of the circulating power in the forward movement of the continuously variable transmission A, even if the lead angle of the torque cam hole 45 is constant. It is possible to easily take out the necessary belt thrust force according to the gear ratio.

The movable sheave 3 of the first speed change pulley 28
A cylindrical collar 51 is fitted on the boss portion 30a of No. 0 so as to cover each torque cam hole 45, and a bearing 49 is mounted thereon.
Since the rotating cam 48 of the first cam mechanism 47 is supported via the, the torque cam hole 45 of the torque cam mechanism 42 can be sealed with the collar 51, and the lubricating oil filled in the torque cam hole 45 is exposed to the outside. Can be effectively prevented.

In the above embodiment, the fixed sheave side end of the pulley shaft portion 4 of the first rotary shaft 2 is supported by the bearing 10 via the bush 9, but another member such as the bush 9 is interposed. Instead, the bearings may be directly supported.

Further, in the above embodiment, the bearing 10 receives the thrust load of the sleeve 8 via the bush 9, but it may be directly contacted with the bearing as in the above.

[0081]

As described above, according to the first aspect of the invention, the movable sheave is moved in the axial direction by utilizing the turning force between the movable sheave and the rotary shaft. In a speed change pulley configured to change a belt winding diameter, a sleeve is rotatably fitted onto the rotary shaft, and a fixed sheave is fixed on the sleeve such that the fixed sheave cannot move in the axial direction and cannot rotate relatively. Moreover, since the movable sheave can be relatively moved in the axial direction and is non-rotatably fitted to each other, the fixed sheave can be rotated together with the movable sheave through the sleeve, so that the movable sheave is rotated. It is possible to avoid a situation in which a displacement of the movable sheave and the fixed sheave in the rotational direction occurs when the movable sheave rotates with respect to the shaft, and the rotational movement of the movable sheave with respect to the rotary shaft is restricted by the belt. From this, it is possible to increase the rotation width of the movable sheave with respect to the rotation shaft and increase the force for moving the movable sheave in the axial direction in the torque cam mechanism, and thus to increase the transmission capability of the speed change pulley. .

According to the second aspect of the invention, the bearing portion for rotatably supporting the fixed sheave side end portion of the rotary shaft allows the fixed sheave side end portion of the sleeve to move in the radial direction. Therefore, it is possible to avoid the variation in the clearance change between the sleeve and the rotating shaft that occurs when the fixed sheave side end portion is restricted from moving in the radial direction by the bearing portion. It is possible to suppress one-sided wear that occurs in the fixed sheave and the belt due to tilting toward the pulley groove, which is opposite to that of the movable sheave.

According to the third aspect of the invention, since the thrust load of the sleeve is supported by the end portion of the fixed sheave side by the bearing portion, it is possible to prevent the fixed sheave from moving in the axial direction. As the movable sheave is moved in the axial direction, each belt winding diameter can be appropriately maintained.

[Brief description of drawings]

FIG. 1 is an enlarged cross-sectional view showing a structure around a first shift pulley of a shift pulley mechanism in a continuously variable transmission according to an embodiment of the present invention.

FIG. 2 is a front view showing the structure of a speed change pulley mechanism.

FIG. 3 is a cross-sectional plan view showing the overall configuration of a continuously variable transmission.

FIG. 4 is an enlarged cross-sectional view showing a structure around a second speed change pulley of the speed change pulley mechanism.

FIG. 5 is an enlarged cross-sectional view showing a structure around a differential gear mechanism.

FIG. 6 is an enlarged cross-sectional view of a movable sheave of the first transmission pulley.

FIG. 7 is an enlarged front view of a movable sheave.

FIG. 8 is an enlarged front view of a torque cam groove in the movable sheave of the torque cam mechanism.

FIG. 9 is an enlarged plan view showing a link of the interlocking mechanism.

FIG. 10 is an enlarged cross-sectional view showing a state in which a spring is attached to the first tension arm.

FIG. 11 is a sectional view of a tension pulley of the tension mechanism.

FIG. 12 is a front view of a tension pulley of the tension mechanism.

FIG. 13 is a plan view showing a drive connection state of the continuously variable transmission with respect to the engine.

FIG. 14 is a front view showing a drive connection state of the continuously variable transmission with respect to the engine.

FIG. 15 is a diagram schematically showing a connecting structure of an interlocking mechanism and an operation lever.

[Explanation of symbols]

 2 1st rotary shaft (rotary shaft) 8 sleeve 10 bearing (bearing part) 28 1st speed change pulley (speed change pulley) 29 fixed sheave 29a boss part 30 movable sheave 30a boss part 31 pulley groove 38 block V belt (torque) 42 torque cam mechanism

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Yutaka Furukawa 3-15-15 Meiwa Dori, Hyogo-ku, Kobe, Hyogo Prefecture Bando Kagaku Co., Ltd.

Claims (3)

[Claims] 1. A rotary shaft rotatably supported about an axis, a fixed sheave supported by the rotary shaft at a boss portion, and a fixed sheave supported by the rotary shaft at a boss portion by the fixed sheave. The movable sheave that forms a pulley groove around which the belt is wound is provided between the movable sheave rear side portion of the rotary shaft and the boss portion of the movable sheave, and is movable by relative rotation between the rotary shaft and the movable sheave. A transmission pulley having a torque cam mechanism for moving a sheave in the axial direction to change a belt winding diameter of the pulley groove, wherein the sheave is rotatably fitted to the rotary shaft and the boss portion of the fixed sheave is a shaft. And a boss portion of the movable sheave provided with a sleeve that is relatively movable in the axial direction and is non-rotatably fitted. Variable speed pulley according to claim. 2. The transmission pulley according to claim 1, further comprising a bearing portion that rotatably supports a fixed sheave side end portion of the rotating shaft, wherein the bearing portion moves the fixed sheave side end portion of the sleeve in a radial direction. A variable speed pulley characterized in that it is configured to allow. 3. The transmission pulley according to claim 2, wherein the bearing portion is configured to support the thrust load of the sleeve at its fixed sheave side end portion.