JPH07167239A - Multi-disc type continuously variable transmission - Google Patents

Abstract

PURPOSE:To make it possible to transmit required torque at high speed by transmitting power by means of causing a power transmission ring body to make pressurized contact with an adjoining disc and displacing the pressurized contact point by means of causing the power transmission ring body to be eccentric to the shaft. CONSTITUTION:Power is transmitted between both shafts 1, 6 by a driving disc 4 provided on a drive shaft 1 after pressurizing it with pressurizing discs 2, 3 and friction drive power generated by causing a drive shaft 1 to rotate by making a follow disc 7 provided on a follow shaft 6 and a power transmission ring body 9 to come into contact under pressure. While rotating, the pressurized contact point is displaced within the area where the adjoining driving disc 4 and the follow disc 7 face each other by making the power transmission 9 eccentric to the drive shaft 1. Thus, besides being able to transmit required torque at high speed, excessive power is not needed at the time of speed change by changing speed after causing the power transmission ring body to make a stabilized rotating motion by providing a means to make the power transmission ring body eccentric to the shaft on which the power transmission ring body is provided and restoring its rotating center onto the center line connecting No.1 and No.2 shafts.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-plate continuously variable transmission equipped with a large number of discs used for transportation machines and industrial equipment.

[0002]

2. Description of the Related Art Conventionally, V-belt type continuously variable transmissions, Bayer type continuously variable transmissions, etc. have been known as continuously variable transmissions for mechanically and smoothly changing the rotation ratio of an input shaft and an output shaft. is there. Since the V-belt type uses a flexible belt as a power transmission medium, it is possible to obtain a large frictional force by widening the friction surface, and the driving torque is large and the reliability is high. When the above is used in a mechanism such as an automobile that requires high-speed rotation, a problem of strength of the power transmission medium occurs such that the belt is broken by centrifugal force due to high-speed rotation. As a method for solving the above-mentioned problem, there is a method of developing a high-strength belt or a method of using a power transmission medium as a rigid body. In the latter Bayer type continuously variable transmission, a drive shaft provided with a plurality of discs and a driven shaft provided with a plurality of discs are arranged so that the discs are alternately superposed, and the discs are axially arranged. The rotary force of the drive shaft is transmitted to the driven shaft by compressing and pressing the adjacent disks into pressure contact with each other. This Bayer type continuously variable transmission transmits power with friction obtained by pressing and contacting rigid bodies, so the friction surface becomes a point, and it is extremely small, but it has multiple points and is configured to transmit large power. Has been done.

[0003]

SUMMARY OF THE INVENTION In the above Bayer type continuously variable transmission, the radius of the portion of the disc that is in pressure contact is brought about by moving one shaft close to or away from the other shaft by a link operation. To change gears. Since this shift is a continuously variable transmission, it is naturally performed during rotation.However, since the disks are brought into pressure contact with each other at a considerably high pressure in order to obtain frictional force, the pressure contact surface is applied. There is a problem that a large force is required to move the disc in the direction of varying the effective radius of rotation against the pressure, and the size of the device becomes large. This becomes a big problem when it is adopted as a speed change mechanism of an automobile or the like which requires space saving. The present invention solves the above-mentioned problems, can transmit a required torque at a high speed, and can be downsized so that it can be used in a field requiring downsizing of an automobile or the like. It is intended to provide a continuously variable transmission.

[0004]

In order to achieve the above object, a multi-plate continuously variable transmission according to the present invention comprises at least one disc formed in a taper shape which is tapered toward the circumferential direction. At least one first shaft and a second shaft having one more disk formed in a similar shape to the disk than the first shaft are arranged in parallel, and the disks of each shaft are alternately arranged. In addition, the tapered portions of the adjacent discs are opposed to each other at a constant interval, and at least a power transmission ring having a diameter larger than that of the discs is located between the discs partially adjacent to each other. To be installed on either side of the shaft,
Further, the second shaft is provided with a pressurizing mechanism for axially pressing the disc, and the power transmission ring is brought into pressure contact with the adjacent disc, and the friction drive force at the pressure contact point is used for power transmission. Power transmission is performed between the first shaft and the second shaft via the ring body, and the power transmission ring body is eccentric with respect to the shaft on which it is provided so that adjacent disks face each other. It is characterized in that means for displacing the pressure contact point is provided within the range in which the pressure is applied. Further, the first shaft may be a drive shaft and the second shaft may be a driven shaft, and the first shaft may be a driven shaft and the second shaft may be a drive shaft. Further, the power transmission ring body may be provided on the first shaft side or the second shaft side. Preferably, the pressurizing mechanism according to the present invention may be configured to apply a pressing force corresponding to the frictional driving force at the pressurizing contact point between the power transmission ring and the adjacent disk to the pressurizing contact point. . Further, the pressure mechanism presses the pressure plate at a position corresponding to the displacement of the pressure contact point between the pressure plate formed to bend along the axial direction and the disc adjacent to the power transmission ring. , A pressing member that applies a pressing force corresponding to the friction driving force at the pressure contact point to the pressure contact point.

