JPH01206150A - Toroidal continuously variable transmission - Google Patents

Abstract

PURPOSE:To ensure a space for housing other accessory parts in a casing by supporting a second shaft at the torque delivering portion thereof on a casing side and providing the end of the second shaft on this supporting portion. CONSTITUTION:As torque is transmitted from an input shaft 12 to an input disk 22, a loading cam 30 is operated and a pressing force corresponding to the input torque is applied to the input disk 22 as well as to an input disk 22a via the shaft 12 increasing the pressure contact force of friction members 26, 26a, to prevent the occurrence of slip in each friction members 26, 26a at the time of increasing the input torque. The torque inputted into output disks 24, 24a is collected to a driving gear 44, from which the torque is outputted to a counter shaft (second shaft) 50 via an output gear 48. Since the shaft 50 has a length about half the length of the shaft 12 with its end portion being supported by an intermediate shaft 18, a wide space S can be provided in a casing 14 on a toroidal speed change mechanism 20 side devoid of the shortened shaft 50.

Description

Detailed Description of the Invention Field of the Invention The present invention relates to a toroidal continuously variable transmission, and more particularly to a toroidal continuously variable transmission in which two sets of toroidal transmission mechanisms that perform a substantial continuously variable transmission function are coaxially provided. Regarding machines.

Conventional technology A toroidal continuously variable transmission includes a toroidal transmission mechanism consisting of a pair of input and output disks whose opposing surfaces are formed into toroidal curved surfaces, and a friction separator rotatably disposed between the input and output disks. The rotation input to the input disk is transmitted to the output disk via the M:4 sesame.
The data is output from the output disk.

At this time, the transmission ratio is changed steplessly according to the amount of inclination of the friction separator.

Furthermore, in order to prevent slippage between the friction piece and the input and output disks, a biasing means applies preload to apply a pressure contact force, and the pressure contact force is increased in proportion to the magnitude of the input torque. Generally, a disc spring is used as the biasing means for preloading, and a loading cam is used as the pressing force increasing means.

However, even though the pressing force, that is, the frictional force, is increased in accordance with the input torque, if an attempt is made to transmit an excessive amount of torque with one set of toroidal transmission mechanisms, the diameter of the toroidal transmission mechanism will become abnormally large. , it is necessary to increase the size of the continuously variable transmission in the radial direction.

Sokote, MACHI NE-DES I GN-Ap
r i 1-18゜1974, P2S5, 5AE (
Society of Automotive En
Gineers, Inc.) PAPER, 751180
, Fig. 7 (Printed in U, S, A), etc., two sets of toroidal transmission mechanisms are provided on the same axis, and the input torque is shared between the two sets of toroidal transmission mechanisms, and each toroidal transmission mechanism is This allows the transmission mechanism to be made smaller in diameter, that is, the continuously variable transmission to be made smaller in the radial direction, which is significantly advantageous when mounted on a vehicle.

Problems to be Solved by the Invention However, such conventional toroidal continuously variable transmissions have the following problems:
Two sets of toroidal transmission mechanisms are provided on the output side shaft, both ends of the output side shaft are supported by a pair of support walls protruding from the casing of the transmission, and the input side shaft is mounted parallel to the output side shaft. is provided, and torque is transmitted from the input side shaft to the input disk of each toroidal transmission mechanism.

However, the input-side shaft shares the support wall that supports the output-side shaft on the casing side, and the input-side shaft is supported by the support wall.

For this reason, the input side shaft is formed to have substantially the same length as the output side shaft, and these two input and output side shafts are arranged within the casing.

Therefore, when an attempt is made to place a control valve or other supplementary part in the casing, the two shafts mentioned above become an obstacle and the supplementary part cannot be accommodated in the casing, causing the supplementary part to protrude from the casing and resulting in an increase in the size of the transmission. There was a problem that they would come.

Therefore, the present invention has been developed by cutting out and shortening the unnecessary portion of the shaft on the side where the toroidal transmission mechanism is not installed, out of the two shafts arranged inside the casing, so that other auxiliary parts can be installed inside the casing. The purpose of the present invention is to provide a toroidal continuously variable transmission that can secure a space for storing.

Means for solving the neck point In order to achieve the above object, the present invention provides a pair of input and output disks whose opposing surfaces are formed into toroidal curved surfaces, and a rotatable arrangement between the input and output disks. Two sets of toroidal transmission mechanisms made of friction sesame are provided on the first shaft, and input disks or output disks of the two sets of toroidal transmission mechanisms are arranged adjacent to each other, and the first
Place a second axis for input or output parallel to the axis, and
In a toroidal continuously variable transmission in which torque is transferred between the shaft and the adjacent input disk and the output disk and the same dirt floor, the second shaft is supported on the casing side at the torque transfer portion, The second shaft is configured by arranging an end of the second shaft on the support portion.

