JPH1151133A - Shift device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a seizure or a gall at the time of a shift operation and simplify a structure, and attain miniaturization and decrease of costs. SOLUTION: The subject shift device is equipped with a rotary driving force transmission member 45 which can move in the axial direction, a roller 75 on the periphery of which an engaging part 77, engaged with an engaging part 79 installed on the member 45, is provided, an operating member 81 which supports the roller 75 through a bearing 83 and can move in the axial direction of the member 45, and an actuator which operates the movement of the member 45 through the operating member 81 and the roller 75.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to, for example, a transmission mechanism of a belt-type continuously variable transmission or a shift device used for a transmission of a vehicle.

[0002]

2. Description of the Related Art Japanese Patent Publication No. 4-134471 discloses a transmission 201 as shown in FIG. In addition, JP
Japanese Patent Publication No. 1453 discloses a transmission 203 as shown in FIG.

A transmission 201 shown in FIG. 7 is a switching mechanism for a transmission of a vehicle.
7, the shift slider 209 moves the guide shaft 2
11 and selectively meshes with a plurality of forks 213. Each fork 213 is engaged with an outer peripheral groove 217 of a different slide gear 215. Next, when the shift lever 205 is operated in a direction perpendicular to the plane of the drawing, the slide gear 215 is shifted through the engaged fork 213. The gear is engaged with the mating gear to perform the speed change.

A transmission 203 shown in FIG. 8 is a transmission of a belt-type continuously variable transmission. The belt-type continuously variable transmission includes a transmission pulley 223 having a fixed flange 219 and a movable flange 221, and a belt 225. The transmission 203 is provided with another transmission pulley connected to the transmission pulley 223, and the transmission 203 is moved by operating the movable flange 221 to change the pulley pitch diameter of each transmission pulley.

The transmission 203 is configured to move the fork 227 by a geared motor. The fork 227 is connected to the outer periphery of the boss 229 of the movable flange 221 via a bearing 231.

[0006]

However, in the transmission 201 shown in FIG. 7, the fork 213 is configured to slide with the outer peripheral groove 217 of the slide gear 215 at the time of a gear change operation, and this sliding resistance is reduced. Since there is no means, there is a possibility that seizure or galling may occur between the fork 213 and the outer peripheral groove 217 due to large heat generation.

Therefore, in order to prevent seizure and galling, it is necessary to use the transmission 201 for an extremely low-speed rotation device or to immerse the oil in oil and sufficiently lubricate the slide gear 215. When the sliding speed increases to some extent, the transmission 201 cannot be used.

When the transmission 201 is immersed in oil, the resistance of the oil causes a large transmission loss of driving force.

On the other hand, in the transmission 203 shown in FIG. 8, a bearing 231 is provided between the fork 227 and the movable flange 221.
To prevent seizure and galling.

However, the boss portion 22 of the movable flange 221
Since the diameter of the bearing 231 arranged on the outer periphery of 9 becomes large, it is extremely expensive.

Further, since the large-diameter bearing 231 has a high peripheral speed, the effect of preventing seizure and galling and the durability are low.

Further, the configuration using the geared motor and the large-diameter bearing 231 is expensive, has a complicated structure, easily breaks down, and is large.

In view of the above, the present invention is configured to perform a moving operation while rotating a rotary driving force transmitting member, and to have a simple structure, high reliability and a small size while preventing image sticking and galling during the moving operation. It is intended to provide a low-cost shift device.

[0014]

According to a first aspect of the present invention, there is provided a shift device, comprising: a rotational driving force transmitting member movable in an axial direction; a circumferential engaging portion provided on the rotational driving force transmitting member; A roller that engages with the engaging portion of the rotary driving force transmitting member with the provided engaging portion, an operating member that rotatably supports the roller and is movable in the axial direction of the rotary driving force transmitting member; An actuator for moving the rotational driving force transmitting member via the operating member and the roller is provided.

As described above, in the shift device of the present invention, the roller is supported by the operating member, and the engaging portion provided on the outer periphery of the roller is engaged with the engaging portion of the rotational driving force transmitting member.

Accordingly, when the operating member (roller) is moved by the actuator, the rotational driving force transmitting member engaged with the roller shifts while rotating, and at this time, the roller also rotates.

In this way, the sliding when the rotational driving force transmitting member is shifted is absorbed by the rotation of the roller, so that seizure and galling are prevented, and the durability is greatly improved.

Further, the diameter of the roller is reduced by engaging the rotational driving force transmitting member at the engaging portion on the outer periphery, and the sliding speed (peripheral speed) between the roller and the operating member is reduced.
As a result, the effect of preventing seizure and galling and the effect of improving durability are high.

