JP2001355694A - Belt type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve a problem that uneven wear of a belt easily occurs and alignment accuracy is difficult to be improved when adjusting the axial deviation of the belt between pulleys in a conventional belt type continuously variable transmission. SOLUTION: Uneven wear of the belt is prevented and improvement of alignment accuracy is realized by providing the belt type continuously variable transmission provided with input side and output side pulleys P1 and P2 constituted of fixed flanges 1 and 2 immobile in an axis direction and movable flanges 3 and 4 reciprocative in the axial direction on input side and output side rotary shafts S1 and S2 arranged in parallel and connecting both of the pulleys P1 and P2 by a belt B equipped with an axial deviation adjusting means for reciprocatively holding at least one rotary shaft S2 in the axial direction and reciprocating the rotary shaft 2 in the axial direction in a range corresponding to axial deviation amount of the belt B for the rotary shaft S2.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a belt-type continuously variable transmission used for, for example, a power transmission of an automobile.

[0002]

2. Description of the Related Art In general, a belt-type continuously variable transmission includes a stationary flange which is immovable in an axial direction and a movable flange which can reciprocate in an axial direction, on input and output rotating shafts arranged in parallel. Input and output pulleys,
Both pulleys are connected by a power transmission belt. At this time, in each pulley, opposing sliding surfaces of both flanges are tapered, and a V-shaped groove for accommodating the belt is formed between both flanges. Then, the belt-type continuously variable transmission transmits the rotation of the input-side rotary shaft to the output-side rotary shaft via both the pulleys and the belt. At this time, each of the pulleys is changed so that the groove width of the both pulleys changes in inverse proportion. By reciprocating the movable flange, the belt wrap position between the input side and the output side is slid in the radial direction of the pulley,
The gear ratio is changed steplessly.

Further, in the belt type continuously variable transmission as described above, when the belt is located on the outer peripheral side of one pulley, the belt is located on the center side of the other pulley. In this case, since the belt slides on the basis of the tapered sliding surface of the fixed flange at this time, the arrangement of the fixed flange and the movable flange of both pulleys is reversed, and for each fixed flange, The belt is slid in the same direction to prevent large belt misalignment between both pulleys.

However, in the belt type continuously variable transmission as described above, when the belt slides on each pulley,
The belt also moves in the axial direction of the rotating shaft by an amount corresponding to the inclination of the sliding surface of the fixed flange, and such an operation is performed by reciprocal movement of each movable flange. Due to a change in the contact area with the belt, the center of the belt is shifted between the two pulleys.

Conventionally, in order to cope with such belt misalignment, the entire pulley is provided so as to be movable in the axial direction of the rotating shaft with respect to at least one of the rotating shafts. The pulley is moved in a direction to cancel the misalignment by using the restoring force of the belt, and the misalignment is eliminated by moving the entire pulley by hydraulic pressure. Such a belt-type continuously variable transmission is described in, for example, JP-A-56-80551.

[0006]

However, in the conventional belt type continuously variable transmission as described above, when the pulley is moved by using the restoring force of the belt, the misalignment is eliminated. Until the belt is unevenly loaded until it is, in other words, because it uses the uneven load,
There is a problem that uneven wear occurs on the belt and durability decreases.In addition, when the pulley is moved hydraulically with respect to the rotating shaft, position control is very difficult, so it is necessary to improve alignment accuracy. There is a problem that it is difficult, and solving these problems has been a problem.

[0007]

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned conventional problems, and has a belt-type continuously variable transmission in which variable-width pulleys provided on input and output rotary shafts are connected by a belt. A belt-type continuously variable transmission capable of accurately correcting a belt misalignment between both pulleys during a gear shift, preventing uneven wear of the belt and maintaining durability. It is an object.

