JPH0814351A - Toroidal type continuously variable transmission - Google Patents

Abstract

(57) [Abstract] [Purpose] Despite the dimensional and shape errors of component parts,
The inner side surfaces of both the input side and output side disks and the peripheral surfaces 8a, 8a of all the power rollers 8, 8 are brought into uniform contact. By preventing the first and second yokes 49, 50 from being displaced in the axial direction of the support shaft 51 and the support pin 52 at the moment when the gear ratio exceeds 1, the speed change operation is facilitated. [Structure] Trunnions 6, 6 supporting a power roller 8
Is supported by both the first and second yokes 49, 50, and the first,
The second both yokes 49, 50 are pivotally supported on the frame 39a.
The second yokes 50, 50 are supported by the support pins 52, 52 so as to be displaceable in the direction perpendicular to the support pins 52, 52. The first and second yokes 49, 50 are prevented from being displaced in the axial direction of the support shaft 51 and the support pin 52.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The toroidal type continuously variable transmission according to the present invention is used, for example, as a transmission for automobiles or as a transmission for various industrial machines.

[0002]

2. Description of the Related Art The use of a toroidal type continuously variable transmission as schematically shown in FIGS. 8 to 9 has been studied as a transmission for an automobile. This toroidal type continuously variable transmission supports an input side disk 2 concentrically with the input shaft 1 as disclosed in, for example, Japanese Utility Model Laid-Open No. 62-71465, and the input shaft 1
At the end of the output shaft 3 arranged concentrically with the output side disk 4
Is fixed. Inside the casing in which the toroidal type continuously variable transmission is housed, there are provided trunnions 6 and 6 which swing around a pivot shaft 5 and 5 which are twisted with respect to the input shaft 1 and the output shaft 3. .

The trunnions 6, 6 are provided with the pivots 5, 5 on the outer surfaces of both ends. Further, the base ends of the displacement shafts 7, 7 are supported by the central portions of the trunnions 6, 6, and the trunnions 6, 6 are swung about the pivot shafts 5, 5, so that the displacement shafts 7, The inclination angle of 7 can be freely adjusted. Power rollers 8, 8 are rotatably supported around displacement shafts 7, 7 supported by the trunnions 6, 6, respectively. The power rollers 8, 8 are sandwiched between the input side and output side disks 2, 4. The inner surfaces 2a, 4a of the input-side and output-side disks 2, 4 facing each other are circular arcs whose cross sections are centered on the pivot 5, and the whole is a concave surface obtained by rotating the circular arcs. Then, the peripheral surfaces 8a and 8a of the power rollers 8 and 8 formed in the spherical convex surface are connected to the inner side surfaces 2a and 4a, respectively.
It is in contact with a.

A loading cam type pressing device 9 is provided between the input shaft 1 and the input side disk 2, and the pressing device 9 causes the input side disk 2 to face the output side disk 4 and elastically moves. Pressing. This pressing device 9
Is a cam plate 10 that rotates together with the input shaft 1, and a retainer 11.
A plurality of (for example, four) rollers 12 held by
It is composed of 12 and. On one side surface (right side surface of FIGS. 8 to 9) of the cam plate 10, a cam surface 13 which is an uneven surface extending in the circumferential direction is formed, and an outer side surface of the input side disk 2 (left side of FIGS. 8 to 9). The same cam surface 14 is also formed on the surface). Then, the plurality of rollers 12, 12 are rotatably supported about a shaft in the radial direction with respect to the center of the input shaft 1.

When the toroidal type continuously variable transmission configured as described above is used, when the cam plate 10 rotates with the rotation of the input shaft 1, the cam surface 13 causes the plurality of rollers 12, 1 to rotate.
2 is pressed against the cam surface 14 on the outer surface of the input side disk 2. As a result, the input side disk 2 is pressed by the plurality of power rollers 8, 8 and at the same time, based on the meshing between the pair of cam surfaces 13, 14 and the plurality of rollers 12, 12. The input side disk 2 rotates. And
The rotation of the input side disk 2 is transmitted to the output side disk 4 through the plurality of power rollers 8 and the output shaft 3 fixed to the output side disk 4 rotates.

When the rotational speeds of the input shaft 1 and the output shaft 3 are changed and when deceleration is first performed between the input shaft 1 and the output shaft 3, the trunnions 6, 6 centering on the pivot shafts 5, 5 are used.
Is rocked as shown in FIG. Then, as shown in the figure, the peripheral surfaces 8a, 8a of the power rollers 8, 8 are arranged on the inner side surface 2a of the input side disk 2 and the output side disk 4 near the center.
The displacement shafts 7, 7 are tilted so as to contact the inner surface 4a and the outer peripheral portion thereof, respectively.

On the contrary, when increasing the speed, the trunnions 6, 6 are swung as shown in FIG. Then, as shown in the figure, the peripheral surfaces 8a, 8a of the respective power rollers 8, 8 are provided on the inner surface 2a of the input side disk 2 near the outer periphery and the inner surface 4a of the output side disk 4 near the center. The displacement shafts 7, 7 are tilted so that they come into contact with each other. If the inclination angles of the displacement shafts 7, 7 are set in the middle between FIG. 8 and FIG. 9,
An intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.