[0005]

According to the multi-plate continuously variable transmission of the present invention configured as described above, the disc provided on the first shaft and the second shaft and the ring for power transmission are pressurized by the pressurizing mechanism. And pressure contact,
When one of the shafts is rotated in that state, power is transmitted between the first shaft and the second shaft by the friction drive force of the portion that is in pressure contact. This power transmission is based on the ratio of the radius of contact of the power transmission ring on the disc of one shaft and the radius of the contact of the power transmission ring on the disc of the other shaft. Is determined. Further, during rotation, the power transmission ring is eccentric with respect to the shaft on which it is provided, and the rotation center of the ring is displaced from the line connecting the centers of the first and second shafts. The ring body can be moved in either axial direction so that the pressure contact point draws a spiral locus until the center of rotation of the ring body coincides with the line connecting both axes. The ratio of the radii of the contact portion between the disk of the axis of the and the disk of the other axis can be changed.

[0006]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a multi-plate continuously variable transmission according to the present invention will be described below with reference to the accompanying drawings. FIG. 1 is a schematic front view showing an embodiment of the multi-plate continuously variable transmission of this embodiment.

As shown in the drawings, the multi-plate continuously variable transmission of this embodiment is provided with three driven shafts 6 around a drive shaft 1, and a drive disk 4 and a driven shaft 6 provided on the drive shaft 1. The rotational force is transmitted between the driven disc 7 and the driven disc 7 via the power transmission ring 9. In the figure, an arrow a indicates the rotation direction of the drive shaft 1, and an arrow b indicates the rotation direction of each driven shaft 6. Since the relationship between the drive shaft 1 and each driven shaft 6 is the same for all three shafts, the two driven shafts will be omitted and the configuration of the drive shaft 1 and one driven shaft 6 will be described below.

FIG. 2 is a schematic plan view showing an embodiment of the multi-plate continuously variable transmission of this embodiment in which the two driven shafts are omitted.
It is partially broken for explanation. In the figure, reference numeral 1 denotes a drive shaft. One end of the drive shaft 1 is rotatably supported by a supporting member 16a provided on a suitable base portion (not shown) via a bearing. The other end of the drive shaft 1 is rotatably supported by a joint 15 connected to a drive source (not shown),
The nut 15 is retained by a nut 1b, and the joint 15 is rotatably supported by a support member 16b provided on a base portion (not shown). The drive shaft 1 is provided with two pressurizing discs 2 and 3 which also function as a drive disc at appropriate intervals. One pressurizing disk 3 is a stopper 3a that is swingable so as not to slide in the axial direction in the direction of the support member 16a.
Are supported on the driven disk 6, and thereby the pressure applied to each driven disk 7 of the three driven shafts 6 is averaged. The other pressurizing disc 2 constitutes a pressurizing mechanism, which will be described later, together with the joint 15, and the drive disc 4, the driven disc 7, and the ring 9 are arranged in accordance with the magnitude of the load applied to the drive shaft 1. The rotational force of the joint 15 is transmitted to the drive shaft 1 while being pressed in the axial direction. Between the pressurizing discs 2 and 3 of the drive shaft 1, there are a plurality of drive discs 4 formed in a tapered shape in the circumferential direction (in this embodiment, 9 discs, therefore, In the embodiment, there are substantially 11 drive discs including the press discs 2 and 3), and a spacer 5 is provided between each drive disc 4. Each is provided.

Reference numeral 6 in the drawing denotes a driven shaft, which is also rotatably supported by an appropriate supporting member (not shown). The driven shaft 6 is provided with a plurality of driven discs 7 (10 in this embodiment) formed in a similar shape to the drive discs 4, and a spacer is provided between each driven disc 7. 8 are provided. The pressurizing disks 2 and 3,
The drive disc 4 and the spacer 5 are attached to the drive shaft 1 by an appropriate method such as spline fitting so as to be slidable in the axial direction. Similarly, the drive disc 7 and the spacer 8 are also attached to the drive shaft 6. The spline is fitted. As shown in FIG. 2, the drive shaft 1 and the driven shaft 6 are formed in a comb shape in which tapered portions of adjacent disks 4 and 7 are partially opposed to each other at a constant interval. It is arranged so as to overlap.

FIG. 3A is a plan view of the spacer 5, FIG.
(B) is a cross-sectional view taken along the line AA of (a). As shown in the drawing, the spacer 5 has four protrusions 5a on the front and back surfaces.
5b are provided at a 45 degree offset, and the protrusions 5a,
The spacer 5 is made elastic by 5b so that it can respond to the delicate movement of the drive disk 4 that slightly moves in the axial direction when being pressed. The spacer 8 also has a structure similar to that of the spacer 5, and copes with a slight deformation of the driven disk 7 and a shift in the axial direction.