Therefore, the shift device of the present invention is suitable not only for a low-speed rotation type device but also for a high-speed rotation type device.

Further, since the shift device does not need to be immersed in oil in order to prevent seizure and galling, it is free from loss of driving force due to oil resistance.

Further, unlike the conventional example shown in FIG. 8, since no geared motor or large-diameter expensive bearings are used, the cost is greatly reduced, and the structure is simple, so that the reliability is high and the size is small. .

According to a second aspect of the present invention, there is provided the shift device according to the first aspect, wherein a bearing is disposed between the roller and the operating member, and an effect equivalent to that of the first aspect is obtained. .

In addition, the sliding resistance between the roller and the operating member is further reduced by arranging a sliding bearing such as a bush or a rolling bearing between the roller and the operating member, for example. The effect of preventing seizure and galling and the durability are greatly improved.

Further, the bearing arranged between the roller and the operating member has a small diameter, and therefore has a small peripheral speed. Therefore, the effect of preventing seizure and galling and the effect of improving the durability are high, and the small diameter and low cost are achieved. Advantageously, a bearing can be used.

Further, if a shield type bearing is used, it can be used as a shift device in a dry state.

According to a third aspect of the present invention, there is provided the first or second aspect.
The shift device according to claim 1, wherein the engaging portion of the rotational driving force transmitting member and the engaging portion of the roller include a plurality of sets of circumferential protrusions and circumferential grooves that mesh with each other. An effect equivalent to that of the configuration of item 2 is obtained.

In addition to this, the engaging portion between the rotary driving force transmitting member and the roller is formed as a convex portion and a circumferential groove which mesh with each other, and a plurality of sets of these are provided. Since the contact area between the roller and the rotational driving force transmitting member is increased, and the surface pressure is dispersed and reduced, the effect of preventing image sticking and galling and the durability are greatly improved.

The invention according to claim 4 is the invention according to claims 1 to 3.
The shift device according to any one of claims 1 to 3, wherein the operating member is shaft-shaped, and one roller is coaxially arranged on the shaft-shaped member. The same effect is obtained.

In addition, the structure in which one roller is coaxially arranged on the shaft-like operation member is simple and compact, and the shift device is correspondingly small and the cost is low.

The invention of claim 5 is the invention of claims 1 to 3
The shift device according to any one of the preceding claims, wherein the operating member comprises a shaft-shaped member, and an arm member fixed to the shaft-shaped member and projecting a plurality of distal ends around the rotation driving force transmitting member. The roller is rotatably supported at each end of the arm member, and the same effect as in any one of claims 1 to 3 is obtained.

In addition, by using a plurality of rollers, the load on each roller is reduced, and the effect of preventing seizure and galling and the durability are greatly improved.

Further, if a plurality of rollers are arranged at equal intervals around the rotational driving force transmitting member, a uniform force is applied to the rotational driving force transmitting member from each roller during a shift operation.

Therefore, the shift can be performed smoothly,
An unreasonable force is not applied to the bearing portion of the rotation driving force transmitting member, and the durability is improved.

The invention of claim 6 is the first to fifth aspects of the present invention.
The shift device according to any one of the above, wherein the rotational driving force transmission member is connected via a belt mounted between a fixed flange and a movable flange, a pair of gear ratios change by a change in the flange interval. The movable flange of one of the speed change pulleys of the belt-type continuously variable transmission having the speed change pulley is characterized in that the same effect as in any one of claims 1 to 5 is obtained.

In addition, as described above, the shift device of the present invention which can be used for a high-speed rotation type device is suitable for a shift device of a belt type continuously variable transmission in which a speed change pulley rotates at a high speed. An arbitrary shift characteristic can be obtained in a wide range from low-speed rotation to high-speed rotation.

Accordingly, the belt-type continuously variable transmission using the shift device of the present invention is particularly suitable as a drive device for a driven machine requiring a wide shift range, such as an auxiliary device of a vehicle.

According to a seventh aspect of the present invention, in the shift device according to the sixth aspect, the other speed change pulley has an urging member that presses the movable flange toward the fixed flange to apply tension to the belt. One of the speed change pulleys operates by receiving a centrifugal weight and the centrifugal force thereof, and has a cam that moves the movable flange against the belt tension,
An effect equivalent to that of the configuration of claim 6 is obtained.

In addition to this, even if the engine speed of the vehicle fluctuates, for example, a speed change mechanism having a simple structure composed of a centrifugal weight and a cam, and a constant speed function for keeping the rotation speed on the driven machine side constant is provided. can get.

