JPH06147284A - Toroidal type continuously variable transmission - Google Patents

Abstract

PURPOSE:To reduce the generation of working noise and vibration by uniformizing a contact pressure between input or output discs and a loading cam. CONSTITUTION:A plurality of loading cams 16 and an intermediate disc 15 with the outer periphery of which a power transmission gear 18 for an input is formed integrally are peripherally arranged between a pair of input discs 5 and 9. Cam plates 87 and 87 are arranged between the loading cam 16 and the input discs 5 and 9. A cam surface 87a for engaging the loading cam 16 is formed at each cam plate 87. Each cam plate 87 is radially spline-coupled to the input discs 5 and 9. Thus, though, during transmission of a power, microwaving deformation in an axial direction occurs to the cam plate 87, a power is transmitted from the cam plate 87 to the input discs 5 and 9 without being influenced by deformation of the cam plate 87, and a contact pressure between the input discs 5 and 9 and the loading cam 16 is uniformized.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to improvement of a toroidal type continuously variable transmission, and more particularly to measures for reducing its operating noise and vibration.

[0002]

2. Description of the Related Art Conventionally, as a toroidal type continuously variable transmission, as disclosed in, for example, Japanese Patent Application Laid-Open No. 62-251559 and Japanese Utility Model Publication No. 3-2041, an input disk and an output disk having a toroidal surface are provided. A toroidal type continuously variable transmission unit having a plurality of tiltable rollers arranged between the toroidal surfaces of the two disks, transmitting power from the input disk to the output disk via the rollers, It is known that the gear ratio between both disks can be adjusted steplessly by the inclination angle.

In both of the above publications, two sets of toroidal type continuously variable transmission units are provided. In the former publication, the rear surfaces of two input disks are arranged so as to face each other.
A power transmission gear for power input is arranged between the both input disks. In the latter publication, the rear surfaces of the two output disks are arranged so as to face each other, and the power for extracting power between the both output disks is arranged. The transmission gear is arranged.

By the way, in the conventional toroidal type continuously variable transmission, as shown in FIG. 6, a pair of disks a and b, whose rear surfaces are opposed to each other, and a power transmission gear e are arranged in the circumferential direction. , A plurality of loading cams are arranged on the disk, and a pair of disks a, b and a power transmission gear e are each formed with a cam surface having a notched surface facing the loading cam o. Power transmission between the gear e and the pair of disks a and b is performed via the loading cams o and o. Further, a hollow cylindrical tube c is arranged between the disks a and b so that a phase difference does not occur between both rotations of the pair of disks a and b, and the tube c and the disks a and b are connected to each other. Join the splines,
A roller (not shown) that regulates the relative rotation between the disks a and b and allows the disks a and b to move relative to each other in the axial direction, and slides between the disks a and b and their toroidal surfaces a1 and b1. ) Is configured so that the pressure contact with
Further, the power transmission gear e is supported on the outer circumference of the tube c via a bearing d (see the above publications).
In the figure, f is an input or output shaft through which the shaft centers of the pair of disks a and b are inserted, and g and g are needle bearings that support the disks a and b with respect to the input or output shaft f.

[0005]

However, in the above-mentioned prior art, since a plurality of loading cams o ..., O ... are arranged in the circumferential direction of each disk a, b, the loading cam is loaded on each disk a, b. There is a difference between the pressing force at the portion that is in pressure contact with the cam o and the pressing force at the portion where there is no pressure contact. Therefore, when the disks a and b are viewed microscopically, the entire shape is wavy in the axial direction. Transforms into. As a result, the contact pressure between each of the disks a and b and the roller becomes non-uniform in the circumferential direction, which causes an increase in operating noise and vibration.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a shaft of a disk for transmitting power to and from a plurality of loading cams even if the plurality of loading cams are provided as described above. The purpose is to prevent the deformation in the direction and to ensure a uniform contact pressure between the disc and the roller.

[0007]

In order to achieve the above object, a concrete solving means of the invention according to claim 1 is to provide an input disk, an output disk and a roller arranged between the both disks. A toroidal type continuously variable transmission unit having
A power transmission gear arranged in the vicinity of the input or output disc of the continuously variable transmission unit, and arranged between the power transmission gear and the input or output disc in the vicinity thereof, and the input or output disc and the power transmission gear. A toroidal-type continuously variable transmission including a loading cam for transmitting power between and. Then, a cam plate having a cam surface with which the loading cam engages is arranged between the input or output disc and the loading cam, and the cam plate is arranged in the radial direction to the input or output disc. And is configured to transmit power to the input or output disk.