[0008]

A belt-type continuously variable transmission according to the present invention is characterized in that a fixed flange and an axial line that are immovable in an axial direction on input and output rotating shafts arranged in parallel. A belt-type continuously variable transmission in which both pulleys are connected by a belt, and at least one of the rotating shafts is reciprocally movable in the axial direction. 3. A structure comprising a misalignment adjusting means for holding the rotating shaft and reciprocating the rotating shaft in the axial direction within a range corresponding to the amount of misalignment of the belt between the pulleys with respect to the rotating shaft. A cam surface perpendicular to the axis at one end of the rotating shaft, a cam plate positioned on the case side holding the rotating shaft and rotatable about the rotating shaft, and a cam surface. A ball interposed between the rotating shaft and the clutch plate, a clutch mechanism for controlling the rotation of the cam plate, and an elastic body for urging the rotating shaft toward one end at the other end of the rotating shaft. An inclined surface having a height difference corresponding to the amount of misalignment of the belt generated between the two pulleys is formed in one of the opposing surfaces of the plates in the circumferential direction. A plurality of driven clutches fixed to the case side and forming a multi-plate clutch together with the drive clutch of the cam plate; and a multi-plate clutch. Wherein the armature is disposed opposite to the solenoid with the armature therebetween.
As a configuration, the current applied to the solenoid is changed in accordance with the gear ratio, and the above configuration is a means for solving the conventional problem.

[0009]

In the belt-type continuously variable transmission according to the first aspect of the present invention, the rotation of the input-side rotary shaft is transmitted to the output-side rotary shaft via each pulley and belt. At this time, in each pulley, the arrangement of the fixed flange and the movable flange on the input side and the output side are reversed with each other, as in the prior art, and the opposing sliding surfaces of both flanges are tapered. A V-shaped groove for accommodating the belt is formed between the two flanges. Therefore, if the respective movable flanges are reciprocated so that the groove widths of both pulleys change in inverse proportion during rotation transmission, the belt wrapping positions of the pulleys on the input side and the output side are changed. Sliding in the radial direction causes the gear ratio to change steplessly.

Here, in this type of belt type continuously variable transmission, when the belt slides on each pulley,
The belt also moves in the axial direction of the rotary shaft by an amount corresponding to the inclination of the sliding surface of the fixed flange. For example, when shifting from the LOW side to the HIGH side is performed, that is, the movable flange of the input pulley is fixed to the fixed flange. To move the belt from the center of the input pulley to the outer periphery, and the movable flange of the output pulley to retract from the fixed flange to slide the belt from the outer periphery of the output pulley to the center. At this time, a belt misalignment (about 0.8 mm at maximum) occurs between both pulleys. The amount of misalignment of the belt is zero before the start of the slide, increases with the start of the slide, reaches a maximum at almost the intermediate position, and thereafter decreases and becomes zero at the end of the slide.

With respect to such belt misalignment, the belt-type continuously variable transmission holds at least one of the rotating shafts so as to be able to reciprocate in the axial direction, and the belt misalignment with respect to the rotating shaft. Since there is provided a misalignment adjusting means for reciprocating the same rotating shaft in the axial direction within a range corresponding to the amount, the function of the misalignment adjusting means is performed while the movable flange of the pulley is moved in one direction to slide the belt. As a result, the entire pulley together with the rotating shaft is moved in the axial direction by the amount of the belt misalignment, thereby eliminating the misalignment of the belt between the two pulleys. At this time, since the amount of misalignment of the belt increases or decreases during the period from the start of the slide to the end of the slide as described above, the misalignment adjusting means moves the entire pulley together with the rotating shaft to the maximum while the movable flange moves in one direction. Reciprocate within the range corresponding to the amount of misalignment.

In the belt type continuously variable transmission according to a second aspect of the present invention, in the misalignment adjusting means, at one end of the rotating shaft, a cam surface provided on the rotating shaft and a cam plate positioned on the case side are disposed. A ball is interposed therebetween, and at the other end of the rotating shaft, the rotating shaft is urged toward the one end by an elastic body. In the initial state, the ball is engaged with the lower part of the inclined surface provided on one of the opposed surfaces of the cam surface and the cam plate, and this engaged state is maintained by the urging force of the elastic body. When the rotating shaft rotates in this state, the cam plate also rotates via the ball.