Also, by using the shift device of the present invention in a belt type continuously variable transmission having such a constant speed function,
In addition to the constant speed function, an arbitrary shift characteristic can be obtained.For example, it is possible to finely control the rotational speed of the driven machine according to the necessity of the driven machine that changes every moment, such as, for example, an accessory of a vehicle. It allows you to take full advantage of the functions of auxiliary equipment,
Engine fuel efficiency can be reduced.

According to an eighth aspect of the present invention, there is provided the shift device according to the seventh aspect, wherein the centrifugal weight and the cam are provided between the engaging portion of the roller and the engaging portion of the movable flange serving as the rotational driving force transmitting member. A gap is provided to avoid interference with the moving operation function due to the above, and the same effect as the configuration of claim 7 is obtained.

In addition, by providing an axial gap between the engaging portion of the movable flange and the engaging portion of the roller, the operation function by the centrifugal weight and the cam and the operation function by the shift device of the present invention are provided. Therefore, the respective operation functions are performed without any trouble, and a predetermined performance is obtained.

[0042]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment will be described with reference to FIGS. This embodiment is described in claims 1, 2, 3,
4, 6, 7, and 8 are provided. Note that the left and right directions are the left and right directions in FIG. 1, and the members and the like without reference numerals are not shown.

FIG. 1 shows a belt-type continuously variable transmission 3 (CVT) using a shift device 1 of this embodiment, an output pulley 5, and a water pump 7 (auxiliary machine). Shift device 1
The belt-type continuously variable transmission 3 is housed inside a casing 9.

The belt type continuously variable transmission 3 is an auxiliary device driving device for transmitting the driving force of the engine to the auxiliary device of the vehicle, and includes a drive pulley 11 (drive-side transmission pulley) and a driven pulley 1.
3 (a driven pulley on the driven side) and a belt 15 for connecting these.

The drive pulley 11 has a fixed flange 19 integral with the hollow shaft 17 and a movable flange 21 arranged on the hollow shaft 17 so as to be movable in the axial direction. V-groove 23 formed between
It is attached to.

The hollow shaft 17 is fixed to an end of the crankshaft 27 by bolts 25 and is prevented from rotating by a half-moon key 29. A sliding bush 33 is disposed between the hollow shaft 17 and the boss 31 of the movable flange 21 to make the movable flange 21 move smoothly.

A hollow clutch member 35 is spline-connected to the outer periphery of the hollow shaft 17. This clutch member 3
A torque cam 37 is formed between the movable flange 5 and the boss 31 of the movable flange 21, and connects the movable flange 21 and the fixed flange 19 in the rotation direction. When a large rotational force is suddenly applied to the drive pulley 11, the torque cam 37 presses the movable flange 21 toward the fixed flange 19 to prevent the belt 15 from slipping.

The clutch member 35 and the movable flange 21
Are disposed between the movable flange 21 and the fixed flange 19, and the belt 15
And the belt 15 is tensioned by the cam action of the V groove 23 so that the pulley pitch diameter R1 is increased.

The movable flange 21 of the drive pulley 11
1 is a position where the distance from the fixing flange 19 is narrowest as in the upper half of FIG.
9 can be moved to the position with the widest interval. The pulley pitch diameter R1 is largest in the upper half state and is smallest in the lower half state.

The driven pulley 13 has a fixed flange 43 integral with the hollow shaft 41 and a movable flange 45 arranged on the hollow shaft 41 so as to be movable in the axial direction. V-groove 47 formed between
It is attached to.

The hollow shaft 41 is fixed to the shaft of the water pump 7 by bolts 49. A sliding bush 53 is arranged between the hollow shaft 41 and the boss portion 51 of the movable flange 45 to make the movement of the movable flange 45 smooth.

A hollow clutch member 55 is spline-connected to the outer periphery of the hollow shaft 41. This clutch member 5
A torque cam 57 is formed between the movable flange 45 and the boss 51 of the movable flange 45, and connects the movable flange 45 and the fixed flange 43 in the rotation direction. When a large rotational force is suddenly applied to the driven pulley 13, the torque cam 57 presses the movable flange 45 toward the fixed flange 43 to prevent the belt 15 from slipping.

The movable flange 45 of the driven pulley 13
Are located at the position where the distance from the fixing flange 43 is narrowest as in the upper half of FIG.
3, the pulley pitch diameter R2 becomes largest in the upper half state and becomes smallest in the lower half state.

A cam member 59 is fixed to the clutch member 55, and a plurality of sets of cam surfaces 61 and 63 (cams) are formed on the cam member 59 and the movable flange 45, respectively. As shown in FIG. 2, these cam surfaces 61 and 63 are arranged at equal intervals in the circumferential direction, and a centrifugal weight 65 is arranged between the cam surfaces 61 and 63. The cam member 59 is provided with a partition wall 67 for holding the centrifugal weight 65 between the cam surfaces 61 and 63.