Effect With the above-described structure, the toroidal continuously variable transmission of the present invention is provided with the 21iIII on the side where the toroidal transmission mechanism is not provided.
However, since the two sets of toroidal transmission mechanisms are supported on the casing side with the torque transfer portion between the input disks and the output disks installed next to each other as the ends, the length of the two shafts is the same as that of the first shaft. The length can be approximately half that of the original length.

Therefore, inside the casing, the effective space in the part where the second shaft is shortened with respect to the first shaft becomes larger, and it becomes possible to store other supplementary parts in this space part.

Example Hereinafter, embodiments of the present invention will be described in detail based on the drawings.

That is, FIGS. 1 and 2 show a toroidal continuously variable transmission 10 showing an embodiment of the present invention, and reference numeral 12 indicates a torque converter (not shown) provided on the left side of FIG. The input shaft 12 serves as a first input shaft, and is rotatably supported with respect to the casing 14 so as to be able to move slightly in the axial direction.

The input shaft 12 includes the casing 14
A first toroidal transmission mechanism 20 and a second toroidal transmission mechanism 20 are sandwiched between an intermediate wall 18 fixed by bolts 16 to
a are arranged coaxially.

Above 1st. The second toroidal transmission mechanisms 20 , 20 & are arranged to face each other and the first manual discs 22 . The first output disk 24, the second manual disk 22a, the second output disk 24a, and each of these input disks 22°2
2 &, and a first friction sesame 26 and a second friction sesame 26 & disposed between each output disk 24, 241.

The opposing surfaces of the input disks 22 , 22 a and the output disks 24 , 24 & are each formed into a toroidal curved surface, and the friction sesame 26 , 2 is formed on the input disks 22 , 22 & and the output disks 24 , 24 &.
6 & is in contact with the friction sesame 26, 26
& is possible, and the friction sesame 26, 26
By tilting and rotating (tilting) &, substantially continuously variable speed is performed.

In the first toroidal transmission mechanism 20, a first manual disk 22 and a first output disk 24 are each rotatably fitted to the input shaft 12 via a bearing or the like.

The first output disk 24 of the first human-powered disk 22
A cam flange 28 is disposed on the opposite side of the input shaft 12 and is spline-fitted to the input shaft 12 and rotated together with the input shaft 12, and the torque of the input shaft 12 is transmitted from the cam flange 28 through a loading cam 30 serving as a suppressing means. The information is input to the one-manpower disk 22.

The loading cam 30 is actuated by the relative rotation of the first manual disk 22 and the cam flange 28, and the input disk 22. It has a function of increasing the distance between the cam flanges 28 according to the torque.

Therefore, when the two are rotated relative to each other as torque is transmitted from the cam flange 28 to the first human-powered disk 22,
The loading cam 30 operates to press the first human-powered disk 22 toward the first output disk 24, increasing the pressure contact force with the first friction separator 26.

At this time, the cam flange 28 is attached to the snap ring 32.
The loading cam 3 is prevented from moving in the axial direction with respect to the input shaft 12 via a nut 34.
The pressing reaction force due to 0 is generated by the cam flange 28° input shaft 12 and the loading wheel (described later) 38. It also acts on the second manual disk 22 & through the disc spring 40.

On the other hand, in the second toroidal transmission mechanism 20B, the second manual disk 22 & is fitted to the input shaft 12 through a linear motion bearing 36 so as to be movable in the axial direction and locked in the rotational direction. 12
The torque of the second
The information is input to the human power disk 22a.

The second human-powered disk 22 & the second output disk 24
A loading nut blade whose tightening amount can be adjusted is provided on the opposite side from &, and a disc spring 40 as a suppressing means is provided between the loading nut 38 and the second manual disk 22 &. It will be done.

The biasing force of the disc spring 40 is adjusted by the amount of tightening of the loading spring 38, and the biasing force is adjusted by the amount of the loading spring 38.
While preloading L in the direction of the second output disk 24a,
This preload reaction force is applied to the loading nut 38.

Input shaft 12. It also acts on the first human power disk 22 via the cam flange and the loading cam 30.

The second output disk 24 a is rotatably fitted to the input shaft 12 via a bearing, and the second output disk 24 & and the first output disk 24 are adjacent to each other with the intermediate wall 18 in between. It is set up.