FIG. 4 is a schematic enlarged view of a power transmission portion of the multi-plate continuously variable transmission shown in FIG. 1, and FIG. 5 is a sectional view taken along line BB in FIG.
FIG. 6 is a view corresponding to FIG. 5 showing a state immediately after the control cam is moved, and FIG. 7 is a view corresponding to FIG. 5 showing a state after the movement of the power transmission ring is completed. . As shown in the drawing, the drive shaft 1 and the driven shaft 6 are adjacent to each other such that the tapered portions of the adjacent discs 4 and 7 are partially opposed to each other at a constant interval. The circular plates 4 and 7 are arranged so as to overlap each other in a comb shape. A power transmission ring 9 as a power transmission medium is provided between these adjacent discs 4 and 7, and thereby the rotational force is transmitted from the drive disc 4 to the driven disc 7. . The power transmission ring 9 is mounted so that a part of the power transmission ring 9 is sandwiched between the driving disc 4 and the driven disc 6 which are adjacent to each other. When pressure is applied in the direction of arrow f in 4), on the line X (hereinafter referred to as the axis line X) connecting the shaft center 4 ′ of the driving disk 4 and the shaft center 7 ′ of the driven disk 7, The contact points 10 are pressed by the side surfaces of the tapered portions of the adjacent discs 4 and 7 and elastically deformed.
Is obtained (see FIG. 5). In the present embodiment, the contact point 10 is drawn in a large size in the drawing for easy understanding, but in reality it is obtained by elastic deformation of rigid bodies such as metal, so it is a very small surface. There is no end. The drive shaft 1 is provided with an oil passage 1a for supplying oil to the surfaces of the contact point 10, the driving disc 4, and the driven disc 7 described above. Oil is constantly supplied to the oil passage 1a via an oil pump (not shown) set to supply an appropriate amount of oil, while the drive shaft and the driven shaft are rotating, and the protrusion of the spacer 5 is provided. The surfaces of the driving disk 4 and the driven disk 7, that is, the contact points 10 and the like are lubricated and cooled through the slits formed by 5a and 5b (see FIG. 2).

The power transmission ring 9 is formed so that its diameter is larger than that of the driven disc 7, and the gap formed by the tapered portions of the adjacent discs 4 and 7 as described above. It is formed into a conical shape so that it can be mounted on the power transmission ring body 9 (see FIG. 8). When mounted, the power transmission ring 9 has an outer periphery protruding outward from the driven disk 7, and the protruding portion of the outer periphery is supported by a pair of control cams 11 and 12.
The center of rotation 9'is located on the axis X. In FIG. 5, the upper control cam 11 is the inclined support surface 1.
1a, the support surface 11a is positioned so as to approach the power transmission ring body 9 within a limit not hindering the rotation of the power transmission ring body 9, and the support surface 11a is parallel to the axis line X in the left-right direction (in FIG. 5) by an appropriate mechanism. It is attached to a foundation (not shown) by a suitable method so that it can move in the direction of arrow c). The lower control cam 12 is provided with a support surface 12a inclined so as to be parallel to the support surface of the upper control cam 11, and is moved in the same direction by the same distance in parallel with the control cam 11 by an appropriate mechanism. Is configured to. These control cams 11,
The guide members 13 and 14 of the power transmission ring 9 are provided at 12 to prevent the vibration of the power transmission ring 9.

The operation of the power transmission portion in the continuously variable transmission of this embodiment constructed as above will be described with reference to FIGS. 5 to 7. First, when the drive shaft 1 is rotated, its rotational force is transmitted from the drive disc 4 to the driven disc 7 via the power transmission ring 9 by the frictional force at the contact point 10.
Effective rotation radii d and D of the drive shaft 1 and the driven shaft 6 at this time
Has a relationship of D> d, and the driven shaft 6 rotates at a lower speed than the drive shaft 1 (see FIG. 5). In this rotating state, when the control cams 11 and 12 are moved leftward by the same distance L1 as shown in FIG.
Since it is only supported by the contact point 10 with the control cams 11 and 12, the contact point 10 tilts downward with the fulcrum as a fulcrum, and an angle θ is generated between the rotation center 9 ′ and the axis X (FIG. 6). The power transmission ring 9 has its contact point 1
0 moves toward the control cams 11 and 12 so that 0 draws a spiral locus Y toward the large diameter direction of the driving disk 4, that is, toward the small diameter direction of the driven disk 7. start,
When reaching the control cams 11 and 12, the lower control cam 1
While being lifted upward with the contact point 10 as a fulcrum along the second support surface 12a, the control cams 11, 12 side, that is,
It moves to the left in the drawing, and its rotation center 9'is the above-mentioned axis X.
The movement is stopped when the state is reached (see FIG. 7). In FIG. 7, the dotted line Y indicates the locus of the contact point 10 on the drive disk 4 when the power transmission ring 9 moves, and from the drawing, this power transmission ring 9 also controls the cams 11, 12. It can be seen that it is moving to the left following the movement of. As a result, the effective rotation radii d and D of the drive shaft 1 and the driven shaft 6 become D <d, the transmission ratio from the drive shaft 1 to the driven shaft 6 changes, and the driven shaft 6 rotates faster than the drive shaft 1.

FIGS. 9 (a) and 9 (b) are principle diagrams for briefly explaining the principle of the movement of the power transmission ring 9 described above in another example. In FIG. 9A, a wheel 51 is placed on a rotating plate 50 and the wheel 51 is supported by a pendulum device 52. When the rotating plate 50 is rotated in the direction of arrow r1, the axis center line X2 of the wheel 51 always rotates. The wheel 51 stably rotates along the circular locus Y2 through the rotation center 53 of the plate 50. When the fulcrum 52a of the pendulum device 52 is displaced to the left as shown in FIG. 9B while the rotary plate 50 is still rotated, the wheel 51 has its axis center line X2 at the center 53 of the rotary plate 50. On the other hand, the angle θ2 is inclined and the spiral plate Y3 is drawn on the rotary plate 50 in the outward direction of the rotary plate 50 while the angle θ2 is reduced. And the wheel 51 has its axis center X2
After moving to a position passing through the center 53 of the rotary plate 50, it rotates stably while drawing a circular locus Y4 again. The power transmission ring body 9 according to this embodiment also moves in the left-right direction on the same principle.