Each of the centrifugal weights 6 is formed by the partition 67.
5 rotates together with the movable flange 45 and moves radially outward by centrifugal force. Each cam surface 61, 63 receives the inertial force of each centrifugal weight 65.

The output pulley 5 is formed integrally with the fixed flange 43 of the driven pulley 13, and is connected to another auxiliary machine side pulley via a belt.

Thus, the belt type continuously variable transmission 3 is configured.

As described above, the drive pulley 11 and the driven pulley 13 are connected via the belt 15,
When these are rotated by the driving force of the engine, the centrifugal weight 65 of the driven pulley 13 receives the centrifugal force and hits each of the cam surfaces 61 and 63, and the movable flange 45 is pressed toward the fixed flange 43 by the cam thrust force.

When the rotational speed of the driven pulley 13 increases with an increase in the engine rotational speed and the cam thrust force of the cam surfaces 61 and 63 becomes larger than the urging force of the disc spring 39 of the drive pulley 11, the movable flange 45 is fixed. 43
Side, the pulley pitch diameter R2 of the driven pulley 13 is increased by the cam action of the V groove 47, and the pulley pitch diameter R
1 becomes smaller, and the speed increase ratio between the pulleys 11 and 13 decreases.

When the engine speed decreases and the cam thrust force of the cam surfaces 61 and 63 due to the centrifugal weight 65 decreases, the pulley pitch R
1 increases, the pulley pitch diameter R2 decreases, and the speed increase ratio increases.

A graph 69 in FIG. 3 shows the shift characteristics of the belt-type continuously variable transmission 3 due to the cam thrust force of the cam surfaces 61 and 63.

As shown in the graph 69, when the rotational speeds of the drive pulley 11 and the driven pulley 13 exceed the respective shift points 71, the cam thrust forces of the cam surfaces 61 and 63 become larger than the urging force of the disc spring 39, and In the range beyond the point 71, even if the engine speed fluctuates, the speed of the driven pulley 13 (the water pump 7 and the other auxiliary devices) causes the speed
It is kept almost constant.

The drive pulley 11 side rotation speed (D
Point P in r) is the upper limit of the normal engine speed range of the engine.

As described above, the function of keeping the rotation speed of the driven pulley 13 constant in the range beyond the shift point 71 enables
Even when the engine is rotating at high speed, the rotation speed of the accessory is stabilized, and damage to the accessory due to excessive high speed rotation is prevented.

When the number of rotations of the drive pulley 11 is lower than the shift point 71, the number of rotations of the driven pulley 13 is reduced, and the load on the engine in the low-speed rotation range is reduced.

The shift device 1 includes a roller 75, a roller 75
Three circumferential projections 77 (engaging portions) provided on the outer periphery of
Three circumferential grooves 79 (engaging portions) provided on the outer periphery of the movable flange 45 (rotary driving force transmitting member movable in the axial direction) of the driven pulley 13 and engaged with the convex portions 77 of the rollers 75;
Operating rod 81 (operating member), angular contact ball bearing 83 (bearing), sliding bearing 85, screw mechanism 87,
It is composed of a worm gear set 89, a step motor 91 (actuator), a bracket 93 and the like.

The shift device 1 is used in a dry state without being immersed in oil.

As shown in FIG. 1, the bracket 93 is
5, the operation rod 81 is fixed to the casing 9 of the belt-type continuously variable transmission 3, and is supported by a bracket 93 via a slide bearing 85 so as to be movable in the axial direction. Roller 7
5 is supported on the left end of the operating rod 81 via an angular contact ball bearing 83, and is prevented from coming off by a nut 97.

The roller 75 and the movable flange 45 are formed with a convex 77
And the circumferential groove 79 are connected in the axial direction.

An axial gap 99 is provided between the convex portion 77 and the peripheral groove 79.

The worm gear set 89 includes a worm 101 and a worm wheel. As shown in FIG.
01 is formed on the output shaft 103 of the step motor 91.

The rotation of the step motor 91 is controlled by the worm 10
1. Rotate the worm wheel through 1.

The screw mechanism 87 is composed of a screw formed on the inner periphery of the worm wheel and a screw 105 formed on the outer periphery of the operating rod 81, and converts the rotation of the worm wheel into a thrust force. The operation rod 81 (roller 75) is moved.

When the roller 75 moves, the movable flange 45 moves due to the engagement between the convex portion 77 and the circumferential groove 79, and the speed of the belt-type continuously variable transmission 3 is shifted as described above.