Further, a concrete solution of the invention described in claim 2 is to specify the toroidal continuously variable transmission of the invention described in claim 1 and to provide two sets of toroidal type continuously variable transmission units, each of which The input or output discs of the speed change unit are arranged such that their rear faces are opposed to each other, and a pair of loading cams are disposed between the rear faces of a pair of input or output discs whose rear faces are opposed to each other. To do.

[0009]

With the above construction, in the invention according to claim 1,
For example, when a power transmission gear for power input is arranged near the input disc, the power of the power transmission gear is transmitted from the plurality of loading cams to the cam plate. At this time, since the pressing force of the cam plate is different between the portion that is in pressure contact with each loading cam and the portion that is not in pressure contact with each other, the cam plate is deformed into a wavy shape in the axial direction. Therefore, the power transmission between the cam plate and the input disk is favorably performed without being affected by the deformation of the cam plate. As a result, the contact pressure between the input disc and the roller is evenly secured in the circumferential direction, and the operating noise and vibration are effectively reduced.

Further, according to the second aspect of the invention, for example, the pressing force between the pair of input disks and the respective loading cams corresponding thereto acts as the two disks are separated from each other. The reaction force of the pressing force acts in the direction in which both discs are attracted, and the action directions of the reaction forces are 18
Since both reaction forces interfere with each other by 0 ° and there is no escape place for this reaction force, the wavy deformation in the axial direction of each cam plate appears largely on the disc side by that amount, but in the present invention, as described above,
By transmitting power in the radial direction via the cam plate, wavy deformation of the disc is reliably prevented, so that the contact pressure between the disc and the roller is evenly secured, and the operating noise and vibration are effectively reduced. .

[0011]

As described above, according to the toroidal type continuously variable transmission of the first aspect of the invention, the cam plate is arranged between the input or output disc and the loading cam, and the cam plate and the disc are arranged. Since the power transmission between the disc and the radial direction is performed, the wavy deformation of the disc is reliably prevented regardless of the wavy deformation of the cam plate in the axial direction, and the contact pressure between the disc and the roller is made uniform. Therefore, it is possible to reduce operating noise and vibration.

According to the second aspect of the invention, when a pair of loading cams are arranged between a pair of input or output discs whose rear surfaces are opposed to each other, the wavy deformation of the cam plate is large. Although it appears, it is possible to eliminate the influence of wavy deformation on the power transmission between the cam plate and the disc, to make the contact pressure between the disc and the roller uniform, and to reduce the operating noise and vibration. it can.

[0013]

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

1 and 2 show a toroidal type continuously variable transmission according to the present invention, wherein 1 is an output shaft, 2 is a first toroidal type continuously variable transmission unit arranged on the output shaft 1, 3 Is a second toroidal type continuously variable transmission unit arranged on the right side of FIG. 1 of the first transmission unit.

The first toroidal type continuously variable transmission unit 2 has an input disk 5 rotatably inserted through an output shaft 1.
And an output disc 6 arranged to face the input disc 5 on the left side of FIG. 1, and the output disc 6 is spline-coupled to the output shaft 1. A toroidal surface 5 formed between the disks 5 and 6 is formed between the disks 5 and 6.
A power roller 7 is arranged so as to be in contact with and straddle a and 6a.

Similarly, the second toroidal type continuously variable transmission unit 3 includes an input disk 9 similar to the above, an output disk 10 arranged on the right side of the input disk 9 in FIG. 10 toroidal surfaces 9a, 10a and a power roller 11 that is in contact with the surface. The back surface of the input disk 9 is arranged so as to face the back surface of the input disk 5 of the first continuously variable transmission unit 2. An intermediate disk 15 is arranged in a space formed between the rear surfaces of the pair of input disks 5, 9 and between the intermediate disk 15 and both input disks 5, 9, respectively.
The loading cams 16, 16 ... Are arranged. A power transmission gear 18, which is a helical gear for transmitting power to the pair of input disks 5 and 9, is integrally formed on the outer periphery of the intermediate disk 15, and the power transmission gear 18 is connected to an engine power from an input shaft (not shown). Is transmitted. Therefore, the engine power is basically transmitted from the power transmission gear 18 and the intermediate disc 15 to the output discs 6 and 10 through the loading cam 16 ..., the input discs 5 and 9 and the power rollers 7 and 11 and then output. It is transmitted to the shaft 1.

