JP2003269558A - Toroidal type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission capable of effectively and inexpensively preventing the periphery of a thrust lace from riding on a corner of a pocket part of a trunnion in accordance with movement of the thrust lace during the swinging of a power roller. <P>SOLUTION: In this toroidal type continuously variable transmission, a chamfer 60 is formed in the outer peripheral part of a thrust lace 25A provided between a thrust needle bearing 25 and a trunnion 6. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to a toroidal type continuously variable transmission that can be used as a transmission for automobiles and various industrial machines.

[0002]

2. Description of the Related Art As a transmission for an automobile, use of a toroidal type continuously variable transmission as schematically shown in FIGS. 10 and 11 has been partially implemented. This toroidal type continuously variable transmission, as disclosed in, for example, Japanese Utility Model Laid-Open No. 62-71465, supports an input side disk 2, which is a first disk, concentrically with the input shaft 1 and an input shaft 1. An output side disk 4, which is a second disk, is fixed to the end of the output shaft 3 arranged concentrically. Inside the casing containing the toroidal type continuously variable transmission, the input shaft 1 and the output shaft 3 are provided.
On the other hand, trunnions 6 and 6 that swing about the pivots 5 and 5 in the twisted position are provided.

That is, each trunnion 6, 6 is shown in FIG.
And as shown in FIG. 14 described later, a state in which the support plate portion 7 is bent at both end portions in the longitudinal direction (left and right direction of FIGS. 12 and 14) to the inner side surface side of the support plate portion 7 (upper side of FIG. 12). It has a pair of bent wall portions 8 and 8 formed by. Then, the bent wall portions 8 and 8 form a concave pocket portion P in the trunnion 6 for accommodating a power roller 11, which will be described later. Further, pivots 5 are provided concentrically with each other on the outer surface (the surface opposite to the support plate portion 7) of each bent wall portion 8, 8.

A circular hole 10 is formed in the center of the support plate portion 7, and the base end portion of the displacement shaft 9 is supported in the circular hole 10. By swinging each trunnion 6, 6 about each pivot 5, 5, the tilt angle of the displacement shaft 9 supported at the center of each trunnion 6, 6 can be adjusted. A power roller 11 is rotatably supported around the distal end of the displacement shaft 9 protruding from the inner surface of each trunnion 6, 6, and each power roller 11, 11 has an input side and an output side. It is sandwiched between both disks 2 and 4. The base end and the tip of each displacement shaft 9, 9 are eccentric to each other.

The cross sections of the inner side surfaces 2a and 4a of the input side and output side disks 2 and 4 facing each other are concave surfaces obtained by rotating an arc centered on the pivot 5 or a curve close to such an arc. Is done. Then, the peripheral surface 1 of each power roller 11, 11 formed into a spherical convex surface
1a and 11a are in contact with the respective inner side surfaces 2a and 4a.

Between the input shaft 1 and the input side disk 2,
A loading cam type pressing device 12 is provided.
The pressing device 12 elastically presses the input side disk 2 toward the output side disk 4. Also, the pressing device 1
2 is a cam plate 13 that rotates together with the input shaft 1;
A plurality of (for example, four) rollers 15 held by 4,
It is composed of 15 and. Also, one side surface of the cam plate 13
A cam surface 16 that is an uneven surface is formed in the circumferential direction (on the left side surface of FIGS. 10 and 11), and similarly on the outside surface of the input side disk 2 (the right side surface of FIGS. 10 and 11). Cam surface 17 is formed. And a plurality of rollers 15,
15 is supported so as to be rotatable about an axis extending in the radial direction with respect to the input shaft 1.

In the toroidal type continuously variable transmission having such a structure, when the input shaft 1 is rotated, the cam plate 13 is rotated along with the rotation, and the cam surface 16 causes the plurality of rollers 15, 15 to move. It is pressed by the cam surface 17 provided 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 11, 11 and at the same time, the pair of cam surfaces 16, 17 and the plurality of rollers 15,
The input side disk 2 rotates based on the pressing force against the rolling surface of 15. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the power rollers 11 and 11, 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 performed between the input shaft 1 and the output shaft 3, each trunnion 6, with the pivot shafts 5, 5 as the center.
6 is rocked, and the peripheral surface 11 of each power roller 11, 11 is moved.
a and 11a are input side disks 2 as shown in FIG.
The displacement shafts 9 and 9 are tilted so that the displacement shafts 9 and 9 come into contact with the central portion of the inner side surface 2a and the outer peripheral portion of the inner side surface 4a of the output disk 4, respectively.