FIG. 10 shows an enlarged view of the guide member 13 for explaining the structure and operation of the guide member 13. Figure 10 (a)
As shown in, the guide member 13 is formed by stacking two guide bodies 13a and 13b each having a comb-shaped slit capable of guiding a plurality of power transmission ring bodies 9 every other one ( (See FIG. 5), both ends are supported by pistons 11d and 11e fixed respectively to a pair of left and right arms 11b and 11c provided on the control cam 11, and are independently slidable in the left and right direction. . Since the support structures of the guide bodies 13a and 13b are the same structure, the configuration of the support structure of the guide body 13a will be described below and the description of the guide body 13b will be omitted. An oil passage 11f through which oil passes is formed inside the piston 11d, and the oil supplied through an oil pump (not shown) passes through the oil passage 11f and the piston 11d.
It is supplied to the oil reservoir 13c of the guide body 13a from a small-diameter hole (no reference numeral) provided at the tip of the. On the other hand, a screw groove is formed in a hole 13d which is provided in the guide body 13a and which forms the oil reservoir 13c (not shown), and the oil supplied to the oil reservoir 13c is the hole 13d.
It is discharged to the outside through the gap between the screw groove provided in the and the piston 11d. The oil supplied to the oil reservoir 13c is supplied at a low pressure that does not run short of the oil in the oil reservoir 13c when the guide bodies 13a and 13b slide in the left-right direction, and the power transmission ring body 9 is normally operated. If the guide body 13a, 13
b follows, and when the power transmission ring 9 suddenly moves due to vibration or the like, the oil in the oil reservoir 13c acts as a damper by the action of the small diameter hole provided in the piston 11d. The guide bodies 13a and 13b suppress the power transmission ring body 9 to prevent vibration and the like. FIG. 10B shows the contact point 1 of the power transmission ring 9 from the state shown in FIG. 10A (this state corresponds to the states of FIGS. 2 and 5).
When 0 moves in the small diameter direction of the driven disk 7 (see Fig. 7)
The state of the guide member 13 is shown. As shown in the drawing, the guide body 13a is pushed by the power transmission ring body 9a guided by the guide body 13a and moves in the direction of the arrow L, so that the guide body 13b
Is pushed by the power transmission ring 9b guided by it and moves in the direction of arrow R. The structure of the guide member 13 described above and the guide member 1 provided on the lower control cam 12
Since the configuration of 4 is the same, the description of the guide member 14 is omitted.

Next, the pressing mechanism provided on the drive shaft 1 will be described. 11A is an enlarged view of the periphery of the pressurizing disc 2 of the drive shaft 1, and FIG. 11B is a pressurizing disc 2 and joint 1.
Nos. 2a and 15b respectively provided in the flange portion 15a of No. 5
And a pressure ball 17 placed in these holes 2a, 15b
11 (c) is an enlarged view of FIG.
It is a figure corresponding to (b). Drive shaft 1 as shown in the drawing
A drive disk 4, a spacer 5 and a pressurizing disk 2 are spline-fitted to the shaft 1. The shaft 1 itself is rotatably supported by a joint 15 connected to a power source such as an engine crankshaft (not shown). This joint 1 is secured by a nut 1b.
5 is pivotally supported by the support member 16a. A flange portion 15a having a shape that matches the pressurizing disc 2 is formed in a portion of the joint 15 that faces the pressurizing disc 2, and a small diameter portion and a large diameter portion of the flange portion 15a and the pressurizing disc 2 are formed. A plurality of holes 2a and 15b tapered toward the bottom are provided at opposite positions on the same circumference of the part.
A pressure ball 17 is placed in a and 15b (Fig. 11).
(See (a) and (b)). Therefore, when the power source is driven and a rotational force is applied to the joint 15, a shift t occurs in the holes 2a and 15b due to the load on the drive shaft 1 side, which causes a shift in the direction in which the pressurizing force is generated and the pressurizing force is generated. generate f. This pressing force f is applied to the pressing disk 3 provided at the other end of the drive shaft 1.
And the driving disk 4, the driven disk 7 and the power transmission ring 9 located between the pressure disk 2 and the pressure disk 2 (FIG. 11C).
reference).

By the way, as shown in FIG. 11, the pressurizing disc 2 is thinned so that the large-diameter portion and the small-diameter portion where the holes 2a are provided are thinned, and this portion is elastically deformed. The ratio of the applied pressure is substantially changed according to the position of the power transmission ring 9.
That is, as shown in FIG. 11A, when the contact point 10 of the power transmission ring 9 is on the large-diameter portion of the drive disk 4, most of the rotational force is transmitted as indicated by arrow F1. . At this time, the holes 2a and 15b and the ball 1 provided in the small diameter portion
By the action of 7, the small-diameter portion of the pressurizing disc 2 is also pressed, but the small-diameter part of the pressurizing disc 2 is formed thin, and the pressurizing direction of the small-diameter part becomes a space. Therefore, the small diameter portion of the pressurizing disc 2 is slightly elastically deformed, and the force for pushing the power transmission ring 9 is extremely small at that portion, and the power transmission ring 9 is mostly used for the pressing force. It concentrates on a certain large diameter part.