Each of the toroidal type continuously variable transmission units 2,
The power rollers 7 and 11 of 3 are respectively eccentric shafts 20 and 2
A pair of trunnions 21, 2 arranged in the vertical direction through 0
1 is rotatably attached. Each trunnion 21
A shaft member 22 arranged in the vertical direction is fixedly arranged at the lower end of the shaft member 22, and the trunnion 21 is displaced in the vertical direction by displacing the shaft member 22 in the vertical direction, so that the power rollers 7 and 11 are separated from each other. The power rollers 7 and 11 are tilted to change contact points at which the power rollers 7 and 11 contact the input / output disks 5, 6, 9 and 10 to change the gear ratio steplessly. The upper end of each trunnion 21 is supported by a support member 27 attached to a transmission casing 25 by a link post 26 so as to allow the rotation of each trunnion 21 around its axis when the power rollers 7, 11 are tilted. While being rotatably supported in the axial direction by 28, the lower end is rotatably supported by a spherical bearing 33 by a support member 32 attached to the partition wall 30 by a link post 31.

As shown in FIG. 2, the lower end portion of the shaft member 22 is supported by a bearing 41 in a recess 40 in the upper and lower housings 37 and 38 arranged below the partition wall 30 so as to be rotatable and vertically movable. And the shaft member 22
A hydraulic cylinder 45 for vertically moving the shaft member 22 is connected to a substantially central position of the. The hydraulic cylinder 45
With the casing 47 fixedly attached to the transmission casing 25 with the bolts 46 and the inwardly projecting portion 47a formed on the casing 47 sandwiched vertically, the center core portion is fitted into the shaft member 22. And a fixed piston 48. The piston 48 and the protruding portion 4 of the casing 47
A pair of hydraulic chambers 49, 50 are formed vertically by 7a, and the shaft member 22 is provided by supplying hydraulic pressure to the upper hydraulic chamber 49.
2 is moved upward in FIG. 2, while the shaft member 22 is moved downward in FIG. 2 by supplying hydraulic pressure to the lower hydraulic chamber 50.

The upper and lower housings 37, 3
A gear shift control device 60 controls the supply of hydraulic oil to the hydraulic chambers 49 and 50 of the hydraulic cylinders 45 to shift gears.
Are placed. That is, the upper housing 37 has a supply oil passage 61 to which a hydraulic pressure is supplied from a hydraulic pressure source (not shown), and the hydraulic chambers 49, 50 of the hydraulic cylinders 45.
A first oil passage 62 and a second oil passage 63 that communicate with each other are formed. A hydraulic control valve 65 is arranged in the lower housing 38. The valve 65 is
An outer wall of a hollow portion formed by horizontally drilling a central portion of the lower housing 38 serves as a valve body 66.
A sleeve 67 slidably disposed in the sleeve, and the sleeve 6
7, and a spool 68 slidably arranged in the inside of the unit 7. The sleeve 67 includes first to third ports 67 corresponding to the supply oil passage 61 and the first and second oil passages 62 and 63.
a to 67c are formed, and in accordance with the movement of the sleeve 67, the oil in the oil supply passage 61 is transferred from the first port 67a to the first oil passage 62 via the spool 68 and the second port 67b, or to the spool 68 and the third port 67c. It is configured to communicate with the second oil passage 63 via.

In the vicinity of the left end of FIG. 2 of the sleeve 67,
A pin member 70 is connected to the pin member 70, and a rotary shaft 72a of a stepping motor 72 attached to a vertical wall portion of an oil pan 79 arranged at a lower portion of the transmission casing 25 via a drive member 71 arranged in a sleeve 67. The sleeve 67 is connected and slides the sleeve 67 in the left-right direction in FIG. 2 according to the rotation of the motor 72.