When the direction of rotation of the step motor 91 is switched, the direction of movement of the movable flange 45 (the roller 75) changes. By changing the angle of rotation of the step motor 91, the amount of movement of the movable flange 45 can be adjusted. Step motor 91
By such control, the gear ratio of the belt-type continuously variable transmission 3 can be arbitrarily selected.

In this shift operation, the movable flange 45 moves while rotating, and the rotation of the movable flange 45 is absorbed by the rotation of the roller 75, seizure and galling are prevented, and the durability is improved. Further, an angular contact ball bearing 83 is provided between the roller 75 and the operating rod 81.
Is disposed, the effect of preventing seizure and galling and the durability are greatly improved.

Therefore, since the shift device 1 does not require lubrication to prevent seizure and galling, the shift device 1 can be used in a dry state without being immersed in oil as described above.

Before the rotation speeds of the drive pulley 11 and the driven pulley 13 rise to the shift point 71 with the increase in the engine rotation speed (before the shift function of the centrifugal weight 65 and the cam surfaces 61 and 63 is activated), the shift is performed. If the movable flange 45 is moved to the right by the device 1, the pulley pitch diameter R2 becomes large and the pulley pitch diameter R1 becomes small, so that the speed increase ratio can be reduced.

The graph 107 in FIG. 3 is an example of such a shift characteristic.

A graph 109 shows the shift characteristics when the movable flange 45 is held at the upper half position (the position where the speed increase ratio is the minimum) in FIG. 1 by the shift device 1 from the start of the engine. Conversely, if the movable device 45 is held at the lower half position (the position where the speed increase ratio is maximum) in FIG.
Thus, the same shift characteristics as those of the shift characteristic graph 69 by the cam surfaces 61 and 63 can be obtained.

Accordingly, the hatched portion surrounded by the graphs 69 and 109 is a control range in which the shift device 1 can change the speed, and the shift device 1 can arbitrarily control the rotation speed of each accessory within this range. it can.

For example, if the shift control is performed to the lower speed side as shown in graphs 107 and 109, each auxiliary machine can be put into a halt state when the function of each auxiliary machine is unnecessary, and the durability of the auxiliary machines can be improved. Alternatively, it is possible to reduce the consumption of the engine driving force by the auxiliary equipment and to improve the fuel efficiency.

As described above, the axial gap 99 is provided between the convex portion 77 of the roller 75 and the peripheral groove 79 of the movable flange 45.
Is provided, the movement of the movable flange 45 by the shift device 1, the centrifugal weight 65 and the cam surfaces 61, 63
And the movement of the movable flange 45 does not affect each other.

Therefore, these two shift functions are prevented from interfering with each other and function normally.

Thus, the shift device 1 is configured.

As described above, in the shift device 1, since the roller 75 is rotated when the movable flange 45 is shifted, seizure and galling are prevented, and the durability is greatly improved.

Further, by disposing the angular contact ball bearing 83 between the roller 75 and the operating rod 81, the sliding resistance is further reduced, and the effect of preventing seizure and galling and the durability are improved.

The roller 75 engaged with the movable flange 45 by the outer convex portion 77 has a small diameter. Therefore, the angular contact ball bearing 83 has a small diameter and a small sliding speed (peripheral speed). The effect of preventing galling and improving the durability is high.

Further, it is advantageous that a small-diameter and low-cost angular contact ball bearing 83 can be used.

The shift device 1 having a high effect of preventing image sticking and galling and a high effect of improving durability is suitable not only for low-speed rotating devices but also for high-speed rotating devices.

Further, since the shift device 1 does not need to be immersed in oil and can be used in a dry state, there is no loss of driving force due to oil resistance.

Further, unlike the prior art shown in FIG. 8, the shift device 1 does not use a geared motor or a large-diameter expensive bearing, so that the cost is greatly reduced, and the structure is simple, high in reliability and small in size. It is.

Also, since three projections 77 of the roller 75 and three circumferential grooves 79 of the movable flange 45 are provided, and three sets (a plurality of sets) of these engagement portions are provided, the shift operation of the movable flange 45 is performed. Since the contact area of the engaging portion is increased and the surface pressure is dispersed and reduced, the effect of preventing seizure and galling and the durability are improved accordingly.

Further, one roller 75 is placed on the operation rod 81.
Are simple and compact, and the shift device 1 is accordingly small in size and low in cost.