In FIG. 12, the power transmission ring 9 is the pressurizing disc 2.
It is a figure corresponding to FIG.11 (a) which shows a transmission method of the pressurizing force when it moves to the small diameter part. In this case, FIG.
Contrary to (a), the rotational force is transmitted to the drive shaft 1 through the small-diameter portion as indicated by the arrow F2, and the pressing direction of the large-diameter portion becomes a space, so that the large diameter of the pressing disk 2 is increased. The part is deformed,
The pressing force proportional to the rotating force is concentrated on the small diameter portion. Although not shown, when the contact point 10 of the power transmission ring 9 is between the large-diameter portion and the small-diameter portion of the pressurizing disc 2, the large-diameter portion of the pressurizing disk 2 is determined to correspond to the position ratio. Both the holes 2a and 15b provided in the small-diameter portion and the ball 17 act so that the pressing force acts on the position where the contact point 10 exists.

With the configuration as described above, the pressing force f corresponds to the pressure contact point 10 corresponding to the position of the power transmission ring 9.
Since the frictional drive force increases and decreases in proportion to the magnitude of the frictional drive force, the transmission efficiency during normal operation deteriorates by setting the pressure force at maximum load, as in a continuously variable transmission in which the pressure force does not change. The problem is solved. The ratio between the rotational force and the pressing force is determined by the taper angle of the holes 2a and 15b, so the taper angle is set according to the number of the driving disks 4, the friction coefficient of the contact point 10, and the like. Further, by partially thinning the pressurizing disc 2, the diameter of the portion to which the pressurizing force is applied is moved in accordance with the movement of the power transmission ring body 9, and its contact point 1
The running diameter of 0 and the diameter of the portion to which the pressing force is applied can be made the same, and the power transmission ring 9 at the position of the contact point 10 and the adjacent discs 4 and 7 are constantly pressed with an appropriate pressing force. The effect that they can be brought into contact is achieved.

FIG. 13 is an enlarged view of a portion corresponding to FIG. 11A of a multi-plate continuously variable transmission adopting another embodiment of the pressurizing mechanism. Since the configuration of the portion other than the pressurizing mechanism of the multi-plate continuously variable transmission in this embodiment is the same as that of the embodiment shown in FIG. 2, the same reference numerals as those in the embodiment shown in FIG. Omit it. In the figure, 1 is a drive shaft, and this drive shaft 1
Is rotatably supported by a joint 15 'and is prevented from coming off by a nut 1b. A pressurizing disc 2'is spline-fitted to the drive shaft 1, and the pressurizing disc 2'of the joint 15 'is fitted.
A flange 15a 'is formed at a position corresponding to. The pressurizing disc 2'is a thin disc, the surface on the side of the drive disc 4 is formed in a tapered shape corresponding to the drive disc 4, and the surface on the side of the flange portion 15a 'is formed from the center of the disc. A plurality of grooves 2 a ′ having a tapered cross section extending in the circumferential direction are provided (see FIG. 14A, this figure shows a schematic top view of the pressing disk 2 ′). On the other hand, the surface of the flange 15a 'of the joint 15 on the pressurizing disc 2'side is provided with a tapered groove 15b' at a position corresponding to the groove 2a 'of the pressurizing disc 2'.

The pressing disk 2'and the flange portion 1 of the joint 15
5a 'is a groove 2a' and 15b 'which are provided in each of them when assembled
Are positioned so as to correspond to each other, and the groove 2a ′ and the groove 15 are
An appropriate number of cylindrical pressure rods 17 'are put in each space formed by b' (see FIG. 14 (b), which is a sectional view taken along the line CC in FIG. 13), and the outer end It is prevented from coming off by the section.

The operation of the pressurizing mechanism configured as described above will be explained. When the power source is driven and a rotational force is applied to the joint 15, the load on the drive shaft 1 side causes the grooves 2a 'and 15 to be formed.
A displacement t'is generated in the portion b ', which causes the pressing force f'.
Occurs and the pressurizing disc 2'is axially pressed (Fig. 1
4 (c), this figure is a diagram corresponding to FIG. 14 (b) showing a state after the deviation t ′ has occurred. ). The deviation t ′ increases in proportion to the load applied to the drive shaft 1, that is, the magnitude of the friction driving force at the contact point 10, so that the applied pressure is proportional to the magnitude of the friction driving force at the contact point 10. Become. Since the pressurizing disc 2'is formed thin so as to be easily elastically deformed, the portion without the contact point 10 is elastically deformed according to the position of the contact point 10 of the power transmission ring body 9 to apply the pressing force f. 'Is released and the pressure is concentrated at the contact point 10. Figure 15
(A), (b), (c) shows an example of a deformed state of the pressure disk 2 ′ according to the position of the contact point 10.

FIG. 16 is a schematic sectional view showing still another embodiment of the pressing mechanism. In the figure, 20 indicates a drive shaft. A pressurizing disc 21, a drive disc 22 and a pressurizing body 23 are spline-fitted to the drive shaft 20, and fixed to a joint 24 connected to a drive source (not shown) with a nut 25. In the figure, reference numeral 26 denotes a pressure plate, and 27 denotes a pressure ball. Nine of them are provided on the joint 24 at intervals of 40 degrees. Each pressure plate 26 is configured to rotate about a shaft 28. The pressure ball 27 is the pressure body 2
The pressurizing body 23 is fitted in the tapered groove 23a provided in the No. 3 and pressurizes in the extension direction of the line connecting the shaft 28 and the center of the pressurizing ball 27. The pressurizing body 23 is guided by the pressurizing plate 26 and moves together with the pressurizing plate 26 around the shaft 28 to change the pressurizing direction. A gear 26a is formed on the pressure plate 26, and the gear 26a meshes with a tubular gear body 29. The gear body 29 is a control cam (11 in FIG. 5,
(A member corresponding to 12) is held by the tubular body 30 so as to move in the vertical direction together with the tubular body 30 which moves in the vertical direction in association with the movement of the pressing cam 26. It rotates about the shaft 28 in conjunction with the movement of (not shown). In the figure, reference numeral 30a denotes a gear for converting the linear motion of the control cam into rotational motion, and 30b denotes a cam pin. The cam pin 30b is a cam groove of a cam body 31 formed obliquely from the upper side to the lower side. Is engaged with. In the figure, 32 is a driven disk, 33 is a power transmission ring, and 34 is a contact point.