Further, at the right end of FIG. 2 of the spool 68,
A feedback mechanism 80 that feeds back the tilting of the power roller 11 is arranged. The feedback mechanism 8
0 is a first recess cam 81 fixedly arranged on the shaft member 22 of the trunnion 21 of the second continuously variable transmission unit 3 and a first end whose end engages with an inclined surface 81a formed on the recess cam 81.
An arm 82, a rotation shaft 83 on which the first arm 82 is rotatably supported, and a second arm rotatably supported on the rotation 83 and engaged with the right end of the spool 68 of the hydraulic control valve 65 in FIG. 84 and a compression coil spring 85 compressed between the left side of the spool 68 in FIG. 2 and the pin member 70, and the shaft member 22 is moved by the oil supply to the hydraulic cylinder 45 according to the movement of the sleeve 67. When the power roller 11 is tilted by moving in the vertical direction, the first and second arms 82, 84 of the feedback mechanism 80 are rotated clockwise or counterclockwise in accordance with the vertical movement of the shaft member 22 to rotate the spool. By moving the sleeve 68 in the same direction as the sleeve 67, the oil supply passage 61 and the first oil passage communicating with the oil supply passage 61 are connected.
Alternatively, the communication with the second oil passages 62 and 63 is cut off, and the oil supply to the hydraulic cylinder 45 is stopped when the tilted position of the power roller 11 reaches the target position.

Next, as a feature of the present invention, the structure around a pair of input disks 5 and 9 whose back surfaces are opposed to each other will be described in detail with reference to an enlarged view of FIG. In FIG. 3, the intermediate disc 15 integrally formed with the power transmission gear 18 has a cam surface 15b having a plurality of cam grooves (not shown) formed on the side surface facing the loading cams 16, 16. A hollow disk-shaped cam plate 8 is provided between each loading cam 16 and 16 and the pair of input disks 5 and 9.
7, 87 are arranged. Each cam plate 87 has a cam surface 87a having a plurality of cam grooves (not shown) formed on the side surface facing the corresponding loading cam 16. These two cam grooves are formed in such a shape that when the intermediate disk 15 and each cam plate 87 rotate relative to each other, the larger the relative displacement amount, the greater the pressing force that presses each loading cam cam 16 ... On the cam plate 87. It

On the back surface of the input disks 5 and 9, claws 5b and 9 extending axially between the disks 5 and 9 are provided.
b is formed, and the inner peripheral edges of the cam plates 87, 87 are splined to the base end portions of the claw portions 5b, 9b. By this spline connection, the cam plates 87, 8 are formed.
7 and both input disks 5 and 9 are linked in the radial direction, and are relatively movable in the axial direction.

Claws 5b, 9 of the input disks 5, 9
Step portions 5c and 9c are formed on the outer peripheral side of b,
The inner peripheral edges of the corresponding cam plates 87, 87 are the input discs 5,
When contacting the step portions 5c, 9c of the cam 9, the cam plate 87,
A gap is formed between the side surface of 87 and the back surface of the corresponding input disk 5, 9. Further, a pressurizing member 88 composed of a disc spring is arranged on each of the step portions 5c and 9c, and urges the corresponding cam plate 87 toward the intermediate disc 15 side.

The intermediate disk 15 disposed between the pair of input disks 5 and 9 has an inner peripheral edge of each of the input disks 5 and 9.
9 is extended in the axial direction so as to enter the inside of the shaft 9, and the extended portions 15a are rotatably directly supported on the output shaft 1 by bearings 90, 90 arranged at two positions in the axial direction.

Further, in the pair of input disks 5 and 9, the outer peripheral side of the extended portion 15a of the power transmission gear 15 is extended to the side between both input disks 5 and 9 as described above, and the tip of the extended portion is clawed. The parts 5b and 9b are integrally formed, and the intermediate disk 15 is provided with the following parts as shown in FIGS.
A through hole 15b is formed in the circumferential direction at the height position of the claw portion 5b, and the claw portion 5b of the one input disk 5 is inserted into the through hole 15b and projects. The circumferential length of the through hole 15b of the intermediate disk 15 is formed longer than the phase range in which the intermediate disk 15 and the input disks 5 and 9 rotate relative to each other. On the other hand, the claw portion 9b of the other input disk 9
Is a claw portion 5 of one of the input discs 5, as shown in FIG.
It is formed in a shape having an engaging groove 9c that engages with the left and right of the tip of b, and when both input disks 5 and 9 rotate,
Due to the engagement of the claw portions 5b and 9b, both input disks 5 and
9 is configured to rotate synchronously.

In the pair of input disks 5 and 9, a tip end portion is a bearing 96 on the output shaft 1, and a rear end inner circumferential extension portion is a bearing 97.
Are rotatably supported by the extending portions 15a of the intermediate disk 15.