At the time of driving the movable flange, that is, at the time of gear shifting in which the center of the belt is shifted between both pulleys, the cam plate rotating together with the rotating shaft is controlled by the clutch mechanism. In this case, the clutch mechanism can temporarily stop the rotation of the cam plate, but mainly reduces the rotation of the cam plate by frictional force. Then, since the cam plate is positioned on the case side and does not move in the axial direction of the rotating shaft, frictional force is applied to the ball due to the speed difference between the rotating cam surface and the decelerated cam plate, and the ball tilts. It rolls on the upper part of the surface, and the rotating shaft pushed by the ball moves toward the other end against the elastic body. At this time, since the inclined surface has a height difference corresponding to the amount of misalignment of the belt generated between the two pulleys, the entire pulley moves along with the rotating shaft by an amount corresponding to the amount of misalignment. Misalignment caused by the above is eliminated. Furthermore, if the clutch mechanism is released, the cam plate tries to rotate with the rotating shaft via the ball, and since the urging force of the elastic body is always acting,
As the rotation speed of the cam plate increases, the ball rolls to the lower part of the inclined surface, and the whole pulley moves toward one end together with the rotation shaft to return to the original position.

In a belt type continuously variable transmission according to a third aspect of the present invention, in the clutch mechanism, a multi-plate clutch comprising a drive clutch of a cam plate and a driven clutch fixed to a case side between a solenoid and an armature. Is provided. Therefore, when a current is applied to the solenoid to generate a magnetic field while the cam plate is rotating together with the rotating shaft and the armature is attracted to the solenoid side, the drive clutch and the driven clutch come into contact with each other by the pressing of the moved armature. The rotation of the cam plate is controlled by the frictional force.

At this time, in the clutch mechanism, when the current applied to the solenoid is increased, the attraction force of the armature is increased, and the friction force of the multi-plate clutch is also increased. The amount of climbing of the ball on the surface, that is, the amount of movement of the rotary shaft and the entire pulley in the axial direction increases. The opposite is true if the current applied to the solenoid is reduced. If the current applied to the solenoid is kept constant, the attraction force of the armature and the friction force of the multi-plate clutch become constant, the ball is kept at a fixed position on the inclined surface, and the moving amount of the rotating shaft is also kept constant. You.

In the belt-type continuously variable transmission according to a fourth aspect of the present invention, in the clutch mechanism according to the third aspect, when the current applied to the solenoid is changed, as a result, the rotational axis and the entire pulley in the axial direction are changed. The amount of movement changes and the amount of belt misalignment that occurs between both pulleys is
As described above, since the speed increases or decreases at a constant rate during gear shifting, by changing the current applied to the solenoid according to the gear ratio, the positions of the rotary shaft and the entire pulley are changed correspondingly, In any step of the stepless speed change, the belt misalignment is eliminated.

[0017]

According to the belt-type continuously variable transmission according to the first aspect of the present invention, a belt-type continuously variable transmission in which variable-width pulleys provided on the input-side and output-side rotary shafts are connected by a belt. In the above, since at least one of the rotating shafts is held so as to be movable in the axial direction and there is provided a misalignment adjusting means for reciprocating the rotating shaft in the axial direction, the misalignment of the belt generated between the two pulleys at the time of shifting is reduced. Can be fixed reliably,
In particular, compared to the conventional device that uses the restoring force of a belt deformed due to misalignment, the pulley is moved together with the rotating shaft to correct the misalignment of the belt, thereby preventing uneven wear and noise of the belt. It is possible to maintain the durability of the belt satisfactorily, and it is possible to greatly increase the alignment accuracy as compared with the conventional device that moves the pulley with respect to the rotating shaft by hydraulic pressure. Uneven wear of the belt and the like can be more reliably prevented, and the performance of the continuously variable transmission can be further enhanced.

According to the belt-type continuously variable transmission according to the second aspect of the present invention, the same effect as that of the first aspect can be obtained, and the cam surface of the rotating shaft and the ball are provided between the cam surface. An interposed cam plate, a clutch mechanism for controlling the rotation of the cam plate,
And the use of the misalignment adjusting means provided with an elastic body for urging the rotating shaft in one direction makes the structure of the misalignment adjusting means very simple and small, and has a stepless structure having a complicated internal structure. While being easy to incorporate into the transmission,
Although it has a very simple structure, it is possible to extremely accurately correct the belt misalignment occurring between the two pulleys.

