JPH06147282A - Toroidal type continuously variable transmission - Google Patents

Abstract

PURPOSE:To suppress or prevent the occurrence of the fall of a pair of input or output discs arranged in a state that the backs thereof are positioned facing each other. CONSTITUTION:The backs of a pair of input discs 5 and 9 are arranged facing each other. A loading cam 16 and an intermediate disc 15 with the outer periphery of which a power transmission gear 18 for input is formed integrally are respectively arranged between a pair of the input discs 5 and 9. Cylindrical parts 5b and 9b extended toward a space between the two discs are formed to the input disc 5 and 9, respectively, and the cylindrical parts 5b and 9b are overlapped in a fitted-in state with each other. The power transmission gear 18 is supported to the outer periphery of the upper cylindrical part 9b through an intermediate disc 15. Thus, a pair of input discs 5 and 9 can be considered to be one rigid body on the whole. Since one rigid body is supported with a long distance between bearings by means of bearings 97 and 98 arranged to the discs 5 and 9, the fall of the input discs 5 and 9 is effectively suppressed or prevented from occurring.

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 preventing an input disk or an output disk from falling.

[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.

Both of the above publications are provided with two sets of toroidal type continuously variable transmission units.
The rear surfaces of the two input disks are arranged to face each other, and the power transmission gear for power input is arranged between the two input disks. In the latter publication, the rear surfaces of the two output disks are arranged to face each other. And a power transmission gear for taking out power is arranged between the both output disks.

By the way, in the above-mentioned conventional toroidal type continuously variable transmission, as shown in FIG. 6, a phase difference does not occur between both rotations of a pair of disks a and b whose rear surfaces are opposed to each other. , A hollow cylindrical tube c is disposed between the disks a and b, and the tube c and the disks a and b are spline-coupled to each other to restrict relative rotation between the disks a and b, and The disks a and b are allowed to move relative to each other in the axial direction, so that the disks a and b and the rollers (not shown) sliding on the toroidal surfaces a1 and b1 of the disks can be strongly pressure-contacted to each other. A power transmission gear e is supported on the outer periphery of c via a bearing d (see the above publications). In the figure, f is both disks a and b.
Is an input or output shaft through which the shaft center is 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, each of the disks a and b has a power transmission gear e.
Although a force is exerted from them at the time of power transmission with the rollers and the rollers, since there is only one bearing g supporting the disks a and b, input or output is applied to the disks a and b. There is a drawback that "tilt" that is inclined with respect to the axis of the axis f is likely to occur.

The present invention has been made in view of the above problems, and an object thereof is to provide two sets of continuously variable transmission units as described above, and to arrange the back surfaces of a pair of input or output disks facing each other. The object is to effectively suppress or prevent the tilt of the pair of input or output disks.

[0007]

In order to achieve the above object, the present invention employs a structure in which a pair of discs suppress the tilt of each other.

That is, the concrete means for solving the problems of the first aspect of the present invention comprises two sets of toroidal type continuously variable transmission units each having an input disc, an output disc, and a roller arranged between the discs. , For a toroidal type continuously variable transmission in which the rear surfaces of the input or output disks of each of the continuously variable transmission units are opposed to each other, between a pair of input or output disks in which the rear surfaces are opposed to each other. In addition, it is assumed that a power transmission gear for input or output for transmitting power between the pair of disks is arranged. Then, a cylindrical portion is formed on each of the pair of discs so as to extend in the axial direction between the pair of discs and to support the power transmission gear in a state of being overlapped with each other.

Further, in the invention described in claim 2, when the structure of the invention described in claim 2 is provided and the pair of disks is supported by the input or output shaft, the pair of disks is rotated. Roller bearings are used to support the bearings freely.

[0010]

With the above construction, in the invention according to claim 1,
Since the tubular portions formed on the pair of discs are superposed on each other in the axial direction, the pair of discs can be regarded as one rigid body as a whole, and therefore the pair of discs can be regarded as one disc. The bearing that supports the disk and the bearing that supports the other disk are in a state equivalent to being supported at a long interval, and the collapse of each disk is effectively suppressed or prevented.

Moreover, since the cylindrical portion of each disc prevents the disc from collapsing, as compared with the case where each disc is supported by two bearings which are separated by a predetermined distance in order to prevent the disc from collapsing by itself. Each disk can be supported by one bearing, the number of required bearings can be limited to two, and an increase in rotational resistance due to the bearing can be prevented.