Therefore, in the above embodiment, when the input torque is transmitted to the power transmission gear 18 and the intermediate disk 15 rotates during power transmission, the loading cams 16 ... Cam surface 15
Since the loading cams 16 ... Are engaged with the cam plates 87, 87 on the b, 87a, the cam plates 87, 8 are engaged.
7 is pressed against the corresponding input disks 5 and 9 by the pressing force from each loading cam 16 ... While rotating. At this time, when the pressing force from the loading cam 16 overcomes the urging force of the pressurizing member 88, the cam plates 87, 87 move to the corresponding input disks 5, 9 side, and the cam plates 87, 87 are moved. The inner peripheral edge of 87 abuts on the stepped portions 5c and 9c of the input disks 5 and 9. After that, when the pressing force further increases, the cam plates 87, 87 undergo a wavy deformation in the axial direction due to the pressing of the loading cams 16 at a plurality of points.
Due to the gap between the rear surfaces of the input disks 5 and 9 corresponding to the axial length of c and 9c, the rear surfaces of the input disks 5 and 9 are not contacted.

The rotation of the cam plates 87, 87 is
By the spline connection with the corresponding input discs 5, 9, it is transmitted from the radial direction to each of the input discs 5, 9, so that the axial deformation of each of the cam plates 87, 87 causes the power to be applied to each of the input discs 5, 9. Power transmission is performed well without affecting transmission. As a result, the contact pressure between the input disks 5 and 9 and the power rollers 7 and 11 becomes uniform, and the operating noise and vibration are effectively reduced.

Moreover, the reaction force against the pressing force of each loading cam 16 ... Is directed toward the intermediate disk 15 side between the first and second toroidal type continuously variable transmission units 2 and 3, so that the escape area is lost. The rigidity of the intermediate disk 15 side becomes high, and the axial deformation of the cam plates 87, 87 strongly appears on the input disk 5, 9 side. The power transmission to the cam plates 87, 87 is performed well without being affected by the axial deformation of the cam plates 87, 87. Therefore, even if the rear surfaces of the pair of input disks 5, 9 are arranged opposite to each other. The contact pressure between the input disks 5 and 9 and the power rollers 7 and 11 can be made uniform to effectively reduce operating noise and vibration.

In the above embodiment, the invention is applied to the toroidal type continuously variable transmission in which the pair of discs whose rear surfaces are opposed to each other are the input discs 5 and 9, but the present invention is not limited to this. The invention described in claim 1 can be applied to a device provided with only one set of toroidal type continuously variable transmission units, and the invention described in claim 2 is required to have two sets of toroidal type continuously variable transmission units. However, it goes without saying that the invention may be applied to a case in which the rear surfaces of the pair of output disks are arranged opposite to each other and the loading cam is arranged between the output disks.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a toroidal type continuously variable transmission as viewed from the side.

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

FIG. 3 is an enlarged view of a main part of FIG.

FIG. 4 is a front view of an intermediate disc.

FIG. 5 is a cross-sectional view showing details of the structure around the through hole of the intermediate disk.

FIG. 6 is a cross-sectional view around a pair of input disks showing a conventional example.

[Explanation of symbols]

 2,3 Toroidal type continuously variable transmission unit 5,9 Input disc 6,10 Output disc 7,11 Power roller (roller) 15 Intermediate disc 16 Loading cam 18 Power transmission gear 87 Cam plate 87a Cam surface

Front page continuation (72) Inventor Hidenao Taketomi 3-1, Shinchi, Fuchu-cho, Aki-gun, Hiroshima Mazda Motor Corporation

Claims (2)

[Claims] 1. A toroidal type continuously variable transmission unit having an input disc, an output disc, and a roller arranged between the both discs, and a power arranged near the input or output disc of the continuously variable transmission unit. A toroidal type no-load device having a transmission gear and a loading cam arranged between the power transmission gear and the input or output disc in the vicinity thereof and transmitting power between the input or output disc and the power transmission gear In the stepped transmission, a cam plate having a cam surface with which the loading cam engages is disposed between the input or output disc and the loading cam, and the cam plate is arranged in the radial direction. In a toroidal type continuously variable transmission, characterized in that the power is transmitted to the input or output disk in cooperation with the input or output disk. Speed machine. 2. A set of two toroidal type continuously variable transmission units, wherein the rear surfaces of the input or output disks of each continuously variable transmission unit are arranged to face each other, and the pair of rear surfaces are arranged to face each other. 2. The toroidal type continuously variable transmission according to claim 1, further comprising a pair of loading cams arranged between the rear surfaces of the output discs.