Further, FIGS. 10 to 11 show Japanese Patent Application No. Sho 63-69.
1 shows a more specific toroidal type continuously variable transmission described in a microfilm of No. 293 (Actual Kaihei No. 1-173552). The input disk 2 which is the first disk and the output disk 4 which is the second disk are
It is rotatably supported around a cylindrical input shaft 15, which is a rotating shaft, via needle bearings 16 and 16, respectively. The cam plate 10 is spline-engaged with the outer peripheral surface of the end portion (the left end portion in FIG. 10) of the input shaft 15, and is prevented from moving in the direction away from the input side disk 2 by the collar portion 17. Then, the cam plate 10 and the rollers 12, 12
Thus, the loading cam type pressing device 9 is configured to rotate the input side disk 2 while pressing the input side disk 2 toward the output side disk 4 based on the rotation of the input shaft 15. An output gear 18 is connected to the output side disk 4 by keys 19 and 19 so that the output side disk 4 and the output gear 18 rotate in synchronization with each other.

Both ends of the pair of trunnions 6 and 6 are oscillated and axially (front and back direction in FIG. 10, left and right direction in FIG. 11) on a pair of support plates 20 and 20, which are support members, respectively.
It is supported to be freely displaceable. Then, in the circular holes 23, 23 formed in the intermediate portions of the trunnions 6, 6,
The displacement shafts 7, 7 are supported. The displacement shafts 7, 7 are parallel to each other and eccentric to the support shaft portions 21, 21 and the pivot shaft portion 2.
2 and 22, respectively. Each of the support shafts 21, 21 is rotatably supported inside the circular holes 23, 23 via radial needle bearings 24, 24. Further, the power rollers 8, 8 are rotatably supported around the respective pivot shaft portions 22, 22 via radial needle bearings 25, 25.

It should be noted that the pair of displacement shafts 7, 7 are provided at equidistant circumferential positions with respect to the input shaft 15 (positions opposite to each other by 180 degrees in the example of FIGS. 10 to 11). In addition, the pivot shaft portions 22, 22 of the displacement shafts 7, 7 are connected to the support shaft portions 2 respectively.
The direction of eccentricity with respect to Nos. 1 and 21 is the same as the rotational direction of the input side and output side disks 2 and 4 (see FIG. 11).
And left and right directions). Further, the eccentric direction is a direction substantially orthogonal to the arrangement direction of the input shaft 15. Therefore, the power rollers 8 and 8 are connected to the input shaft 1.
5 is supported so as to be slightly displaceable in the arrangement direction. As a result, even if the power rollers 8, 8 tend to be displaced in the axial direction of the input shaft 15 due to the shape accuracy and dimensional accuracy of the component parts, an unreasonable force is applied to each component part. This displacement can be absorbed without incident.

Between the outer surface of each of the power rollers 8 and 8 and the inner surface of the intermediate portion of each of the trunnions 6, 6, there are thrust ball bearings 26, in order from the outer surface of the power rollers 8, 8. 26 and thrust needle bearings 27, 27 are provided. The thrust ball bearings 26, 26 support the loads in the thrust direction applied to the power rollers 8, 8 and allow the power rollers 8, 8 to rotate. Such thrust ball bearings 26, 26 have a plurality of balls 29, 29 and balls 29, 2 respectively.
An annular retainer 28, 28 for holding 9 in a rollable manner,
It is composed of an annular outer ring 30, 30. The inner ring raceways of the thrust ball bearings 26, 26 are formed on the outer side surfaces of the power rollers 8, 8 and the outer ring raceways are formed on the inner side surfaces of the outer races 30, 30 respectively.

Further, the thrust needle bearings 27, 27
Is composed of a race 31, a retainer 32, and needles 33, 33. This thrust needle bearing 27, 27
With the races 31 and 31 in contact with the inner side surfaces of the trunnions 6 and 6, the inner side surfaces and the outer ring 3 are
It is sandwiched between the outer surface of 0 and 30. The thrust needle bearings 27, 27 support the thrust load applied to the outer rings 30, 30 from the power rollers 8, 8 while the pivot shafts 22, 22 and the outer rings 30, 30 are in contact with each other. It is allowed to swing around the support shaft portions 21, 21.

Further, drive rods 36, 36 are provided at one end (the left end in FIG. 11) of each trunnion 6, 6 respectively.
And drive pistons 37, 37 are fixedly provided on the outer peripheral surfaces of the intermediate portions of the drive rods 36, 36. The drive pistons 37, 37 are oil-tightly fitted in the drive hydraulic cylinders 38, 38, respectively.

When the toroidal type continuously variable transmission configured as described above is used, the rotation of the input shaft 15 is transmitted to the input side disk 2 via the pressing device 9. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the pair of power rollers 8, 8 and the rotation of the output side disk 4 is taken out from the output gear 18.

When the rotational speed ratio between the input shaft 15 and the output gear 18 is changed, the pair of drive pistons 37,
37 is displaced in opposite directions. As the drive pistons 37, 37 are displaced, the pair of trunnions 6,
6 are displaced in opposite directions, for example, the lower power roller 8 in FIG. 11 is displaced to the right side in FIG. 11, and the upper power roller 8 in FIG. 11 is displaced to the left side in FIG. As a result,
Peripheral surfaces 8a, 8a of these power rollers 8, 8 and inner side surfaces 2a, 4 of the input side disk 2 and the output side disk 4, respectively.
The direction of the tangential force acting on the contact portion with a changes. The trunnions 6, 6 are pivotally supported by the support plates 20, 20 according to the change in the direction of the force.
It swings in directions opposite to each other with 5 as the center. As a result,
As shown in FIGS. 8-9, the power rollers 8,
The abutting positions of the peripheral surfaces 8a, 8a of 8 and the respective inner side surfaces 2a, 4a change, and the rotation speed ratio between the input shaft 15 and the output gear 18 changes.