Further, by ensuring the synchronous rotation of both discs by the overlapping portions of the cylindrical portions formed on each disc, the tube c as in the conventional case can be eliminated, so that the bearing of each disk is compared with the conventional one. They can be arranged closer to the inter-disk side, and the degree of freedom in the arrangement position of the bearing is increased. Therefore, in the conventional example of FIG. 6, the bearings g, g are arranged at the disk a,
The toroidal surfaces a1 and b2 are restricted to the tip position of b.
Although the bearings g, g were constituted by needle bearings due to the restriction by the position of the above, in the invention of claim 2, the bearing of each disc is arranged on the side between both discs and the bearing is rotated more than the needle bearing. Since the roller bearing has a low resistance, the rotational resistance of each disk is effectively reduced, and the power transmission efficiency is increased. In this case, 1
Since a pair of discs as rigid bodies are supported by the bearings of the discs as described above, even if the bearings of the discs are arranged on the side between the discs, the bearing spacing is 2 for each disc as in the conventional case. It is secured longer than when it is supported by individual bearings, and the suppression or prevention of the disc fall is sufficiently secured.

[0013]

As described above, according to the toroidal type continuously variable transmission of the first aspect of the present invention, the cylindrical portions formed on the back surfaces of the pair of input or output disks are superposed on each other. By using a pair of discs as one rigid body, it is possible to effectively suppress or prevent the respective discs from collapsing, and it is possible to limit the number of required bearings to two and reduce the number of bearings.

According to the second aspect of the invention, since the bearings that respectively support the pair of disks are formed by roller bearings, the rigidity of the pair of disks can be ensured at a high level.
It is possible to reduce the rotational resistance of each disk and improve the efficiency of power transmission.

[0015]

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, in which 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 continuously variable transmission unit 2 includes an input disk 5 rotatably inserted in the output shaft 1 and an output disk 6 arranged to face the input disk 5 on the left side of FIG. The output disc 6 is splined to the output shaft 1. A power roller 7 is disposed between the disks 5 and 6 and is in contact with the toroidal surfaces 5a and 6a formed by the disks 5 and 6, respectively.

Similarly, the second continuously variable transmission unit 3 includes an input disk 9 similar to that described above and the input disk 9 shown in FIG.
An output disk 10 arranged on the right side and a power roller 11 that contacts the toroidal surfaces 9a and 10a of the both disks 9 and 10 are provided. The input disc 9 has a back surface which is the input disc 5 of the first continuously variable transmission unit 2.
It is located opposite the back of the. An intermediate disk 15 is arranged in the space formed between the rear surfaces of the pair of input disks 5 and 9. A plurality of cam grooves (not shown) are formed on the side surfaces of the intermediate disk 15 and the input disks 5 and 9 which face each other, and loading cams 16, 16 ... Are arranged in the cam grooves. Set up. 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. Each cam groove has a larger relative displacement when the intermediate disc 15 and the input discs 5, 9 rotate relative to each other.
Is formed in a shape that increases the pressing force for pressing the input disk 5 or 9 toward the input disk. Therefore, engine power is transmitted from the intermediate disc 15 to the output discs 6 and 10 through the cams 16 ..., the input discs 5 and 9, and the power rollers 7 and 11 in sequence, and then to the output shaft 1.

Each of the above toroidal continuously variable transmission units 2 and 3
The power rollers 7 and 11 of the eccentric shafts 20 and 20 are
Pair of trunnions 21 and 21 arranged vertically through
It is rotatably attached to. A shaft member 22 arranged in the vertical direction is fixedly arranged at the lower end of each trunnion 21, and the trunnion 21 is displaced in the vertical direction by displacing the shaft member 22 in the vertical direction, so that each power roller 7 and 11 are tilted so that each power roller 7, 11 causes each input and output disk 5, 6, 9, 10 to move.
The gear ratio is changed steplessly by changing the contact point that comes into contact with. The upper end of each trunnion 21 has an upper end portion to allow the rotation of each trunnion 21 around the axis due to the tilting of the power rollers 7 and 11.
5 is rotatably supported in the axial direction by a spherical bearing 28 by a supporting member 27 attached by a link post 26, and the lower end portion is supported by a supporting member 32 attached by a link post 31 on a partition wall 30 by a spherical bearing 33. It is rotatably supported.