The operation of the pressurizing mechanism configured as described above will be described with reference to the schematic diagrams shown in FIGS. 17 (a) and 17 (b). When the pressure ball 27 is in the position shown in FIG. 17A, the pressure ball 27 has a line X connecting the shaft 28 and the center 27a of the pressure ball 27.
The pressing body 23 is pressed by the force of f5 in the extending direction of 3. At this time, the pressing body 23 is pressed in the axial direction of the drive shaft 1 by the force f4. From this state, the gear body 29 is lowered to move the pressure plate 26 to the center of rotation 2.
Figure 6 shows the state after rotating counterclockwise in the drawing around 6b.
7 (b). When the position of the pressurizing ball 27 is changed by rotating the pressurizing plate 26 in this way, the pressurizing direction of the pressurizing ball 27 changes, but the pressing force does not change, so the pressurizing body 23 is pressed in the axial direction. The power will be smaller. The width of the force pressing in the axial direction can be arbitrarily set by adjusting the rotation width of the pressure plate 26.
In the case of (b), the force f4 by which the pressurizing balls 27 press the pressurizing body 23 in the axial direction is set to be 1/2 of the state of FIG. 17 (a). In this way, the pressure ball 27 is moved to change the angle of the pressure ball 27 acting on the pressure body 23, and the force for pressing the pressure body 23 in the axial direction is moved by the control cam (not shown). The pressure applied to the contact point 34 can be changed approximately with respect to the theoretical value by being configured to be changed according to According to this pressurizing mechanism, the pressurizing disk 21 is configured to be uniformly pressed by the nine pressurizing balls 26 provided in the circumferential shape, and therefore, the four shafts (that is, the drive shafts) of the present embodiment. The present invention is not limited to the configuration of one driven shaft to three), and a desired effect can be obtained even when applied to a configuration of one driven shaft to one drive shaft.

FIG. 18 shows a third embodiment of the pressing mechanism.
FIG. 1 is a schematic front view of a continuously variable transmission showing a state in which it is applied to a continuously variable transmission having a shaft (that is, one driven shaft and two driven shafts). The relationship between the drive shaft and the driven shaft other than the pressurizing mechanism is the same as in the case of the embodiment shown in FIG. 2, so common parts are designated by the same reference numerals and detailed description thereof is omitted. In FIG. 1, reference numeral 1 denotes a drive shaft, and a plurality of drive discs 4 and spacers (not shown) are alternately spline-fitted to the drive shaft 1. Reference numeral 6 in the drawing denotes a driven shaft, and a plurality of driven disks 7 and spacers (not shown) are alternately spline-fitted to the driven shaft 6. These driven shafts 6 are respectively arranged on both sides of the drive shaft 1 so that the driving discs 4 and the driven discs 7 are alternately overlapped with each other, and like the embodiment of FIG. A plurality of power transmission ring bodies 9 are provided so as to be sandwiched between the driven disc 7 and the driven disc 7. 11, 1 in the figure
Reference numeral 2 denotes a control cam, and the control cams 11 and 1
2 is movable parallel to the left-right direction in FIG.
The position of the power transmission ring 9 is controlled. Therefore, drive shaft 1
When is rotated in the direction of arrow a ', power is transmitted to the driven shafts 6 on both sides via contact points 10 (not shown) obtained by the power transmission ring 9, and they rotate in the direction of arrow b'. In the figure, reference numeral 40 indicates a basic frame, and the drive shaft 1 is the basic frame 4
0 is rotatably supported by an appropriate support member (not shown) provided at 0, and one end thereof is connected to a power source (not shown) such as a motor or a crank of an engine. The driven shaft 6 is rotatably supported by the support plates 41 and 42 near both ends thereof. The support plates 41, 42 are formed in the same shape and are connected by three rod-shaped members 43, 43, 43 to be integrated. The support plates 41 and 42 are supported by upper and lower supports 44 and 45 provided on the base frame 40.

FIG. 19 is an explanatory view of the principle of the above-mentioned pressing mechanism. When the drive shaft 1 rotates in the direction of the arrow a ′, the rotational force of the drive disk 4 is transmitted to the driven disk 7 via the contact point obtained by the power transmission ring body 9. The point 10 is that the driven shaft 6 on the right side is moved downward and the driven shaft 6 on the left side is
Press upward. Since the line connecting the fulcrum q of the driven shaft 6 and the axis center has an angle θ with respect to the vertical line B, these vertical lines B
Is a vector of forces pushing the driven shaft 6 downward and upward, a component force F3 toward the drive shaft 1 side is generated. The contact point 10 is obtained when the power transmission ring 9 is sandwiched between the driving disc 4 and the driven disc 7 which are adjacent to each other, and they come into contact with each other. When it is pushed to the drive shaft 1 side and slightly moves to the drive shaft 1 side, the contact point 10
The pressure will be applied to. In this pressurizing mechanism, the driven shaft needs to move slightly for pressurization, as described above,
It is preferable to attach a universal joint or the like to the output portion of the driven shaft. According to the above-mentioned pressurizing mechanism, since the pressing force changes in proportion to the frictional driving force at the contact point 10, there is no waste, and it is possible to constantly apply the pressing force to the contact point 10.