It has also been conventionally considered to increase the number of power rollers 8 in order to increase the power that can be transmitted by the toroidal type continuously variable transmission. For example, JP-A-3-
Japanese Patent No. 74667 discloses a structure in which three power rollers 8, 8 are provided between an input side disk 2 and an output side disk 4 at equal intervals in the circumferential direction of both the disks 2, 4. Has been described. FIG. 12 shows a toroidal type continuously variable transmission described in this publication. In the case of this toroidal type continuously variable transmission, the intermediate portions of the yokes 40, 40, which are bent at 120 degrees, are respectively supported by the support shafts 72, 72 at three positions at equal intervals in the circumferential direction of the fixed frame 39. It is pivotal. The trunnions 6, 6 are respectively supported between the adjacent yokes 40, 40 so as to be swingable and displaceable in the axial direction.

One end of each drive rod 36, 36 is connected to one end of each trunnion 6, 6, and the other end of each drive rod 36, 36 drives a hydraulic cylinder 38, 38 as a displacement means. It is connected to the pistons 37, 37. Each of these hydraulic cylinders 38, 38 has a control valve 43 provided with a sleeve 41 and a spool 42 which are respectively displaceable in the axial direction (left and right direction in FIG. 12), and a pump 44 as a hydraulic pressure source It leads to the discharge port.

When changing the inclination angle of the power rollers 8, 8 pivotally supported by the displacement shafts 7, 7 to the trunnions 6, 6, respectively, the sleeve 41 is axially moved by the control motor 45 (see FIG. 12). Left and right).
As a result, the pressure oil discharged from the pump 44 is sent to the hydraulic cylinders 38, 38 through hydraulic pipes. As a result, the drive pistons 37, 37 fitted into the respective hydraulic cylinders 38, 38 become
And the output side disk 4 (see FIGS. 8 to 11) is displaced in the same direction as the rotation direction. Also, each drive piston 3
With the displacement of 7, 37, the hydraulic cylinders 38, 38
The hydraulic oil extruded from is returned to the oil sump 46 through the hydraulic pipe including the control valve 43.

On the other hand, the displacement of the drive piston 37 due to the feeding of the pressure oil is transmitted to the spool 42 via the cam 47 and the link 48, and the spool 42 is displaced in the axial direction. As a result, the flow path of the control valve 43 is closed while the drive piston 37 is displaced by a predetermined amount, and the supply and discharge of the pressure oil to the hydraulic cylinders 38, 38 is stopped. Therefore, the amount of displacement of each trunnion 6, 6 in the axial direction, that is, the inclination angle of each power roller 8, 8 is
It only corresponds to the amount of displacement of the sleeve 41 by the motor 45.

[0020]

However, in the case of the conventional toroidal type continuously variable transmission constructed and operated as described above, the dimensional errors of the constituent members are easily accumulated. When the accumulated dimensional error becomes large, each power roller 8,
8 peripheral surfaces 8a, 8a and both input side and output side disks 2, 4
There is a possibility that the contact state with the inner side surfaces 2a, 4a of the above becomes uneven.

That is, these inner side surfaces 2a, 4a (see FIGS.
In the case of the conventional structure shown in FIG. 12 in which three or more power rollers 8, 8 are sandwiched between them, the frame 39
Is fixed to a mounting flange provided inside the housing, the yokes 40 and 40 are pivotally supported on the frame 39, and the trunnions 6 and 6 pivotally supporting the three power rollers 8 and 8 are arranged adjacent to each other. Support between each other. Therefore, these three power rollers 8, 8 are supported by the housing in a substantially independent state. Even if the supporting portion of any one of the power rollers 8 is distorted due to a dimensional error, a shape error, or the like, the supporting portion of the other power roller 8 is not displaced to compensate for the distortion.

For this reason, unless the dimensional accuracy and shape accuracy of each component are increased, the peripheral surface 8 of each of the power rollers 8, 8 must be improved.
There is a possibility that the contact state between the a and 8a and the inner side surfaces 2a and 4a of both the disks 2 and 4 becomes uneven. In such a non-uniform contact state, the disks 2, 4
Power cannot be transmitted sufficiently (when the contact pressure is too low), or the peripheral surfaces 8a, 8a
Also, the inner side surfaces 2a, 4a roll early to reach the fatigue life (when the contact pressure is partially too high), which is not preferable. Further, increasing the dimensional accuracy and the shape accuracy of each component is not preferable because the processing cost of the parts is increased correspondingly and the cost of the toroidal type continuously variable transmission is increased.

Further, in the case of the conventional structure shown in FIG. 12, in addition to the above problem, both the input side and output side disks 2, 4 are provided.
From the inner side surfaces 2a, 4a of the power roller 8 to the peripheral surface 8
There is also a problem that the gear shift operation may not be smoothly performed due to the force applied to a. That is, when the toroidal type continuously variable transmission is used, the peripheral surfaces 8a, 8a of the power rollers 8, 8 are strongly sandwiched between the inner side surfaces 2a, 4a based on the operation of the pressing device 9. . Then, due to the engagement between the peripheral surfaces 8a, 8a and the respective inner side surfaces 2a, 4a, the force in the direction of pushing out the respective power rollers 8, 8 from between the both disks 2, 4 is changed. Acting in the axial direction of the displacement shafts 7, 7.

On the other hand, the direction of each of the displacement shafts 7, 7 changes according to the gear ratio between the input side disk 2 and the output side disk 4. Therefore, each surface 8a, 2a, 4a
The direction of the force applied to each of the power rollers 8 by the engagement of is also changed by the gear ratio. For example, when decelerating between the input side disk 2 and the output side disk 4,
The force is applied in the direction of the arrow in FIG. 13, and the trunnions 6, 6 supporting the power rollers 8, 8 are displaced outward in the diametrical direction of the disks 2, 4 while the input side disk 2 is being displaced.
It tends to be displaced to the side. On the contrary, when the speed is increased between the input side disk 2 and the output side disk 4, the force is applied in the direction of the arrow in FIG. 14, and the trunnions 6 and 6 supporting the power rollers 8 and 8 are moved. , The disks 2 and 4 tend to be displaced toward the output side disk 4 side while being displaced outward in the diametrical direction.