On the other hand, when increasing the speed, the trunnions 6 and 6 are swung so that the peripheral surfaces 11a and 11a of the power rollers 11 and 11 of the input side disk 2 are, as shown in FIG. The outer surface of the inner side surface 2a and the output side disk 4
The displacement shafts 9 and 9 are tilted so as to abut on the inner side surface 4a near the center. By setting the inclination angles of the displacement shafts 9 and 9 to be intermediate between those in FIGS. 10 and 11, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.

Further, FIG. 13 and FIG.
1 shows a more specific toroidal type continuously variable transmission described in the microfilm of No. -69293 (No. 1-173552 of Utility Model). The input side disk 2 and the output side disk 4 are respectively provided around the input shaft 18 having a circular tubular shape,
It is supported rotatably and axially displaceable via needle bearings 19, 19. Further, the cam plate 13 for constituting the loading cam type pressing device 12 is spline-engaged with the outer peripheral surface of the end portion (the left end portion in FIG. 13) of the input shaft 18, and is connected to the input side disk 2 by the collar portion 20. Movement away is prevented. An output gear 21 is connected to the output side disk 4 by keys 22 and 22, so that the output side disk 4 and the output gear 21 rotate in synchronization with each other.

Both ends of the pair of trunnions 6 and 6 having the structure shown in FIG. 12 are swingable and axially movable with respect to the pair of support plates 23 and 23 (see FIG. 13).
It is supported so as to be displaceable in the front and back directions, and the left and right direction in FIG. Then, in the circular hole 10 formed in the central portion of the support plate portion 7 constituting each trunnion 6, 6, the base end portion 9a and the tip end portion 9b are parallel to each other and the base end portion of the displacement shaft 9 is eccentric. 9a is rotatably supported. A power roller 11 is rotatably supported around the tip end portion 9b of each displacement shaft 9 protruding from the inner surface of each support plate portion 7.

The pair of displacement shafts 9 and 9 provided for each of the pair of trunnions 6 and 6 are provided at positions opposite to each other by 180 degrees with respect to the input shaft 18. Further, the direction in which the tip end portion 9b of each of these displacement shafts 9, 9 is eccentric with respect to the base end portion 9a is the same as the rotational direction of both the input side and output side disks 2 and 4 (see FIG. (Left and right)
Has become. Further, the eccentric direction is a direction substantially orthogonal to the arrangement direction of the input shaft 18. Therefore,
The power rollers 11, 11 are supported so as to be slightly displaceable in the longitudinal direction of the input shaft 18. As a result, even when the power rollers 11, 11 tend to be displaced in the axial direction of the input shaft 18 due to elastic deformation of each component member based on the thrust load generated by the pressing device 12, each component This displacement is absorbed without applying excessive force to the member.

Further, between the outer side surface of each power roller 11 and the inner side surface of the support plate portion 7 constituting each trunnion 6, 6, thrust rolling bearings are arranged in order from the outer side surface of the power roller 11. A thrust ball bearing 24 and a thrust needle bearing 25 are provided. Of these, the thrust ball bearing 24 bears the load in the thrust direction applied to each power roller 11 while supporting each of these power rollers 1.
One rotation is allowed. Each such thrust ball bearing 24 is composed of a plurality of balls 26, 26, an annular retainer 27 that rotatably holds the balls 26, 26, and an annular outer ring 28. ing. The inner ring raceway of each thrust ball bearing 24 is formed on the outer side surface of each power roller 11, and the outer ring raceway is formed on the inner side surface of each outer ring 28.