According to the belt-type continuously variable transmission of the third aspect of the present invention, the same effect as that of the second aspect can be obtained, and a clutch mechanism having a solenoid, an armature and a multi-plate clutch is employed. Therefore, centering of the belt can be performed by operation of the clutch mechanism, that is, electronic control, and further simplification of the structure, cost reduction, and further improvement of centering accuracy can be realized.

According to the belt type continuously variable transmission according to the fourth aspect of the present invention, the same effect as in the third aspect can be obtained, and the current applied to the solenoid is changed according to the speed ratio. Accordingly, in any process of the gear shifting performed steplessly, highly accurate belt alignment can be smoothly performed with extremely simple control.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a belt-type continuously variable transmission according to the present invention will be described below with reference to the drawings.

The belt-type continuously variable transmission shown in FIG. 1 has an input-side rotary shaft S1 connected to the engine side of an automobile and an output-side rotary shaft S2 connected to the axle side, which are vertically parallel to each other. S1 and S2 are provided with input-side and output-side pulleys P1 and P2 each comprising fixed flanges 1 and 2 which are immovable in the axial direction by integral molding and movable flanges 3 and 4 which can reciprocate in the axial direction. , Both pulleys P1, P2
Are connected by a power transmission belt B.

Each of the pulleys P1, P2 has a fixed flange 1,
2 and sliding surfaces 1a to 4a of movable flanges 3 and 4 facing each other
Are formed in a tapered shape, and V-grooves 5 and 6 are formed between the two flanges, the intervals of which gradually increase toward the outer peripheral side. The pulleys P1 and P2 have the fixed flanges 1 and 2 and the movable flanges 3 and 4 arranged in opposite directions.

The input-side rotary shaft S1 is rotatably held at both ends by bearings 8 and 9 in a case 7 of the transmission. The movable flange 3 of the input-side pulley P1 is movable in the axial direction by being mounted on the input-side rotary shaft S1 via a plurality of ball keys 10, and is rotatable integrally with the input-side rotary shaft S1. is there.

The movable flange 3 of the input pulley P1
In the figure, a cylinder portion 11 is integrally formed concentrically on the outer peripheral end on the back side. On the other hand, a piston 12 is fixed to the input side rotation shaft S1 by a ring 13. The outer peripheral end of the piston 12 is in airtight and slidable contact with the inner peripheral surface of the cylinder portion 11, and forms a pressure chamber 14 with the movable flange 2. Further, the input side rotation axis S
In FIG. 1, a flow path 15 communicating from the right end in FIG. 1 to the pressure chamber 14 is formed, and a supply means for hydraulic oil (not shown) is connected to the flow path 15. That is, the movable flange 3
Moves from the retreat position shown above the input-side rotary shaft S1 in FIG. 1 to the forward position shown below also by pressurizing and supplying the hydraulic oil to the pressure chamber 14 via the flow path 15.

The output side rotary shaft S2 is rotatably held at one end on the left side in FIG. 1 via a rotor 16 in a case 7 of the transmission, and a thrust bearing is mounted on a cap 7A fixed to the case 7. The other end is rotatably held via a disc spring 18 which is an elastic body and constitutes a misalignment adjusting means described later. At this time, the output side rotation shaft S
2 is spline-coupled (S) to the rotor 16 and can reciprocate in the axial direction within the length range of the spline, and is always in one end direction (left direction in FIG. ).

The output side pulley P2 has the movable flange 4 mounted on the output side rotary shaft S2 via a plurality of ball keys 19, and has a cylinder portion 20 on the back side of the movable flange 4 like the input side. In addition, the piston 22 fixed to the output-side rotation shaft S2 using the ring 21 and the movable flange 4
A pressure chamber 23 is formed between the output shaft and the movable flange 4 by pressurizing and supplying hydraulic oil to the pressure chamber 23 through a flow path 24 formed in the output side rotation shaft S2. Is moved from the retreat position shown on the upper side to the forward position also shown on the lower side.