Therefore, when changing the gear ratio between the input side disk 2 and the output side disk 4, the moment when the decelerating state changes to the speed increasing state or the moment when the speed increasing state changes to the decelerating state (input side disk 2 and the output side disk 4 change at a rotational speed ratio exceeding 1), of the forces applied to the trunnions 6 and 6, the rotational axes of the disks 2 and 4 (left and right in FIGS. 13 to 14). The direction of the component force of (direction) changes.

However, in the case of a toroidal type continuously variable transmission having three or more conventional power rollers 8, 8 as shown in FIG. 12, the yoke 4 pivotally supporting both ends of the trunnion 6, 6 is provided.
No particular consideration was given to preventing displacement of 0 and 40. More specifically, the yokes 40, 40 are pivotally supported by the support shafts 72, 72 at the intermediate portions of the yokes 40, 40, respectively.
No consideration was given to positively prevent the displacement in the axial direction (the front-back direction in FIG. 12). Therefore, in the case of the conventional structure shown in FIG. 12, the power rollers 8, 8 and the trunnions 6, 6 are turned on at the moment when the rotation speed ratio between the input side disk 2 and the output side disk 4 changes beyond 1. The supporting yokes 40, 40 may be displaced in the axial direction of the support shafts 72, 72, albeit slightly.

When the yokes 40, 40 are thus displaced,
The positions of the power rollers 8, 8 supported by the yokes 40, 40 via the trunnions 6, 6 also slightly change in the central axis direction of the disks 2, 4. As a result, there is a possibility that the gear ratio between the disks 2 and 4 cannot be adjusted smoothly. The toroidal type continuously variable transmission of the present invention was invented in view of such circumstances.

[0028]

The toroidal type continuously variable transmission according to the present invention includes a housing and a rotary shaft rotatably supported inside the housing, like the above-described conventional toroidal type continuously variable transmission. A cross section having an arcuate concave inner surface, a first disk arranged concentrically with the rotation shaft and rotating together with the rotation shaft, and a cross section having an arc concave inner surface, The second shaft, which is concentric with the rotating shaft and is rotatable relative to the rotating shaft in a state where the inner surface and the inner surface of the first disk face each other, is inserted through the rotating shaft. It is composed of an annular coupling portion having a free center hole and three or more support arms radially protruding from the outer peripheral edge of the coupling portion, and the rotary shaft is inserted through the center hole, and the tip portions of these support arms are formed. By connecting to a part of the housing A frame fixed to the inside of the housing at a position between the first disc and the second disc, and three or more yokes each having an intermediate portion supported by an intermediate portion of each support arm, At both ends of each of these yokes, a circular hole formed in a positional relationship of being twisted with respect to the rotating shaft and a pivot provided at each end of the circular holes of adjacent yokes in the circumferential direction are rotated and axially A trunnion of the same number as the supporting arm, which is swingably supported between the first and second discs and is supported in a slightly displaceable manner in the axial direction of the pivot shaft. Displacement means for displacing each trunnion in the axial direction of the pivot shaft, and a displacement shaft supported in a state of protruding from the inner side surface at a portion of the inner side surface of each trunnion facing the rotation axis, It is an arcuate convex surface Having a surface, and a them said in a state of being rotatably supported around the displacement shafts first, power rollers interposed between the second two discs.

In particular, in the toroidal type continuously variable transmission of the present invention, the three or more yokes include at least one first yoke and at least one second yoke, and the three or more support members are provided. The arm includes the same number of first support arms as the first yoke and the same number of second support arms as the second yoke. A support shaft parallel to the rotation shaft is inserted through an intermediate portion of the first support arm, and a cylindrical portion through which the support shaft is insertable is formed at an intermediate portion of the first yoke. There is. The first yoke is swingably supported by an intermediate portion of the first support arm by inserting the support shaft into the cylindrical portion, and the cylindrical portion is provided at an intermediate portion of the first support arm. The support shaft is supported so that it cannot be displaced in the axial direction. Further, a support pin having a circular arc convex surface at least a portion parallel to the rotary shaft and facing the rotary shaft is inserted through an intermediate portion of the second arm, and the circular arc convex surface is formed on an outer surface of the second yoke. The portion facing to is a circular arc concave surface. The intermediate portion of the second yoke is supported by the intermediate portion of the second support arm in a state where the arc convex surface and the arc concave surface are in contact with each other, so that the displacement of the support pin in the axial direction is impossible. ing.

[0030]

The toroidal type continuously variable transmission of the present invention constructed as described above is based on the same action as that of the above-described conventional toroidal type continuously variable transmission, and is based on the operation between the first disk and the second disk. By transmitting the rotational force with, and changing the inclination angle of the trunnion, the rotational speed ratio of these two disks is changed.

Particularly, in the case of the toroidal type continuously variable transmission of the present invention, the positional relationship of the first yoke with respect to the housing is centrally determined, but the position of the second yoke with respect to the housing is relative to the support shaft and the support pin. Regarding the right angle direction,
It is slightly adjustable. As a result, the dimensional accuracy and shape accuracy of the constituent members are somewhat poor, and the contact state between the peripheral surface of a part of the power roller and the inner side surfaces of both the first and second disks tends to be uneven. However, the second yoke is displaced in the direction perpendicular to the support pin to compensate for this and prevent the contact state from becoming non-uniform.