A cylindrical portion 42 is integrally formed on the inner peripheral portion of the first output disk 24 and extends in the direction of the second output disk 24 a through the intermediate wall 18 . A drive gear 44 is spline fitted to the drive gear 44, and the second output disk 24a is fitted to the outer periphery of the boss portion of the drive gear 44.
is fitted via the key 46.

Therefore, the above 1. Second output disk 24, 24a
The drive gear 44 and the drive gear 44 are coupled together in the rotational direction via a spline portion and a key 46, respectively.

Note that the drive gear 44 is meshed with an output gear 48, and the first. The rotation of the second output disks 24 , 24 & is caused by the drive gear 44 . It is transmitted via the output gear 48 to a countershaft 50 as a second shaft.

By the way, the above 1. Second friction sesame 26, 26! L
are provided in pairs in the direction perpendicular to the plane of the paper in FIG.
The outer circumferential surface of L is the first person mentioned above, as shown in FIG.

The output disks 22 and 24 and the second input and output disks 22 & 24a are shaped to follow the respective toroidal surfaces.

Above 1st. 2nd day rubbed sesame seeds 26.・26 & is the first. Second
It is tiltably supported by the support machine 4m152,528,
These first. The second support mechanism 52a has substantially the same configuration, and the configuration of the second support mechanism 52a is shown in detail in FIG. Alphapella is attached to the reference numeral of each constituent member of the corresponding first support mechanism. (The suffix "ILI" is added to the reference numeral of each constituent member recognized by the first support mechanism.) The explanation will be omitted and redundant explanations will be omitted.

That is, FIG. 2 is a sectional view taken along the line ■-n in FIG.
an eccentric shaft 54a as a tilting shaft on which is rotatably supported; a top support member 56a to which the eccentric shaft 54& is rotatably attached; and the top support member 56a f.
Hydraulic actuator 58jL that moves in the plane angle direction of a
and are provided in pairs in the left and right direction with the input shaft 12 in between in FIG.

In the eccentric shaft 54&, the support portion of the friction top 26a and the attachment portion to the top support member 56jL are eccentric to each other, and the eccentric directions of the left and right eccentric shafts 26& are set to be opposite to each other.

The upper and lower ends of the top support member 56& are spherical bearings 60&
, 62a to be rotatably and tiltably supported by upper and lower links 64a and 66a.

The hydraulic actuator 58& is a cylinder 68a.

It consists of a piston 70a and a piston rod 21L, and the piston rod 72a is connected to the top support member 56a.

The hydraulic actuator 58a has the left and right pistons in the respective operating directions, and the left and right pistons move in response to the control hydraulic pressure output from the control valve B in order to obtain a desired gear ratio. The direction in which the door 2& is moved is an upside down direction.

Therefore, the pair of left and right hydraulic actuators 58JL
When operated, the left and right top support members 56a are moved in the upside down direction while the upper and lower links 64a and 66L are tilted.

Then, the second friction piece 26& sandwiched between the input and output disks 22a, 24a is tilted in the direction perpendicular to the plane of the paper in FIG. .

The function of the second support machine*52a described above is the function of the above-mentioned 7iX1.
Similar to the support mechanism 52, when a hydraulic actuator (not shown) of the first support mechanism is operated, the first friction piece 26 moves up and down between the piece support members shown in FIG. is tilted.

In addition, the above @1. The second support mechanism area, 52&, is the first degree second support mechanism area.
Input disk 2 of toroidal transmission mechanism 20, 20a
2, 22 & and the output disks 24, 24a are respectively reversed in the left-right direction in the $1 figure, so the first support mechanism 52a and the second support mechanism 52a correspond to each other. They are operated in opposite directions.

By the way, the above 1. The middle part of the upper link 64, 64 & lower link group, s6a, and sole of the second support mechanism 52.52a serves as a support member via the upper link bosses h 74 , 74a and the lower link bosses 76 , 76g. No casing side members 78, 78a, 80, 8
0a respectively, and the first.
The inclination center of the second friction sesame 26 , 26 & is determined.

Sokuchi, each of the above link posts 74.74jL, 76,
76 & is the casing side member 78.78L, 8
0.80a through bolts 82 (see FIG. 1), and support members 84a, formed on the upper links 64, 64jL and the lower links 66, 66a,
86 and 86a correspond to the respective link posts 74 and 7
4 & , 76 , 76 & , and their positions are regulated.

In addition, the upper link posts 74, 74 & are upper support holes.