The movable flanges 3 and 4 of each of the pulleys P1 and P2 move the output side (or the input side) backward when the input side (or the output side) is advanced by pressurized supply of hydraulic oil. Therefore, when the pressure chamber 23 is opened on the output side, the movable flange moves backward while the belt B slides toward the center of the pulley on the output side due to the pulling force of the belt B sliding on the input side toward the outer periphery of the pulley. However, as shown particularly in the output pulley P2 in FIG. 1, a cover 25 is provided at the tip of the cylinder section 20 to form pressure chambers 23 and 26 before and after the piston 22, and hydraulic oil is applied to the rear pressure chamber 26. The movable flange 3 may be retracted by supplying pressure. This configuration can naturally be provided on the input side.

In the belt type continuously variable transmission according to this embodiment, as described above, the output side rotation shaft S2 is held by the rotor 16 and the disc spring 18 so as to be able to reciprocate in the axial direction. The output rotary shaft S2 reciprocates in the axial direction with respect to the output rotary shaft S2 within a range corresponding to the amount of misalignment of the belt B generated between the pulleys P1 and P2 with the reciprocation of the movable flange 4 with respect to the output rotary shaft S2. It is provided with a misalignment adjusting means for causing the misalignment.

The misalignment adjusting means holds, in addition to the disc spring 18, a cam surface 27 orthogonal to the axis at one end of the output side rotating shaft S2 and the output side rotating shaft S2, as shown in FIG. Positioned on the case 7 side and the output side rotation axis S
A cam plate 28 which is rotatable about the center 2 and a cam surface 2
A ball 29 interposed between the cam plate 7 and the cam plate 28 and a clutch mechanism 30 for controlling the rotation of the cam plate 28 are provided.

In this embodiment, a step 31 is formed integrally with the output-side rotating shaft S2 at the rear-side base end of the fixed flange 2 in the circumferential direction, and a step surface orthogonal to the axis is formed on the cam surface 27 at the step 31. And As shown in FIG. 3, the cam plate 28 has an insertion hole 28 for the output side rotation shaft S2 at the center.
A is formed in an annular shape having an A. On a surface opposed to the cam surface 27, an inclined surface 28B having a height difference H corresponding to the amount of misalignment of the belt B generated between the pulleys P1 and P2 is provided in a circumferential direction. It is formed in.

The cam plate 28 has twelve inclined surfaces 28B whose inclination directions are alternately changed so that six irregularities (28L, 28H) are alternately formed in the circumferential direction.
Here, when the amount of misalignment of the belt B is about 0.8 mm, the height difference H of the inclined surface 28B is about 1.5 mm. The cam plate 28 has a bearing 38 in which needles are arranged in a ring shape interposed between the cam plate 28 and the rotor 16.
A plurality of balls 29 are interposed between the cam surface 27. In this embodiment, twelve inclined surfaces 28B of the cam plate 28 are used.
, Six balls 29 are interposed. The cam plate 28 does not move in the axial direction of the output side rotation shaft S2, and in the initial state, the lower portion (recess) of the six portions of the inclined surface 28
The ball 29 is engaged with the ball 28L, and the engaged state is maintained by the urging force of the disc spring 18.
9, and rotates with the output side rotation shaft S2.

The clutch mechanism 30 includes an annular solenoid 32 fixed to the case 7 about the output side rotation shaft S2.
A plurality of drive clutches 33 provided on the outer peripheral portion of the cam plate 28; and a plurality of driven clutches 36 fixed to the case 7 via the holder 34 and forming a multi-plate clutch 35 together with the drive clutch 33 of the cam plate 28. And an armature 37 disposed opposite the solenoid 32 with the rotor 16 and the multi-plate clutch 35 interposed therebetween.

The rotor 16 is provided on the inner periphery of a solenoid 32 fixed to the case 7 via a bearing 39. Therefore, the output side rotation shaft S2 spline-coupled (S) to the rotor 16 is rotatably held on the case 7 side together with the rotor 16.