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 and 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 rollers 7 and 11 is arranged. The feedback mechanism 80 includes a recess cam 81 fixedly arranged on the shaft member 22 of the trunnion 21 of the second continuously variable transmission unit 3, a first arm 82 whose tip engages with an inclined surface 81a formed on the recess cam 81, A rotating shaft 83 having a first arm 82 rotatably supported, a second arm 84 rotatably supported by the rotation 83 and engaging with the right end of the spool 68 of the hydraulic control valve 65 in FIG. 68
2 of FIG. 2 and a compression coil spring 85 that is compressed between the pin member 70, and the shaft member 22 moves in the vertical direction by the oil supply to the hydraulic cylinder 45 in accordance with the movement of the sleeve 67. When the power rollers 7 and 11 tilt,
As the first and second arms 82, 84 of the feedback mechanism 80 rotate clockwise or counterclockwise in accordance with the vertical movement of the shaft member 22, the spool 68 moves in the same direction as the sleeve 67. The communication between the supply oil passage 61 and the first or second oil passages 62, 63 communicating with the supply oil passage 61 is cut off,
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, a 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 first and second
Each of the input disks 5 and 9 of the continuously variable transmission units 2 and 3 has a cylindrical portion 5 extending in the axial direction between the disks.
b and 9b are integrally formed. The inner diameter of the tubular portion 5b of the input disc 5 of the first continuously variable transmission unit 2 is smaller than the inner diameter of the tubular portion 9b of the other input disc 9 so that the other input disc 9 has the same inner diameter. The inner portion of the intermediate disc 15 is axially enlarged outside the tubular portion 9b of the outer input disc 9 while being fitted and overlapped inside the tubular portion 9b. It is supported by bearings 90, 90 so as to be relatively rotatable.

Cylindrical portions 5a, 9a of both the disks 5, 9
A plurality of keys 92 embedded in the cylindrical portions 5a and 9a are arranged in the space between them in a circumferential direction so that the disks 5 and 9 are synchronously rotated. Further, the intermediate disk 15 and the power transmission gear 18 for input outside thereof are
The left and right parts in the figure are divided into two parts, a left part and a right part, and a disc spring 93 for pressurizing these parts is provided between the left part and the right part to urge these parts toward the input disks 5 and 9, respectively. The loading cam 16 is arranged even when transmitting a small torque.
Is configured to generate a pressing force for pressing the input disks 5 and 9 against. Further, a plurality of pins 95 are embedded in the circumferential direction between the left side portion and the right side portion of the intermediate disk 15 so that the rotation of the left side portion and the right side portion are synchronized to perform phase matching. I am configuring.

Bearings 97, 98 for rotatably supporting the input disks 5, 9 are arranged between the input disks 5, 9 and the output shaft 1. Each bearing 9
7 and 98 are arranged at axial positions near the back surfaces of the corresponding input disks 5 and 9, that is, at positions of thick portions in the radial direction of the respective input disks 5 and 9, and roller bearings having low rotation resistance. It is composed of.

Therefore, in the above embodiment, the cylindrical portions 5 of both input disks 5 and 9 whose rear surfaces are opposed to each other are provided.
Both input disks 5, 9 can be seen as one rigid body, since b, 9b are superposed with each other fitted together, so that one rigid body consisting of both disks 5, 9 is Since the bearings 97 and 98 for supporting the disks 5 and 9 are supported at a relatively long distance in the axial direction, it is possible to effectively prevent the input disks 5 and 9 from eccentrically tilting with respect to the output shaft 1. Can be prevented.

In addition, when suppressing or preventing the above-mentioned tilting of the input disks 5 and 9, the number of bearings arranged on each of the input disks 5 and 9 is one for each input disk 5 and 9, and there are a total of two bearings. Since the bearings 97 and 98 are used, the number of bearings can be reduced and the rotational resistance of the input discs can be increased by the bearings as compared with the case where the tilting of the input discs 5 and 9 is suppressed by a plurality of bearings for each disc. It can be effectively suppressed and power transmission efficiency can be improved.