Further, in the case of the toroidal type continuously variable transmission of the present invention, the first and second yokes cannot displace the support shaft or the support pin in the axial direction with respect to the first and second support arms. The gear ratio between the first and second discs is 1 because it is supported by
Even at the moment when it changes beyond, the first and second yokes are not displaced in the axial direction of the support shaft or the support pin. As a result,
The positional relationship between the first and second disks and the power roller is
There is no slight deviation from the regular position, and the gear ratio can be adjusted smoothly.

[0033]

1 to 5 show an embodiment of the present invention.
The feature of the present invention is that the first yoke 49 is pivotally supported on the frame 39a and the second yokes 50, 50 are adjusted in order to adjust the positional deviation of the power rollers 8, 8 due to the dimensional error and the shape error of each component. The first and second yokes 49, 50 with respect to the frame 39a so that the frame 39a can be freely displaced and the gear ratio can be adjusted smoothly.
In the axial direction of the support shaft 51 and the support pin 52 (front and back directions in FIG. 1, left and right directions in FIGS. 2 and 3). The structure and operation of the other parts are the same as the conventional structure described above. Therefore, the description of the parts equivalent to those of the conventional structure will be omitted or simplified, and the characteristic parts of the present invention will be mainly described below.

An annular coupling portion 53 is provided at the center of the frame 39a. The coupling portion 53 has a central hole 54 through which the input shaft 15 which is a rotary shaft can be inserted. On the outer peripheral edge of the coupling portion 53, the base end portions of one first support arm 55 and two second support arms 56, 56 are continuous. A total of these three first and second support arms 55, 56
Are provided at equal intervals in the circumferential direction (at a pitch of 120 degrees) and project in the radial direction from the outer peripheral edge of the coupling portion 53. The first half portions of the first and second support arms 55 and 56 are formed in a bifurcated shape as shown in FIGS. That is, as shown in FIG. 2, the front half of the first support arm 55 is provided with a pair of parallel first support plate portions 57, 57, and the front half of the second support arm 56 is shown in FIG. As shown, a pair of second support plates 58, 58 parallel to each other are provided.

The first and second support plate portions 57, which are provided in pairs at the front half portions of the support arms 55 and 56, respectively.
The tip portion of 58 is externally fitted to the mounting flange 59. Then, one (right side of FIGS. 2 to 3) of the first and second support plate portions 5
7 and 58 and the tip portion of the bolt 62 inserted through the circular holes 60 and 61 formed in the mounting flange 59, the other (first left side of FIGS. 2-3) the first and second support plate portions 57 and 58. It is screwed into a screw hole 63 formed at the tip of the and further tightened. The mounting flange 59 is provided inside a housing 73 (see FIG. 11) in which the toroidal type continuously variable transmission is housed. Therefore, the frame 39a is fixed to the inside of the housing 73 at three positions of the tips of the first and second support arms 55 and 56.

Further, as shown in FIGS. 1 and 2, the support shafts are provided at the base end portions of the pair of first support plate portions 57, 57 provided on the front half of the first support arm 55. 51 has been passed over. The support shaft 51 is parallel to the input shaft 15. On the other hand, as shown in FIG. 4, the first yoke 49 pivotally supported by the frame 39a by the support shaft 51 is
It has a bent shape bent at 20 degrees. This first yoke 4
A cylindrical portion 64 is formed in the middle portion of 9. The support shaft 51 is inserted inside the cylindrical portion 64.
A bearing 65 is provided between the outer peripheral surface of the support shaft 51 and the inner peripheral surface of the cylindrical portion 64. As the bearing 65, a sliding bearing such as a metal or a rolling bearing such as a needle bearing can be used. In any case, the cylindrical portion 64 is supported by the bearing 65 around the support shaft 51 without any rattling in the radial direction. As a result, the intermediate portion of the first yoke 49 has the first support arm 55.
It is swingably supported in the middle part of the.

Further, the length dimension L of the cylindrical portion 64 (see FIG. 2)
The axial dimension which is the left-right direction) is a dimension as close as possible to the spacing dimension D between the pair of first support plate portions 57, 57. The distance dimension D slightly changes due to elastic deformation of the pair of first support plate portions 57, 57 due to the tightening of the bolt 62. Therefore, the length dimension L
Is the same as the thickness T of the mounting flange 59 as much as possible. As a result of making the length dimension L and the thickness dimension T substantially equal to each other, when the bolts 62 are tightened in a state where the respective parts are assembled as shown in FIG. Lightly abut the inner surfaces of the first support plate portions 57, 57 (when the length L is slightly larger than the thickness T), or (preferably) with both end surfaces of the cylindrical portion 64. Only a very small gap exists between the inner side surfaces of the pair of first support plate portions 57, 57 (when the length dimension L is slightly smaller than the thickness dimension T). As a result, the cylindrical portion 64 becomes the pair of first support plate portions 57, 57.
During this period, the support shaft 51 is supported so as not to be displaced in the axial direction.

Incidentally, when the length L is slightly smaller than the thickness T and also when the length L is slightly larger than the thickness T, the first axis centered on the support shaft 51 is used. The swing of the yoke 49 is not hindered. That is, even when the length dimension L is slightly larger than the thickness dimension T, if the difference (L−T) is small, the pair of first support plate portions 5 is formed.
Due to the elastic deformation of 7 and 57, the contact pressure between the both end surfaces of the cylindrical portion 64 and the inner side surfaces of the pair of first support plate portions 57 and 57 becomes extremely light. Therefore, the swing can be performed to the extent that there is no practical problem.