Next, the operation of the belt-type continuously variable transmission having the above configuration will be described.

The belt type continuously variable transmission has two pulleys P1, P
2 and the belt B, the rotation of the input-side rotation shaft S1 is transmitted to the output-side rotation shaft S2.
The belt B is slid in the radial direction of the pulleys P1 and P2 by reciprocating the movable flanges 3 and 4 so that the widths of the V-grooves 5 and 6 change inversely with each other. Change step by step. At this time, the belt B is fixed on each of the fixed flanges 1 and 2 on the input side and the output side.
Slides in the same direction on the basis of the sliding surfaces 1a, 2a of each of the rotary shafts S1, S2 by the amount of inclination of the sliding surfaces 1a, 2a.
2 also moves in the axial direction.

In this type of belt type continuously variable transmission, both ends of the belt B are slid by the reciprocating motion of the individual movable flanges 3 and 4, so that each of the pulleys P1 and P
The belt B wraps around the rotation axis S
Misalignment in the axial direction of 1, S2 (maximum 0.8 mm
Degree) occurs.

The misalignment of the belt B is caused by, for example, a process of shifting from the LOW side to the HIGH side, that is, the movable flange 3 of the input side pulley P1 is advanced with respect to the fixed flange 1, and the belt B is moved to the input side pulley P1. , The movable flange 4 of the output side pulley P2 is retracted with respect to the fixed flange 2, and the belt B
Is zero before the movable flanges 3 and 4 are moved, increases with the amount of movement of the movable flanges 3 and 4, reaches a maximum almost at the middle, and then decreases after the movable flanges 3 and 4 are moved. And movable flanges 3, 4
Becomes zero at the end of the movement. This misalignment also occurs in the process of shifting from the HIGH side to the LOW side.

With respect to such a misalignment of the belt B, in the belt type continuously variable transmission, the output is adjusted by the misalignment adjusting means provided on the output side rotation shaft S2 while the movable flange 4 moves forward or backward. The output side pulley P2 is reciprocated in the axial direction together with the side rotation shaft S2 to correct the misalignment. Specifically, the current applied to the solenoid 32 constituting the clutch mechanism 30 is increased or decreased.

That is, the misalignment adjusting means is provided at one end of the output-side rotating shaft S2 on the cam surface 27 provided on the rotating shaft S2.
A ball 29 is interposed between the cam plate 28 and the cam plate 28 positioned on the case 7 side, and the ball 29 is engaged with a lower portion (recess) of the inclined surface 28B of the cam plate 28 as shown in the upper half of FIG. At the other end of the output side rotating shaft S2, the rotating shaft S2 is urged toward the one end by the disc spring 18, so that when the output side rotating shaft S2 rotates, the cam plate 28 And the drive clutch 33 rotates, and the rotor 16 in spline connection (S) also rotates.

When a current is applied to the solenoid 32 in this state, a magnetic field is generated and the armature 37 is moved to the solenoid 3
The drive clutch 33 and the driven clutch 36 come into contact with each other by the pressure of the armature 37 that has been sucked and moved to the side 2, and the friction force of the multi-plate clutch 35 causes the cam plate 2 to move.
8 is controlled. In this case, the clutch mechanism 30
Although it is possible to temporarily stop the rotation of the cam plate 28, the rotation of the cam plate 28 is decelerated mainly by frictional force.

When the cam plate 28 decelerates in this way, a frictional force is applied to the ball 29 due to the speed difference between the cam surface 27 that continues to rotate and the decelerated cam plate 28, and the ball 29 is raised (convex) on the inclined surface 28B. Since the cam plate 28 is positioned on the case 7 side and does not move in the axial direction of the output side rotation shaft S2 at this time, as shown in the lower half of FIG. The output-side rotation shaft S2 pressed by 29 moves toward the other end (to the right in FIG. 1) against the disc spring 18. At this time, the inclined surface 28 of the cam plate 28
B has a height difference H including the amount of misalignment of the belt B generated between the pulleys P1 and P2, so that the output side rotation shaft S2
At the same time, the entire output side pulley P2 moves a distance corresponding to the amount of misalignment, thereby correcting the misalignment occurring between the two pulleys P1 and P2.