84a input shaft 12 (formed as a square post closely axially inward, and lower link boss)
76.76a is formed as a master post that is brought into spherical contact with the inner periphery of the support hole 86.86B.

On the other hand, the casing side members 7B, 78a, 8
0 and 80a are respectively integrally protruded from the intermediate wall 18, and the eleventh and second support mechanisms 52, 52a are ultimately supported by the intermediate wall 18.

Therefore, the above 1. The relative position between the second support mechanisms 52.52a, that is, the first. The relative position between the tilting centers of the tilting axes of the second friction pieces 26 and 26B is restricted to one foot with respect to the intermediate wall 18.

On the other hand, the outer periphery of the cylindrical portion 42 of the first output disk 24,
A pair of first . 2nd angular ball bearing 88°88JL
is inserted, and the first. The second angular ball bearing 88.88JL connects the first output disk 24 and the second
The relative position of the output disk 24a with respect to the intermediate wall 18 is regulated to be constant.

That is, the above 1. 2nd angular ball bearing 88
．． 88jL are arranged facing each other in the axial direction, and the respective outer races 90, 90& are connected to the through hole 18a from the first output disk 24 and second output disk 24a side.
The inner races 94 and 918 are brought into contact with both sides of the annular spacer.

Further, shims 98, 98a are provided on the end faces of the inner races 94, 94a opposite to the annular spacer □□□, and the shims 98, 98 & provide a gap between the inner race leg and the first output disk 24. Also, the gap between the inner race 94a- and the second output disk 24a can be finely adjusted.

FIG. 3 is a schematic configuration diagram showing the entire toroidal continuously variable transmission 10, and FIG. The engine rotation output from the second output disk 24.24a to the countershaft 50 via the torque transfer portion of the drive gear 44 and output gear 48 is transmitted to the first gear 100. Idler gear 102 and the first
Forward clutch 106 via drive gear 104
The forward rotation or Output as backward rotation.

By the way, the necessary parts of the counter shaft are connected from the output gear 48 to the first gear 100 and the second gear.
This is the length up to the attachment part of the gear 108, and in this embodiment, the length of the countershaft 50 is set to approximately half the length of the input shaft 12, leaving the necessary length.

Then, the output gear 48 of the countershaft (capital)
The side end portion is rotatably supported by the intermediate wall 18 via a bearing 116 fitted to the outer periphery of the boss portion of the output gear 48 .

In addition, the other end of the countershaft is the casing 1
It is supported by the end wall (not shown) of 4.

With the above configuration, the toroidal continuously variable transmission 10 of this embodiment
If the engine stops and the input shaft 1
2, the preload by the disc spring 40 is applied to the first. It acts on the second manual disks 22 and 22a, and the 111th
1 ground sesame 26, and the second input and output disk 22a,
The second friction sesame 26& is sandwiched between the two pieces 24a with a pressing force corresponding to the preload.

Then, as the engine operates, the input shaft 12
When torque is input to cam flange 2, this torque is applied to cam flange 2.
8. The first human powered disc 2 via the loading cam 30
2 and to the second human power disk 22a via the linear motion bearing 36, respectively, so that these first .
The second human-powered disks 22 , 22 & are rotated, and this input rotation is transmitted to the first disks 22 , 22 & through the eleventh and second friction separators 26 , 26 &. The signal is transmitted to the second output disk 24.degree. 24a.

At this time, the above 1. A gear ratio corresponding to the tilt angle of the second friction pieces 26, 26a is generated steplessly between the input and output disks.

In addition, from the input shaft 12 to the first human power disc 22
When torque is transmitted, the loading cam 30 is activated, and a pressing force corresponding to the input torque is applied to the first human-powered disc 22.
is applied to the second manual disk 22a via the input shaft 12, and is also applied to the first manual disk 22a. The pressing force of the second friction pieces 26 1 , 26 2 & is increased, and slippage of the respective friction pieces 26 1 , 26 2 & is prevented when the input torque increases.

And the above 1. Second output disk 24, 24!
The torque input to L is collected in the drive gear 44, and is output from the drive gear 44 to the countershaft 50 via the output gear 48.

By the way, the countershaft 50 has approximately half the length of the input shaft 12, and its end is connected to the intermediate wall 1.
8, the casing 14 on the first toroidal transmission mechanism 20 side where the countershaft 50 is shortened.
Inside, a large space S is provided in the axially extending portion of the countershaft 50.

Therefore, in this embodiment, the casing 1 is placed in the space S.
4 is depressed, the control pulp n is housed in the depressed part 14a, and the outer opening of the depressed part 14a is closed with a cover 14b having a shape that is smoothly continuous from the general outer part of the casing 14. Ru.