On the other hand, a pair of second support plates 5 provided on the front half of each of the two second support arms 56, 56.
As shown in FIGS. 1 and 3, the support pins 52 are bridged around the base end portions of the reference numerals 8 and 58. This support pin 52
Is parallel to the input shaft 15. On the other hand, the intermediate portion of the second yokes 50, 50 supported by the frame 39a by the support pins 52 is bent in a V shape as shown in detail in FIG. Is formed. The outer peripheral surface of the support pin 52 is a cylindrical surface, and the entire outer peripheral surface is an arc convex surface. The outer peripheral surface of the support pin 52 and the arcuate concave surface 66 are in contact with each other. As a result, the middle portion of the second yoke 50 is supported by the middle portion of the second support arm 56 so as to be swingable and slightly displaceable in the surface direction of the second yoke 50.

Further, the width dimension W of the intermediate portion of the second yoke 50 is set as close as possible to the spacing dimension D'between the pair of second support plate portions 58, 58. The reason for this is
The length dimension L of the cylindrical portion 64 is defined by the first support plate portion 57,
This is the same as the reason why it is close to the distance dimension D between the 57. Therefore, when the bolts 62 are tightened in a state where the respective parts are assembled as shown in FIG. 3, both side edges of the middle part of the second yoke 50 lightly contact the inner side surfaces of the pair of second support plate parts 58, 58. In contact with each other, or (preferably), there is only a very small gap between the both side edges of the intermediate portion and the inner side surfaces of the pair of second support plate portions 58, 58. As a result, the second yoke 50 has the pair of second support plate portions 58, 58.
During this period, the support pin 52 is supported so as not to be displaced in the axial direction.

As described above, the respective intermediate portions are located at the intermediate portions of the first and second support arms 55 and 56 which form the frame 39a, and the swinging or surface centering around the support shaft 51 and the support pin 52. At both ends of the first and second yokes 49 and 50, which are movably supported in any direction, circular holes 67 and 67 are respectively provided.
Is formed. The centers of the circular holes 67, 67 are in a twisted positional relationship with the input shaft 15. Then, the pivots 5 and 5 projecting from both ends of the trunnions 6 and 6 inside the circular holes 67 and 67 are respectively attached to the centering rings 68 and
It is pivotally supported via 68 and bearings 69, 69. Out of these aligning rings 68, 68, the outer peripheral surfaces are spherical convex surfaces, and are fitted in the respective circular holes 67, 67 so as to be swingable. The bearings 69, 69 are sliding bearings made of metal or the like, or rolling bearings such as needle bearings, and are formed between the inner peripheral surfaces of the centering rings 68, 68 and the outer peripheral surfaces of the pivots 5, 5. It is provided in between. In any case, these bearings 6
Reference numerals 9 and 69 denote the pivot shafts 5 and 5, respectively, and the alignment ring 68,
It is supported so as to be rotatable with respect to 68 and displaceable in the axial direction.

The pivots 5, 5 provided at both ends of one trunnion 6 have first and second yokes 4 adjacent to each other in the circumferential direction.
9, 50, or second yokes 50, 5 adjacent to each other in the circumferential direction
Circular holes 67, which are formed in 0 and are arranged substantially concentrically with each other,
67, the centering rings 68, 68 and bearings 69, 69
Is pivoted through and. As a result of assembling the members in this way, the trunnions 6, 6 swing around and axially around the input shaft 15 by the pivot shafts 5, 5 which are in a twisted positional relationship with respect to the input shaft 15. It is supported so that it can be displaced a little. Even when the centers of the pivots 5 and 5 and the centers of the circular holes 67 and 67 do not coincide (when the centers intersect with each other), the centering rings 68 and 68 are swung. , This discrepancy is compensated.

Further, of the pivots 5 and 5 provided on both end faces of the trunnions 6 and 6, one of the pivots 5 and 5 is provided.
The tip ends of rods 70, 70 are coupled to the outer end surfaces of the rods 70, 70, respectively. The base end portions of the rods 70, 70 can be pushed and pulled by the hydraulic actuators 71, 71 so that the trunnions 6, 6 are connected to the pivot shafts 5, 5, respectively.
Displacing means for displacing in the axial direction. When changing the gear ratio between the input side disc 2 and the output side disc 4, pressure oil is supplied to and discharged from the hydraulic actuators 71, 71 to cause the trunnions 6, 6 to move to the discs 2, 4 respectively. Displace in the same direction with respect to the circumferential direction.

In the toroidal type continuously variable transmission of the present invention constructed as described above, the positional relationship of the first yoke 49 with respect to the housing is determined by the position of the support shaft 51, but the second yoke 50, 50 with respect to the housing. The position is slightly adjustable in the direction perpendicular to the support shaft 51 and the support pin 52 (plane direction in FIG. 1). That is, the second yokes 50, 50 are prevented from being displaced in the direction away from the input shaft 15 by the contact between the arcuate concave surfaces 66, 66 and the outer peripheral surfaces of the support pins 52, 52. However, it is possible to displace the second yokes 50, 50 themselves in the arrangement direction (the surface direction in FIG. 1).

Therefore, the dimensional accuracy or the shape accuracy of each constituent member is somewhat poor, and the peripheral surface 8 of some of the power rollers 8, 8 is formed.
a and 8a and the inner side surface 2 of both the input side and output side disks 2 and 4
Even if the contact state with a and 4a tends to be uneven,
The second yokes 50, 50 have the arc concave surfaces 66, 66.
While making sliding contact between the outer peripheral surface of the support pins 52 and 52,
Displacement in a direction perpendicular to the support shaft 51 and the support pin 52 compensates for this and prevents the contact state from becoming non-uniform. In order to smoothly perform such compensation, it is preferable that the radius of curvature of the arcuate concave surfaces 66, 66 be slightly larger than the radius of curvature of the outer peripheral surface of the support pins 52, 52.