In addition, the belt-type continuously variable transmission 3 used in the accessory drive device of the vehicle, in which the speed change pulleys 11 and 13 rotate at high speed and require a wide speed change range, is provided.
The shift device 1 that can be used for a high-speed rotation type device is preferable, and by using the shift device 1, as described above, an arbitrary shift characteristic can be obtained in a wide range from low-speed rotation to high-speed rotation. Can be

The centrifugal weight 65 and the cam surfaces 61, 63
By using the shift device 1 in the belt-type continuously variable transmission 3 having a constant speed function for keeping the rotation speed of the auxiliary machine constant even when the engine speed fluctuates, in addition to this constant speed function, Speed characteristics and the ability to finely control the rotational speed of the auxiliary equipment according to the ever-changing need of the auxiliary equipment, so that the functions of the auxiliary equipment can be used to the highest degree and the engine fuel consumption can be reduced. be able to.

Further, by providing an axial gap 99 between the convex portion 77 of the roller 75 and the peripheral groove 79 of the movable flange 45, the operation function of the centrifugal weight 65 and the cam surfaces 61 and 63 and the shift device 1 , Interference with the operation functions is prevented, the movement operation by both operation functions is performed without any trouble, and the respective predetermined performances are obtained.

Next, a second embodiment will be described with reference to FIG. This embodiment has the features of claims 1, 2, and 4. In addition, members and the like without reference numerals are not shown.

FIG. 4 shows a shift device 111 according to the second embodiment. This shift device 111 is used in a driving force transmission system of a vehicle.

The shift device 111 includes a roller 113, a circumferential protrusion 115 (engaging portion) provided on the outer periphery of the roller 113, a drive gear 117 (a rotational driving force transmitting member movable in the axial direction), and a drive gear 117. Sleeve 118
, An operating rod 121 (operating member), a sliding bush 123, an actuator that moves the operating rod 121 bidirectionally as indicated by an arrow 125, and the like. It is composed of

The drive gear 117 is movably spline-connected on the drive shaft 127, and can be disengaged from the driven gear 129 coaxially arranged by moving.

The roller 113 is rotatably supported on the right end of the operating rod 121 via a sliding bush 123.

The roller 113 and the drive gear 117 are connected in the axial direction by the engagement of the projection 115 and the circumferential groove 119.

The actuator moves the roller 113 via the operation rod 121.

When the roller 113 moves, the drive gear 117 moves due to the engagement between the projection 115 and the peripheral groove 119, and the drive gear 117 is disengaged from the driven gear 129.

In this shift operation, the drive gear 117 moves while rotating, the rotation of the drive gear 117 is absorbed by the rotation of the roller 113, and the sliding bush 12 is moved between the roller 113 and the operating rod 121.
Since 3 is arranged, seizure and galling are prevented, and the durability is improved.

Therefore, since the shift device 111 does not require lubrication to prevent seizure and galling, the shift device 111 is used in a dry state without being immersed in oil.

Thus, the shift device 111 is configured.

As described above, in the shift device 111, when the shift operation of the drive gear 117 is performed, the rollers 113
The rotation of the shaft prevents seizure and galling, and greatly improves durability.

Further, by using the sliding bush 123, the sliding resistance between the roller 113 and the operating rod 121 is reduced, and the effect of preventing seizure and galling and the durability are further improved.

Also, the drive gear 11 is formed by the convex portion 115 on the outer periphery.
The roller 113 engaged with the roller 7 has a small diameter. Therefore, the sliding bush 123 has a small diameter and a small sliding speed (peripheral speed), and accordingly, the effect of preventing seizure and galling and the effect of improving the durability are high.

Further, a small-diameter, low-cost sliding bush 123 is provided.
Can be advantageously used.

The shift device 111 having a high effect of preventing image sticking and galling and a high effect of improving durability is suitable for not only low-speed rotating devices but also high-speed rotating devices.

The shift device 111 does not need to be immersed in oil to prevent seizure and galling, and can be used in a dry state, so that there is no loss of driving force due to oil resistance.

Further, unlike the prior art shown in FIG. 8, the shift device 111 does not use a geared motor or a large-diameter expensive bearing, so that the cost is greatly reduced, and the structure is simple, high in reliability and small in size. It is.

Further, one roller 1 is placed on the operation rod 121.
The structure in which 13 is coaxially arranged is simple and compact,
The shift device 111 becomes smaller and lower in cost.

Next, a third embodiment will be described with reference to FIGS. This embodiment has the features of claims 1, 2, 4, and 5. In addition, members and the like without reference numerals are not shown.

In the description of the third embodiment and FIGS. 5 and 6, the same reference numerals are given to members having the same functions as those of the second embodiment, and redundant description of these same members is omitted.

FIGS. 5 and 6 show a shift device 1 according to a third embodiment.
The shift device 131 is used in a driving force transmission system of a vehicle, similarly to the shift device 111 of the second embodiment.

The shift device 131 includes two rollers 11
3. Circumferential projection 11 provided on the outer periphery of roller 113
5, the drive gear 117 is provided on the outer periphery of the sleeve 118 of the drive gear 117,
The operation member 133 includes an actuator for moving the operation member 133 in the axial direction, and the like.