Further, since the synchronous rotation between the pair of input disks 5 and 9 is secured by the key 92 arranged between the cylindrical portions 5a and 9a, the conventional tube c shown in FIG. 6 becomes unnecessary. . Therefore, the bearings 97, 9 of each disk 5, 9
8 can be arranged between both disks 5 and 9 as compared with the prior art, that is, in a thick portion where the distance from the shaft center to the toroidal surfaces 5a and 9a is long, the input disks 5 and 9 corresponding to the toroidal surfaces 5a and 9a can be arranged. Even if there are restrictions on the placement position of
The bearings 97 and 98 of the respective input disks 5 and 9 can both be constituted by roller bearings while ensuring good rigidity of the respective input disks 5 and 9. As a result, the bearing 97,
The rotation resistance of each disk 5, 9 is reduced as compared with the case where 98 is constituted by a conventional needle bearing, so that power transmission can be performed efficiently. In this case, since the two input disks 5 and 9 as one rigid body are supported by the bearings 97 and 98 of the disks 5 and 9 as described above, the arrangement positions of these two bearings 97 and 98 are both input. Even if the bearings are arranged closer to the side between the disks 5 and 9 and the distance between both bearings is narrowed, the bearing spacing is secured wider than when each input disk 5 and 9 is individually supported by two bearings. Disks 5, 9
The fall of the can is sufficiently suppressed or prevented.

FIG. 4 shows a bearing 9 for supporting the disks 5 and 9.
7 and 98 show modified examples of the arrangement positions of the above-mentioned embodiments, in which the bearings 97 and 98 are arranged on the respective disks 5 and 9 in the above embodiment, but two bearings are arranged on one of the input disks 5. is there. That is, in the present modification, the tubular portion 5b 'of the input disk 5 of the first continuously variable transmission unit 2 is connected to the second portion of the other.
Of the continuously variable transmission unit 3 is extended to the front end side from the back surface of the input disk 9 and the other input disk 9 is formed by the tubular portion 5b '.
The bearings 97 'and 98' for supporting the input disks 5 and 9 are arranged on the cylindrical portion 5b 'in a state of supporting the input disks 5 and 9.

Therefore, according to this modification, the input disk 5 on the side supported by the two bearings 97 'and 98' is securely prevented from falling down, so that the other input disk 9 supported by the input disk 5 is prevented. It is possible to reliably prevent the falling of both discs, and to eliminate the falling of both discs 5 and 9.

FIG. 5 shows another modification. Instead of dividing the intermediate disk 15 and the power transmission gear 18 for input into two parts in the above-mentioned embodiments and modifications, the power transmission gear 1 is used.
No. 8 is not divided into two, and the intermediate disk 15 has a circumferential portion facing the loading cam 16 as a separate body, and a disc spring 93 for pressurizing is provided between the main body and the main body in a splined state. It is a thing.

In the above embodiment, the cylindrical portions 5b and 9b provided on the pair of input disks 5 and 9 are formed integrally with the input disks 5 and 9, but they may be formed separately and fixedly connected. Good. Further, although the present invention is applied to a toroidal type continuously variable transmission in which the pair of discs whose rear faces are opposed to each other are the input discs 5 and 9, the present invention is not limited to this, and the rear faces of the output discs are opposed to each other. Needless to say, the present invention may be applied to a configuration in which a loading cam and an intermediate disc are arranged between the output discs and a power transmission gear for taking out an output is arranged on the intermediate disc.

[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 diagram showing a modified example of an arrangement position of a bearing that supports an input disk.

FIG. 5 is a diagram showing another modification.

FIG. 6 is an enlarged sectional view around a pair of disks showing a conventional example.

[Explanation of symbols]

 1 output shaft 2,3 toroidal type continuously variable transmission unit 5,9 input disc 5b, 9b tubular portion 6,10 output disc 7,11 power roller (roller) 18 power transmission gear 97,98 bearing (roller bearing)

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 including two input disks, an output disk, and a roller disposed between the two disks, the rear surface of the input or output disk of each continuously variable transmission unit. A toroidal-type continuously variable transmission in which two vehicles are arranged opposite to each other, and power is transmitted between a pair of input or output disks whose rear planes are arranged opposite to each other. A power transmission gear for input or output is arranged, and the pair of discs respectively support the power transmission gear in a state where they extend axially toward the pair of discs and are superposed on each other. A toroidal-type continuously variable transmission characterized in that a tubular portion is formed. 2. The toroidal according to claim 1, wherein the pair of disks are supported by an input or output shaft, and the bearing rotatably supporting the pair of disks by the input or output shaft is a roller bearing. Type continuously variable transmission.