Further, the thrust needle bearing 25 is provided with the inner surface of the support plate portion 7 forming each trunnion 6, 6 and the outer ring 2.
It is sandwiched between the outer side surface of 8 and. The thrust needle bearing 25 supports the thrust load applied from the power rollers 11 to the outer rings 28, while the power rollers 11 and the outer rings 28 support the base end portions 9 a of the displacement shafts 9.
Allows oscillating displacement around. Specifically,
The thrust needle bearing 25 includes a race 25a, a cage 25b, and a needle 25c. Of these, the race 25a and the cage 25b are combined so as to be slightly displaceable in the rotational direction. The race 25a and the retainer 25b have annular portions (not shown) centering on the displacement shaft 9 and protruding portions (not shown) that protrude radially outward from a part of the outer peripheral edge of each annular portion. And).

Further, one end of each trunnion 6, 6 (see FIG. 1)
A drive rod 29 is connected to each of the left end portions of the drive rods 4, and a drive piston 30 is fixedly provided on the outer peripheral surface of the intermediate portion of each drive rod 29. The drive pistons 30 are oil-tightly fitted in the drive cylinder 31.

In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 18 is transmitted to the input side disk 2 via the pressing device 12. Then, the rotation of the input side disk 2 causes the pair of power rollers 11, 11 to rotate.
Is transmitted to the output side disk 4 via the, and the rotation of the output side disk 4 is taken out from the output gear 21.

When the rotation speed ratio between the input shaft 18 and the output gear 21 is changed, a pair of drive pistons 30, 30 is used.
Are displaced in opposite directions. Each of these drive pistons 3
With the displacement of 0 and 30, the pair of trunnions 6 and 6 are displaced in opposite directions. For example, the lower power roller 11 in FIG. 14 is displaced to the right side in the figure, and the upper power roller 11 in the figure is displaced to the left side in the figure. As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 and the inner side surfaces 2a and 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. Then, along with the change in the direction of the force, the trunnions 6 and 6 are pivotally supported by the support plates 23 and 23, respectively.
Swing around in the opposite directions.

As a result, as shown in FIGS. 10 and 11, the peripheral surfaces 11a of the power rollers 11, 11 are
The contact position of 11a and each inner side surface 2a, 4a changes, and the rotation speed ratio between the input shaft 18 and the output gear 21 changes. Further, when the torque transmitted between the input shaft 18 and the output gear 21 fluctuates and the elastic deformation amount of each component changes, the power rollers 11, 11 and the outer ring 28 attached to each of the power rollers 11 change. , The base end 9 of each displacement axis 9
It rotates slightly around a. Since the thrust needle bearings 25 are present between the outer side surface of each outer ring 28 and the inner side surface of the support plate portion 7 forming each trunnion 6, the above-mentioned rotation can be performed smoothly. Therefore, as described above, a small force is required to change the inclination angles of the displacement shafts 9, 9.

FIG. 15 is an inner side view of the trunnion in which the thrust needle bearing 25 according to the prior art is assembled.
The figure shows a state in which the neutral state is displaced to the maximum.
In order to prevent the needle 25c constituting the thrust needle bearing 25 from protruding from the race 25a attached to the inner side surface of the trunnion 6 without protruding from the inner side surface, unevenness is provided between the cage 25b and the trunnion 6. Engagement (convex portion 54, concave portion 56) is provided.

The holder 25b is formed by forming a plurality of pockets 41 each having a rectangular shape on a substrate 49 formed of a metal plate or a synthetic resin. Further, a circular hole 50 and a notch 51 projecting radially outward from a part of the circular hole 50 are formed in a portion of the substrate 49 that is slightly deviated from the center to one side in the length direction (right side in FIG. 15). And are formed.

The length direction of each pocket 41 formed on the substrate 49 of the holder 25b coincides with the radial direction centering on the circular hole 50. Therefore, the thrust needle bearing 2
The axial direction of all the needles 25c forming the
It coincides with the radial direction centered on the base end portion 9a of the displacement shaft 9 inserted through.