The number of discs in the multi-plate continuously variable transmission described above is not limited to this embodiment, and can be appropriately changed according to the magnitude of the force to be transmitted, that is, the horsepower of the drive shaft. Of course. Further, the shaft on which the pressurizing mechanism is provided is not limited to the present embodiment, and may be provided on any shaft as needed as long as it can be compressed so that the power transmission ring and the adjacent disk can be pressed and contacted. For example, it may be provided on the driven shaft side. Further, the shaft on which the power transmission ring is provided is not limited to the present embodiment, and a part of the power transmission ring is located in the gap formed between the adjacent discs and is pressed by the pressure mechanism. Any shaft may be provided as long as it is provided so as to be in pressure contact with an adjacent disc, and for example, it may be provided on the drive shaft side if necessary. The multi-plate continuously variable transmission of this embodiment is
Since a plurality of drive discs and driven discs are stacked in a comb shape so as to transmit power through the power transmission ring 9, the drive discs and the driven discs are The effect is that the magnitude of the transmission torque can be adjusted by simply increasing or decreasing the pressure contact area by simply increasing or decreasing. Further, in the multi-plate type continuously variable transmission of the present embodiment, the larger the number of the disks 4, 7 and the number of the power transmission ring 9 are, the more the contact points for power transmission are increased, and thus the high torque is transmitted. However, in the multi-plate continuously variable transmission according to the present embodiment, the control cams 11 and 12 are moved in the left-right direction by an appropriate distance regardless of the number of the power transmission ring bodies 9. With a small amount of control force, the transmission gear ratio from the drive shaft 1 to the driven shaft 5 can be changed, that is, the rotation of large horsepower can be freely controlled with a small force. . In addition, the multi-plate continuously variable transmission of this embodiment has a circular disc 4,
7 are alternately stacked in the axial direction in a comb shape, and these are pressed in the axial direction to obtain the contact points with the power transmission ring body. Therefore, in order to increase the transmission torque, the disc Even if the number of sheets is increased, the pressing force is not proportionally increased.

[0028]

The multi-plate continuously variable transmission of the present invention is similar to at least one first shaft provided with at least one disk formed in a taper shape which is tapered in the circumferential direction. A second shaft having one more disk formed in a shape larger than the first shaft is arranged in parallel so that the disks of the respective axes are alternately arranged, and the tapered portions of the adjacent disks are To be opposed to each other at a constant interval, at least a power transmission ring having a diameter larger than that of the disk is provided on one of the shafts so that a part thereof is located between the adjacent disks, Further, the second shaft is provided with a pressurizing mechanism for axially pressing the disc, and the power transmission ring is brought into pressure contact with the adjacent disc, and the friction drive force at the pressure contact point is used for power transmission. Since power is transmitted between the first shaft and the second shaft via the ring body, Compared with a continuously variable transmission that uses a flexible V-belt, the durability is improved, high torque can be transmitted at high speed, and a power transmission ring is attached to the shaft on which it is provided. By providing a means that can be eccentric,
Movement for stabilizing the rotation by returning the center of rotation of the power transmission ring to the line connecting the axes of the first shaft and the second shaft when the power transmission ring is eccentric during rotation Since the power transmission annulus is used to shift gears, it does not require a large force when shifting, unlike the conventional Bayer type continuously variable transmission, and it is possible to downsize the device. This also has the effect of making it easier to control. Discs of similar shape are provided on the first shaft and the second shaft, and the discs are arranged so as to partially oppose each other with a constant interval, and a power transmission ring is arranged so as to be pressed between the adjacent discs. Since it is provided so that power can be transmitted between the first shaft and the second shaft, the number of disks and the number of power transmission rings are appropriately set according to the magnitude of the driving force to be transmitted. By changing the frictional surface, the driving force can be transmitted with the minimum necessary size.

[Brief description of drawings]

FIG. 1 is a schematic front view showing an embodiment of a multi-plate continuously variable transmission according to the present embodiment.

FIG. 2 is a schematic plan view showing an embodiment of the multi-plate continuously variable transmission of this embodiment in which two driven shafts are omitted.

3A is a plan view of a spacer, and FIG. 3A is a cross-sectional view taken along line AA of FIG.

FIG. 4 is a schematic enlarged view of a power transmission portion of the multi-plate continuously variable transmission shown in FIG.

5 is a sectional view taken along line BB in FIG.

FIG. 6 is a diagram corresponding to FIG. 5 showing a state immediately after moving the control cam.

FIG. 7 is a view corresponding to FIG. 5 showing a state after the power transmission ring has finished moving.

FIG. 8 is a perspective view of a single power transmission ring body.

9 (a) and 9 (b) are principle diagrams for explaining the principle of movement of the power transmission ring.