Further, since the amount of misalignment of the belt B decreases after passing the middle in the moving process of the movable flange 4, the clutch mechanism 30 is released correspondingly, that is, the application of the current to the solenoid 32 is stopped (or Decrease). Then, the cam plate 28 tends to rotate together with the output side rotation shaft S2 via the ball 29, and the urging force of the disc spring 18 is always acting. Is the lower part (recess) of the inclined surface 28B
28L, and the entire output side pulley P2 together with the rotation output side shaft S2 moves toward one end and returns to the original position.
That is, the output side rotation shaft S2 is returned to the original position as the misalignment decreases.

As shown in FIG. 4, the misalignment adjusting means determines that the axial force due to the current applied to the solenoid 32 and the stroke of the output side rotation shaft S2 are proportional to each other (y = α).
x), there is a proportional relationship (y = −β) between the axial force of the disc spring 18 and the stroke of the output side rotation shaft S2.
x). At this time, the axial force due to the current applied to the solenoid 32 and the axial force due to the disc spring 18 act in directions to cancel each other. Therefore,
The axial force due to the actual current applied to the solenoid 32 and the stroke of the output side rotating shaft S2 are proportional to the axial force of the disc spring 18 minus the axial force (y = (α−β)
x). This also indicates that the magnitude of the current applied to the solenoid 32 is proportional to the stroke of the output side rotation shaft S2.

That is, when the current applied to the solenoid 32 is increased, the clutch mechanism 30 increases the attraction force of the armature 37 and the friction force of the multi-plate clutch 35,
As a result, the degree of deceleration of the cam plate 28 also increases, and the amount of climbing of the ball 29 on the inclined surface 28B, that is, the amount of movement of the output side rotation shaft S2 and the output side pulley P2 in the axial direction increases. The opposite is true if the current applied to the solenoid 32 is reduced. When the current applied to the solenoid 32 is kept constant, the attraction force of the armature 37 and the friction force of the multi-plate clutch 35 become constant, and the ball 2
9 is maintained at a fixed position on the inclined surface 28B, and the amount of movement of the output side rotation shaft S2 is also maintained constant.

Therefore, in the belt-type continuously variable transmission, when the current applied to the solenoid 32 is changed on the output side rotating shaft S2, as a result, the amount of movement of the output side rotating shaft S2 and the output side pulley P2 in the axial direction is changed. And the amount of misalignment of the belt B generated between the two pulleys P1 and P2 increases and decreases at a constant rate during the speed change. Therefore, while the movable flange 4 moves forward or backward, the current applied to the solenoid 32 is changed. Is not only turned on / off, but also by changing the current applied to the solenoid 32 continuously or stepwise in accordance with the speed ratio determined by the moving amount of the movable flange 4 and the like, so that the output side rotation shaft S2 and By changing the position of the output side pulley P2, it is possible to smoothly correct the misalignment of the belt B in any step of the stepless speed change. That.

As described above, according to the belt-type continuously variable transmission described in the above embodiment, the structure is extremely simple and the energization to the clutch mechanism 30 constituting the misalignment adjusting means, that is, the simple electronic control is performed. Thus, the misalignment of the belt B generated at the time of gear shifting can be corrected with high precision. By moving the pulley P2 to correct the misalignment of the belt B, uneven wear and noise of the belt B are prevented,
The durability of the belt B is maintained well, and the alignment accuracy can be greatly increased as compared with a conventional device that moves a pulley with respect to a rotating shaft by hydraulic pressure.

In the above embodiment, the output side rotation shaft S2
Is provided so as to be able to reciprocate in the axial direction.
However, the same configuration can be provided for the input-side rotation shaft S1 or both of the rotation shafts S1 and S2. Further, in the above-described embodiment, the configuration in which the inclined surface 28B is provided on the cam plate 28 has been described. However, even if the inclined surface is provided on the cam surface 27, the same operation and effect as the above-described embodiment can be obtained.