Further, in the case of the toroidal type continuously variable transmission of the present invention, the pair of the first and second support plate portions 57 and 5 are provided.
The first and second yokes 49, 50 are supported by the support shaft 51 or the support pin on the basis of the engagement between the inner surface of 8 and both end surfaces of the cylindrical portion 64 or both side edges of the intermediate portion of the second yoke 50. With respect to 52, the support shaft 51 or the support pin 52 is supported so as not to be displaced in the axial direction. Therefore, even at the moment when the gear ratio between the input side disk 2 and the output side disk 4 changes by more than 1, the first and second yokes 49, 50 move to the support shaft 51 or the support pin 50. Does not displace in the axial direction.

That is, when decelerating between the input side disc 2 and the output side disc 4, the first and second yokes 4 are used.
2 and 3, a leftward force is applied to 9, 50, and the left end face of the cylindrical portion 64 (FIG. 2) and the left end edge of the intermediate portion of the second yoke 50 (FIG. 3) are located on the left side in FIGS. First and second support plate portion 5
It tends to be pressed against the inner surface of 7, 58. On the other hand, when increasing the speed between the input side disk 2 and the output side disk 4, the first and second yokes 49, 50 are used.
2 to 3, a rightward force is applied, and the right end surface of the cylindrical portion 64 and the right end edge of the intermediate portion of the second yoke 50 are the first and second support plate portions 57 and 58 on the right side in FIGS. It tends to be pressed against the inner surface of the. Therefore, at the moment when the gear ratio changes beyond 1, the first yoke 49 and the second yoke 50 including the cylindrical portion 64 are moved in the axial direction of the support shaft 51 and the support pin 52 (the horizontal direction in FIGS. ) Tends to be displaced.

On the other hand, in the case of the toroidal type continuously variable transmission according to the present invention, both end faces of the cylindrical portion 64 and both side edges of the intermediate portion of the second yoke 50 have the pair of first and second supporting members. The inner surfaces of the plate portions 57 and 58 are in contact with each other or face each other with a very small gap therebetween. Therefore, even at the moment when the gear ratio changes beyond 1, the cylindrical portion 64 and the second yoke 50 are also changed.
Has little or no axial displacement. As a result, the positional relationship between the input side disk 2 and the output side disk 4 and the power roller 8 does not deviate slightly from the normal position, and the gear ratio can be adjusted smoothly.

In the illustrated embodiment, three power rollers 8, 8 are provided between the input side disc 2 and the output side disc 4, but four or more power rollers 8 are provided. , 8 can be provided in almost the same manner. For example, when four power rollers 8 and 8 are provided, a total of four first and second support arms 55 and 56 are provided by shifting the phase by 90 degrees in the circumferential direction, and the middle of each support arm 55 and 56 is provided. Each part supports a yoke bent at a right angle.
Further, even if two sets of the first support arm 55 and the first yoke 49 are provided and one set of the second support arm 56 and the second yoke 50 are provided, even if the dimensional accuracy and the shape accuracy are poor, the contact state is to some extent. Can be made uniform. Further, the cylindrical portion 64 may be any one having a cylindrical inner peripheral surface, and it goes without saying that the shape of the outer peripheral surface is not particularly limited.

Further, in the above-described embodiment, the cylindrical portion 64 intermediate the first yoke 49 or the intermediate portion of the second yoke 50 is provided between each pair of the first and second support plate portions 57 and 58. By sandwiching them, these first and second yokes 49, 5
Although 0 was prevented from being displaced in the axial direction of the support shaft 51 or the support pin 52, these first and second yokes 49, 50
The structure for preventing the displacement is not limited to such a structure. For example, as for the first yoke 49, as shown in FIG. 6, the axial direction of the cylindrical portion 64 (the horizontal direction in FIG. 6).
By forming the through hole 74 in the intermediate portion and inserting the intermediate portion of the flat first support arm 55a that constitutes the frame 39b into the through hole 74, the first yoke 49 causes the support shaft 51 to move.
Can be prevented from being displaced in the axial direction. The length dimension of the through hole 74 (dimension in the front-back direction in FIG. 6) is defined by the support shaft 5
Needless to say, it is sufficient to allow the first yoke 49 to swing about 1. Further, in order to prevent the displacement, the width dimension of the through hole 74 (the dimension in the left-right direction in FIG. 6) is made substantially equal to the thickness dimension of the first support arm 55a in the above-described embodiment. Is the same as.

As for the second yoke 50, as shown in FIG. 7, the width direction of the second yoke 50 (the horizontal direction in FIG. 7).
By forming a through hole 75 in the middle portion and inserting the middle portion of the flat second support arm 56a that constitutes the frame 39b into the through hole 75, the second yoke 50 also causes the support pin 5 to move.
It can be prevented from being displaced in the axial direction of 2. The consideration regarding the length dimension and the width dimension of the through hole 75 is the same as in the case of the first yoke 51 (FIG. 6) described above.

Further, in each of the above-described embodiments, the surfaces of the first and second yokes 49, 50 and the first and second support arms 55, 55a, 56, 56a that face each other, if necessary. An appropriate friction reducing member such as a thrust slide bearing or a thrust needle bearing may be provided between the members.