The operating member 133 includes an operating rod 135 (shaft-shaped member) and an arm member 139 fixed to the operating rod 135 and having two distal ends 137 protruding around the drive gear 117.

Each roller 113 has a sliding bush 123 on a shaft 141 fixed to each end 137 of the arm member 139.
And are arranged at equal intervals around the drive gear 117 as shown in FIG.

Each of the rollers 113 and the drive gear 117 are connected in the axial direction by the engagement of the projection 115 and the circumferential groove 119.

The actuator moves each roller 113 via the operation member 133.

When each roller 113 moves, the convex 115
The drive gear 117 is moved by the engagement between the drive gear 117 and the peripheral groove 119, and the drive gear 117 is disengaged from the driven gear 129.

In this shift operation, the rotation of the drive gear 117 is absorbed by the rotation of each roller 113, and the sliding bush 123 is disposed between each roller 113 and the shaft 141. Is prevented and durability is improved.

Therefore, the shift device 131 is used in a dry state.

Thus, the shift device 131 is configured.

The shift device 131 has the same effect as the shift device 111.

In addition to this, as described above,
3 (two or more), each roller 113
Is reduced, and the effect of preventing seizure and galling and the durability are greatly improved.

The two rollers 113 are connected to the drive gear 1
Since the rollers are arranged at equal intervals around the drive gear 17, an even force is applied to the drive gear 117 from each roller 113 during the shift operation.

Therefore, the shift is performed smoothly, and
Unreasonable force is not applied to the support portion of the drive gear 117, and the durability is improved.

The use of the shift device of the present invention is not limited to the belt-type continuously variable transmission and the driving force transmission system as in each embodiment. The shift device of the present invention suitable for a high-speed rotation type device can be used for a wide range of devices from a low-speed rotation type to a high-speed rotation type.

[0134]

According to the first aspect of the present invention, since the rotation of the rotational driving force transmitting member during the shift operation is absorbed by the rotation of the roller, seizure and galling are prevented, and the durability is greatly improved.

Further, the roller engaged with the rotary driving force transmitting member at the outer peripheral engaging portion has a small diameter, and the sliding speed (peripheral speed) between the roller and the operating member is small. High effect of prevention and improvement of durability.

Therefore, this shift device is particularly suitable for a high-speed rotation type device.

Since the shift device does not need to be immersed in oil, there is no loss of driving force due to oil resistance.

Further, unlike the conventional example, since a geared motor and a large-diameter expensive bearing are not used, the cost is greatly reduced, and the structure is simple, high in reliability and small in size.

According to the second aspect of the invention, the same effect as that of the first aspect is obtained, and the sliding resistance between the roller and the operation member is reduced by disposing the bearing between the roller and the operation member. The effect of preventing image sticking and galling and the durability are further improved.

Further, since the bearing for supporting the small-diameter roller has a small diameter and a low peripheral speed, the effect of preventing seizure and galling and the durability are greatly improved, and a small-diameter and low-cost bearing can be advantageously used. .

The invention of claim 3 is the invention of claim 1 or claim 2.
The same effect as the configuration described above is obtained, and by providing a plurality of sets of engagement portions between the rotational driving force transmission member and the roller, the contact area at the engagement portions is widened during the shift operation, and the surface pressure is dispersed. Since this is reduced, the effect of preventing seizure and galling and the durability are greatly improved.

The invention of claim 4 is the invention of claims 1 to 3
And the structure in which one roller is coaxially arranged on the shaft-shaped operation member is simple and compact, so that the shift device becomes smaller and lower in cost.

The invention of claim 5 is the invention of claims 1 to 3
In addition to obtaining the same effect as any one of the above, the load on each roller is reduced by using a plurality of rollers, and the effect of preventing image sticking and galling and the durability are greatly improved.

Further, by disposing a plurality of rollers at equal intervals around the rotational driving force transmitting member, a uniform force is applied from each roller to the rotational driving force transmitting member during the shift operation, so that the shift can be performed smoothly. At the same time, an unreasonable force is not applied to the bearing of the rotary driving force transmitting member, and the durability is improved.

The invention of claim 6 is the invention of claims 1 to 5
The shift device of the present invention, which has the same effect as any one of the above, and can be used for a high-speed rotation type device, is suitable for a shift device of a belt-type continuously variable transmission in which a speed change pulley rotates at a high speed, Arbitrary shifting characteristics can be obtained in a wide range up to high-speed rotation.

Therefore, the belt-type continuously variable transmission using the shift device of the present invention is suitable as a drive device for a driven machine requiring a wide shift range, such as an auxiliary device of a vehicle.