FIG. 10A is a partially enlarged view of a guide member, and FIG. 10B is a partially enlarged view corresponding to FIG. 10A showing a state of the guide member after the power transmission ring has moved.

FIG. 11A is an enlarged view of the periphery of a drive shaft pressurizing disc; FIG. 11B is an enlarged view of holes and balls provided between the pressurizing disc and the joint; and FIG. 11C is a pressurizing disc and joint. An enlarged view corresponding to (b) showing a state in which the pressing force F is generated due to the deviation

FIG. 12 is a view corresponding to FIG. 11 (a) showing how pressure is transmitted when the power transmission ring moves to the small diameter portion of the pressurizing disc.

FIG. 13 is a partially enlarged view of a multi-plate continuously variable transmission adopting another embodiment of a pressure mechanism.

14A is a schematic top view of a pressurizing disc, FIG. 14B is a cross-sectional view taken along line CC of FIG. 13, and FIG. 14C is a view corresponding to FIG. 14B showing a state after a displacement t ′ has occurred.

15 (a), (b), and (c) are diagrams showing an example of a deformed state of the pressure disk 2'according to the position of the contact point 10. FIG.

FIG. 16 is a schematic sectional view showing still another embodiment of the pressurizing mechanism.

17 (a) and (b) are explanatory diagrams of the principle of the embodiment disclosed in FIG.

FIG. 18 is a schematic front view of a continuously variable transmission showing still another embodiment of the pressurizing mechanism.

FIG. 19 is an explanatory view of the principle of the embodiment shown in FIG.

[Explanation of symbols]

1 Drive shaft 1a Oil passage 1b Nut 2 Pressurizing disc 2'Pressurizing disc 2a Hole 2a 'Groove 3 Pressurizing disc 3a Stopper 4 Drive disc 4'Axis center 5 Spacer 6 Driven shaft 7 Driven disc 7'axis center 8 spacer 9 power transmission ring 9'rotation center 10 contact point 11 control cam 11a support surface 11b arm 11c arm 11d piston 11e piston 11f oil passage 12 control cam 12a support surface 13 guide member 13a guide body 13b Guide body 13c Oil sump 13d hole 14 Guide member 15 Fitting 15 'Fitting 15a Flange part 15a' Flange part 15b Hole 15b 'Groove 16a Support member 16b Support member 17 Pressurizing ball 17' Pressurizing rod X axis: Drive disk Line connecting the shaft centers of the driven disc and the driven disc Y The locus of the contact point L1 The moving distance of the control cam a The rotational direction of the drive shaft b The rotational direction of the driven shaft c The movable direction of the control cam D The effective of the driven shaft Radius of rotation d Effective half rotation of drive shaft Diameter f Pressing force F Pressing direction L Moving direction of guide body 13a R Moving direction of guide body 13b 20 Drive shaft 21 Pressing disk 22 Driving disk 23 Pressing body 23a Groove 24 Joint 25 Nut 26 Pressing plate 26a Gear 27 Pressurizing ball 27a Center 28 Shaft 29 Gear body 30 Cylindrical body 30a Gear 30b Cam pin 31 Cam body 32 Driven disc 33 Power transmission ring 34 Contact point 40 Base frame 41 Support plate 42 Support plate 43 Rod-like member 44 Support Body 45 Support p Support direction of support plate q Support direction of support plate F3 Applied pressure

Claims (7)

[Claims] 1. At least one first shaft having at least one disk formed in a taper shape which is tapered toward the circumferential direction, and a disk formed in a similar shape to the disk.
The second shaft, which is provided with one more than the shaft, is arranged in parallel, the discs of the respective shafts are alternately arranged, and the taper portions of the adjacent discs are opposed to each other at a constant interval. A shaft for power transmission having a diameter at least larger than that of the disc is provided on one of the shafts so that a part thereof is located between the adjacent discs, and the disc is axially arranged on the second shaft. A pressurizing mechanism for pressurizing the power transmission ring body is brought into pressure contact with an adjacent disk, and the friction drive force at the pressure contact point causes the power transmission ring body to pass through the first shaft and the second shaft. In addition to transmitting power to the shaft, the power transmission ring is eccentric with respect to the shaft on which it is provided, and the pressure contact point is set within the range where the adjacent disks face each other. A multi-plate continuously variable transmission characterized in that it is provided with means for displacing it. 2. The multi-plate continuously variable transmission according to claim 1, wherein the first shaft is a drive shaft and the second shaft is a driven shaft. 3. The multi-plate continuously variable transmission according to claim 1, wherein the first shaft is a driven shaft and the second shaft is a drive shaft. 4. The multi-plate continuously variable transmission according to claim 1, wherein the power transmission ring is provided on the first shaft side. 5. The multi-plate continuously variable transmission according to claim 1, wherein the power transmission ring is provided on the second shaft side. 6. The pressurizing mechanism is configured to apply a pressing force corresponding to a frictional driving force at a pressurizing contact point between the power transmission ring and the adjacent disk to the pressurizing contact point. The multi-plate type continuously variable transmission according to any one of claims 1 to 5. 7. The pressure mechanism includes a pressure plate at a position corresponding to displacement of a pressure contact point between the pressure plate formed to bend along the axial direction and the disc adjacent to the power transmission ring body. 6. The multi-plate type none according to any one of claims 1 to 5, further comprising: a pressing member that presses and applies a pressing force corresponding to a frictional driving force of the pressing contact point to the pressing contact point. Gearbox.