[0053]

The toroidal type continuously variable transmission according to the present invention is constructed and operates as described above. However, the first and second disks and the power can be controlled regardless of the dimensional error and the shape error of each component. Since the contact state with the roller can be made uniform, a toroidal type continuously variable transmission that is inexpensive and has high performance and excellent durability can be obtained. In addition, it is possible to prevent the trunnion supporting the power roller from performing unnecessary or unexpected movement. As a result, it is possible to improve the durability by smoothing the operation of changing the gear ratio and preventing unnecessary force from being applied to the respective constituent members.

[Brief description of drawings]

FIG. 1 is a partially cut front view showing an embodiment of the present invention, in which only a main part is taken out and seen from the same direction as FIG.

FIG. 2 is an enlarged AA sectional view of FIG.

FIG. 3 is an enlarged BB sectional view of the same.

FIG. 4 is a perspective view of a first yoke.

FIG. 5 is a perspective view of a second yoke.

FIG. 6 is a diagram showing a second embodiment of the present invention and corresponding to the lower portion of FIG.

FIG. 7 is a view corresponding to the lower portion of FIG.

FIG. 8 is a side view showing a basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum deceleration.

FIG. 9 is a side view showing the same state at the time of maximum acceleration.

FIG. 10 is a sectional view showing an example of a conventional specific structure.

11 is a cross-sectional view taken along line CC of FIG.

FIG. 12 is a main part front view showing another example of the conventional structure in a partially cut state.

FIG. 13 is a schematic side view showing a force applied to the trunnion during deceleration.

FIG. 14 is a schematic side view showing the force applied to the trunnion when increasing the speed.

[Explanation of symbols]

 1 Input Shaft 2 Input Side Disk (First Disk) 2a Inner Side Surface 3 Output Shaft 4 Output Side Disk (Second Disk) 4a Inner Side Surface 5 Axis 6 Trunnion 7 Displacement Axis 8 Power Roller 8a Circumferential Surface 9 Pressing Device 10 Cam Plate 11 Cage 12 Roller 13, 14 Cam surface 15 Input shaft 16 Needle bearing 17 Collar part 18 Output gear 19 Key 20 Support plate 21 Support shaft part 22 Pivot shaft part 23 Circular hole 24, 25 Radial needle bearing 26 Thrust ball bearing 27 Thrust needle bearing 28 Cage 29 Ball 30 Outer ring 31 Race 32 Cage 33 Needle 36 Drive rod 37 Drive piston 38 Hydraulic cylinder 39, 39a, 39b Frame 40 Yoke 41 Sleeve 42 Spool 43 Control valve 44 Pump 45 Control motor 46 Oil sump 47 cam 48 link 49 First yoke 50 Second yoke 51 Support shaft 52 Support pin 53 Coupling portion 54 Center hole 55, 55a First support arm 56, 56a Second support arm 57 First support plate portion 58 Second support plate portion 59 Mounting flange 60, 61 circular hole 62 bolt 63 screw hole 64 cylindrical portion 65 bearing 66 arc concave surface 67 circular hole 68 aligning ring 69 bearing 70 rod 71 hydraulic actuator 72 support shaft 73 housing 74, 75 through hole

Claims (1)

[Claims] 1. A housing, a rotary shaft rotatably supported inside the housing, and an inner side surface having a concave section with an arcuate cross section. The rotary shaft is arranged concentrically with the rotary shaft and together with the rotary shaft. It has a rotating first disk and an inner side surface whose cross section is an arcuate concave surface, and is concentric with the rotating shaft with the inner side surface and the inner side surface of the first disk facing each other, and this A second disc rotatably arranged relative to the rotary shaft, an annular joint having a central hole through which the rotary shaft can be inserted, and three or more supports radially protruding from the outer peripheral edge of the joint. The housing is formed of an arm, the rotary shaft is inserted through the central hole, and the tips of the supporting arms are coupled to a part of the housing, so that the housing is located between the first disk and the second disk. With a frame fixed inside , Three or more yokes each having an intermediate portion supported by an intermediate portion of each of the support arms, and circular holes formed at both end portions of each of the yokes in a positional relationship of being twisted with respect to the rotation axis, By supporting pivots provided at both ends of the circular holes adjacent to each other in the circumferential direction so as to be rotatable and displaceable in the axial direction, swinging and pivoting between the first and second disks. The same number of trunnions as the supporting arms, which are supported to be slightly displaceable in the axial direction, the displacement means for displacing each of these trunnions in the axial direction of the pivot, and the rotation on the inner surface of each trunnion. A displacement shaft supported in a state of protruding from the inner side surface and a peripheral surface having a convex cross-section in an arc shape in a portion facing the shaft, and being rotatably supported around these displacement shafts. Between the first and second discs In the toroidal type continuously variable transmission having a lifting been power roller,
The three or more yokes include at least one first yoke and at least one second yoke, and the three or more support arms have the same number of first support arms and second yokes as the first yoke. A second support arm is included, and a support shaft parallel to the rotation shaft is inserted through an intermediate portion of the first support arm, and the support shaft is freely inserted through an intermediate portion of the first yoke. A cylindrical portion is formed, and the first yoke is swingably supported by an intermediate portion of the first support arm by inserting the support shaft into the cylindrical portion. An intermediate portion of one support arm is supported so as not to be displaced in the axial direction of the support shaft, and an intermediate portion of the second support arm is
A support pin, which is parallel to the rotation axis and faces at least the rotation axis and has an arcuate convex surface, is inserted, and a portion of the outer surface of the second yoke that faces the arcuate convex surface is an arc concave surface. The intermediate portion of the second yoke is supported by the intermediate portion of the second support arm in such a manner that the arcuate convex surface and the arcuate concave surface are in contact with each other so that the axial displacement of the support pin is impossible. A toroidal-type continuously variable transmission characterized by this.