According to the seventh aspect of the present invention, the same effect as the configuration of the sixth aspect is obtained, and even if the engine speed fluctuates, the rotation of the driven machine side can be achieved by a simple transmission mechanism including a centrifugal weight and a cam. A constant speed function that keeps the speed constant is obtained.

By using the shift device of the present invention in a belt type continuously variable transmission having such a constant speed function,
In addition to the constant speed function, an arbitrary shift characteristic can be obtained, so that the rotational speed of the driven machine can be finely controlled according to the constantly changing need of the driven machine, and the function of the driven machine can be improved. It can be used to the highest degree and engine fuel efficiency can be reduced.

According to the eighth aspect of the present invention, the same effect as that of the seventh aspect is obtained, and an axial gap is provided between the engaging portion of the movable flange and the engaging portion of the roller. Since the interference between the operation function by the weight and the cam and the operation function by the shift device of the present invention is prevented, the respective operation functions are performed without any trouble, and a predetermined performance is obtained.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a graph showing shift characteristics of a belt-type continuously variable transmission using the first embodiment.

FIG. 4 is a sectional view showing a second embodiment of the present invention.

FIG. 5 is a sectional view showing a third embodiment of the present invention.

FIG. 6 is a sectional view taken along line BB of FIG. 5;

FIG. 7 is a sectional view showing a first conventional example.

FIG. 8 is a sectional view showing a second conventional example.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1, 111, 131 Shift mechanism 3 Belt-type continuously variable transmission 11 Drive pulley (driving-side transmission pulley) 13 Driven pulley (driven-side transmission pulley) 15 Belt 19, 43 Fixed flange 21 Movable flange 39 Disc spring (biasing member) ) 45 Movable flange (rotary driving force transmitting member movable in the axial direction) 61, 63 Cam surface (cam) 65 Centrifugal weight 75 Roller 77 Three circumferential projections (engagement portions) provided on the outer circumference of roller 75 ) 79 Three circumferential grooves (engaging portion) provided on the outer periphery of the movable flange 45 81 Operating rod (operating member) 83 Angular contact ball bearing (bearing) 91 Step motor (actuator) 99 Roller 75 and movable flange 45 A gap 113 for preventing interference 113 Roller 115 A circumferential projection (engaging portion) provided on the outer periphery of the roller 113 7 Drive Gear (Rotary Driving Force Transmission Member That Can Move in Axial Direction) 119 Circumferential Groove (Engagement) Provided on Outer Periphery of Drive Gear 117 121 Operating Rod (Operating Member) 123 Sliding Bush (Bearing) 133 Operating Member 135 Operation rod (shaft member) 139 Arm member

Claims (8)

[Claims] 1. A rotational driving force transmitting member which is movable in an axial direction, a circumferential engaging portion provided on the rotational driving force transmitting member, and an engaging portion provided on an outer periphery of the rotational driving force transmitting member. , An operating member that rotatably supports the roller and is movable in the axial direction of the rotational driving force transmitting member, and transmits a rotational driving force through the operating member and the roller. A shift device comprising: an actuator for moving a member. 2. The shift device according to claim 1, wherein a bearing is disposed between the roller and the operation member. 3. The invention according to claim 1, wherein the engaging portion of the rotary driving force transmitting member and the engaging portion of the roller are:
A shift device comprising a plurality of sets of circumferential protrusions and circumferential grooves that mesh with each other. 4. The invention according to claim 1, wherein the operation member is shaft-shaped, and one roller is coaxially arranged on the shaft-shaped member. Shift device. 5. The invention according to claim 1, wherein the operating member includes a shaft-shaped member, and a plurality of operating members fixed around the shaft-shaped member, around the rotation driving force transmitting member. A shift device comprising: an arm member protruding from a tip of the arm member; and a roller rotatably supported at each tip of the arm member. 6. The invention according to claim 1, wherein the rotational driving force transmitting member is connected via a belt mounted between the fixed flange and the movable flange, A shift device characterized in that the shift device is a movable flange of one of the speed change pulleys of a belt-type continuously variable transmission having a pair of speed change pulleys whose speed ratio changes according to a change in a flange interval. 7. The invention according to claim 6, wherein the other speed-change pulley has an urging member that presses the movable flange toward the fixed flange to apply tension to the belt, and the one speed-change pulley includes: A shift device comprising a centrifugal weight and a cam that operates by receiving the centrifugal force and moves a movable flange against the belt tension. 8. The moving operation function by a centrifugal weight and a cam between an engaging portion of a roller and an engaging portion of a movable flange which is a rotational driving force transmitting member. A shift device having a gap for avoiding interference.