For this reason, the control valve n, which was conventionally attached so as to protrude outward from the general outer part of the casing 14, can be housed inward from the general outer part of the casing 14 in this embodiment, and the speed change a! 10 can be made more compact.

In this embodiment, since the control valve B is located at the lower part of the first toroidal transmission mechanism 200 in the drawing, the pair of hydraulic actuators (not shown) provided in the first support mechanism & is located inside the control pulp n. It has been incorporated.

On the other hand, the second toroidal transmission mechanism 20a supporting the second toroidal transmission mechanism 20a
A pair of hydraulic actuators 58 & provided in the support mechanism 52JL are connected to each other as shown in FIG.
They are placed on both sides of 50.

FIG. 4 is a schematic groove bottom diagram showing another embodiment, in which the same components as those in the above embodiment are given the same reference numerals and redundant explanations will be omitted.

That is, the toroidal continuously variable transmission 10a of this embodiment is as follows:
Two sets of first shafts are connected to the output shaft 120 as the first shaft. The second toroidal transmission mechanisms 20, 20& are arranged, and the respective input disks 22, 22& are disposed adjacent to each other.

The engine rotation input from the input shaft 122 is transmitted to the idler shaft 128 as a second shaft via the gears 124 and 126, and from the idler shaft 128 via the gears 130 and 132 to the input disks 22 and 22. transmitted to a.

The engine rotations input to the input disks 22 and 228 are the first. Second toroidal transmission 1320
．． 20 & continuously variable speed rice output shaft 12
0 and is output via the forward/reverse switching means 134.

Therefore, in this embodiment, a necessary portion of the idler shaft 128 as the second shaft is on the first toroidal transmission mechanism 20 side, and the idler shaft 128 is connected to the gear 124 of the input shaft 122 and the input disks 22, 22.
8 and the gear 132.

It goes without saying that both ends of the idler shaft 128 are supported by the casing.

Therefore, in this embodiment, as in the above embodiment, a wide space S is provided in the shaft extension portion of the idler shaft 128 on the second toroidal transmission mechanism 20a side.
A control valve B can also be housed within the space S.

Therefore, this embodiment can also be made compact in the same way as the above embodiment.

As described in detail of the invention, the toroidal continuously variable transmission dW of the present invention has a first shaft on which two sets of toroidal transmission mechanisms are provided, and input disks adjacent to each other with the same dirt floor or output disks with the same dirt floor. Of the second shafts where torque transfer is performed between the two shafts, the second shaft on the side where the toroidal transmission mechanism is not provided is supported on the casing side with the torque transfer portion as the end. The length can be made approximately half of the length of the first shaft, and a large effective space can be secured within the casing at the portion where the second shaft is shortened.

Therefore, it is possible to store auxiliary parts such as control valves in the above-mentioned effective space, and it is possible to prevent the auxiliary parts from protruding from the outside of the casing, thereby making it possible to downsize the transmission. be effective.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional view of essential parts showing one embodiment of the present invention, Fig. 2 is a cross-sectional view corresponding to the line ■-■ in Fig. 1, Fig. 3 is a general outline +W of the present invention, and Fig. 4 is FIG. 3 is an overall schematic diagram showing another embodiment of the present invention. 1.0, 1. Oa...Toroidal continuously variable transmission, 12
...Input shaft (first shaft), 14...Casing, 18...Intermediate wall, 20, 20a...
Toroidal transmission mechanism, 22, 22a... Input disk, 24, 241... Output disk, 26° 26 &
...jJ ground sesame, 50...counter shaft (2nd m), 73...control pulp, 120...
Output shaft (first shaft), 128... idler shaft (second shaft). 2 people outside

Claims (1)

[Claims] (1) Two sets of toroidal transmission mechanisms are provided on the first shaft, each consisting of a pair of input and output disks whose opposing surfaces are formed into toroidal curved surfaces, and a friction separator rotatably arranged between these input and output disks. , the input disks or the output disks of the two sets of toroidal transmission mechanisms are arranged adjacent to each other, and a second shaft for input or output is arranged parallel to the first shaft, and the second shaft is arranged parallel to the first shaft. In a toroidal continuously variable transmission in which torque is transferred between the shaft and the adjacent input disks on the same earth floor or between the output disks, the second shaft is supported on the casing side at the torque transfer portion, A toroidal continuously variable transmission characterized in that an end of the second shaft is disposed in the support portion.