[Brief description of the drawings]

FIG. 1 is a view for explaining an embodiment of a belt-type continuously variable transmission according to the present invention, and is a cross-sectional view in which a moving state is different above and below a center line.

FIG. 2 is an enlarged cross-sectional view of one end portion of an output-side rotary shaft in the belt-type continuously variable transmission shown in FIG.

FIG. 3 is a perspective view (a) and a plan view (b) illustrating the configuration of a cam plate.

FIG. 4 is a graph showing a relationship between a current applied to a solenoid, a force in an axial direction by a disc spring, and a stroke of a rotating shaft.

[Explanation of symbols]

 B belt P1 input side pulley P2 output side pulley S1 input side rotating shaft S2 output side rotating shaft 1 2 fixed flange 3 4 movable flange 7 case 18 disc spring (elastic body: misalignment adjusting means) 27 cam surface (misalignment adjusting means) ) 28 Cam plate (center misalignment adjusting means) 28B Inclined surface (center misalignment adjusting means) 29 Ball (center misalignment adjusting means) 30 Clutch mechanism (center misalignment adjusting means) 32 Solenoid (clutch mechanism) 33 Drive clutch (clutch mechanism) 35 Multi-plate clutch (clutch mechanism) 36 Driven clutch (clutch mechanism) 37 Armature (clutch mechanism)

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[Procedure amendment]

[Submission date] July 28, 2000 (2007.2
8)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0025

[Correction method] Change

[Correction contents]

The movable flange 3 of the input pulley P1
In the figure, a cylinder portion 11 is integrally formed concentrically on the outer peripheral end on the back side. On the other hand, a piston 12 is fixed to the input side rotation shaft S1 by a ring 13. The outer peripheral end of the piston 12 is in airtight and slidable contact with the inner peripheral surface of the cylinder portion 11, and forms a pressure chamber 14 with the movable flange 3. Further, the input side rotation axis S
In FIG. 1, a flow path 15 communicating from the right end in FIG. 1 to the pressure chamber 14 is formed, and a supply means for hydraulic oil (not shown) is connected to the flow path 15. That is, the movable flange 3
Moves from the retreat position shown above the input-side rotary shaft S1 in FIG. 1 to the forward position shown below also by pressurizing and supplying the hydraulic oil to the pressure chamber 14 via the flow path 15.

Claims (4)

[Claims] 1. An input side and an output side pulleys comprising a fixed flange which is immovable in an axial direction and a movable flange which can reciprocate in an axial direction are provided on a rotating shaft on an input side and an output side arranged in parallel. In a belt-type continuously variable transmission in which both pulleys are connected by a belt, at least one of the rotation shafts is held so as to be able to reciprocate in the axial direction, and the belt misalignment generated between the pulleys with respect to the rotation shaft. A belt-type continuously variable transmission, comprising a misalignment adjusting means for reciprocating the rotating shaft in the axial direction within a range corresponding to the amount. 2. A cam surface orthogonal to an axis at one end of a rotary shaft, a cam plate positioned on a case holding the rotary shaft and rotatable about the rotary shaft, A ball interposed between the cam surface and the cam plate, a clutch mechanism for controlling the rotation of the cam plate, and an elastic body for urging the rotation shaft toward one end at the other end of the rotation shaft; One of the surfaces and the cam plate facing each other,
2. The belt-type continuously variable transmission according to claim 1, wherein an inclined surface having a height difference corresponding to an amount of misalignment of the belt generated between both pulleys is formed in a circumferential direction. 3. The clutch mechanism includes a solenoid provided on a case side for holding a rotating shaft, a plurality of drive clutches provided on a cam plate, a multi-plate clutch fixed on the case side and a drive clutch for the cam plate. 3. The belt-type continuously variable transmission according to claim 2, further comprising: an armature disposed opposite to the solenoid with a plurality of driven clutches and a multi-plate clutch therebetween. 4. The belt-type continuously variable transmission according to claim 3, wherein a current applied to the solenoid is changed according to a speed ratio.