[0022]

By the way, when the toroidal type continuously variable transmission as described above is in operation, FIG.
When the power roller 11 swings around the displacement shaft 9 as indicated by the arrow A in (a) of FIG.
The cage 25b of the thrust needle bearing (backup bearing) 25 also moves in the swinging direction of the power roller 11 as shown by, but the thrust trace 25a is thrust as shown by an arrow C in FIG. 15 (b). The needle bearing 25 is moved in the opposite direction of the cage 25b to move the trunnion 6
Contacts the pocket portion P of. Specifically, trunnion 6
15C and the outer periphery of the thrust trace 25a are shown in FIG.
The contact is made at the D portion of the above, and the movement of the thrust trace 25a stops.

In this case, if the outer edge 90 of the thrust trace 25a is at a right angle as clearly shown in FIG. 15 (d), the corner R of the pocket P of the trunnion 6 and the outer edge 90 of the thrust trace 25a are Interfere with each other, and the thrust trace 25a rides on the corner R of the pocket P of the trunnion 6,
There is a possibility that the thrust trace 25a may be damaged or the thrust needle bearing 25 may be peeled off. If the amount of movement of the thrust trace 25a is too large, the thrust trace 25a
There is a possibility that a may interfere with the disks 2 and 4. Such a situation can similarly occur in the case of the thrust trace 25a 'of the round bearing (thrust needle bearing) 25' shown in FIG.

As a matter of fact, conventionally, the thrust trace 25a has a straight outer peripheral portion as shown clearly in FIG. 15 (d) (only deburring or press punching is performed). The outer edge portion 90 of the thrust trace 25a has a right angle (Japanese Patent Laid-Open No. 9-
133193, JP-A-10-30700,
See JP-A-11-351344, etc.). Therefore, as described above, the problem that the thrust trace 25a runs over the corner R of the pocket portion P of the trunnion 6 may occur.

In order to prevent such a thrust race 25a from climbing up, it is necessary to reduce the corner R of the trunnion 6 (to make the corner R a right angle according to the right angle shape of the outer edge portion 90 of the thrust trace 25a). However, if the corner R is accurately machined at a right angle using a tool, the tool may be worn or chipped and the life of the tool may be shortened.
In addition, the increase in inspection load increases the manufacturing cost.

The present invention has been made in view of the above circumstances, and it is effective that the outer periphery of the thrust race rides on the corner of the pocket portion of the trunnion as the thrust trace moves when the power roller is swung. An object of the present invention is to provide a toroidal type continuously variable transmission that can be prevented at low cost.

[0027]

In order to solve the above-mentioned problems, the invention described in claim 1 is concentrically and rotatably supported to each other in a state in which the inner side surfaces of each are opposed to each other. First and second discs, a trunnion swinging around a pivot in a twisted position with respect to the central axes of the first and second discs, and a central portion of a support plate portion forming the trunnion, A displacement shaft supported in a state of protruding from the inner side surface of the support plate portion, and a power roller sandwiched between the first and second disks in a state of being rotatably supported around the displacement shaft. And a bearing provided on the outer side surface of the power roller so as to support the load in the thrust direction applied to the power roller and allow the power roller to swing. In front Characterized in that a chamfer on the outer periphery of the thrust race provided between the bearing and the trunnion.

According to the first aspect of the invention, even when the power roller swings and the thrust trace comes into contact with the wall of the trunnion, the chamfer formed on the outer peripheral portion of the thrust trace causes the trunnion pocket. Since there is a margin for interference between the corner of the portion and the thrust race, it is possible to prevent the outer periphery of the thrust race from riding on the corner of the pocket portion of the trunnion, and to increase the corner on the trunnion side.

According to a second aspect of the present invention, in the first aspect of the invention, the chamfering of the thrust trace on the side facing the trunnion is more than the chamfering of the thrust trace on the side facing the power roller. It is also characterized in that

According to the second aspect of the present invention, it is possible to prevent the thrust trace from biting into the trunnion wall.

The invention described in claim 3 is characterized in that, in the invention described in claim 1, the chamfer in the thrust trace is formed by press working.

In the invention described in claim 3, the processing cost of the thrust trace can be reduced.

Further, in the invention described in claim 4, in the invention described in claim 3, a meat escape portion for escaping meat during press working is provided at a portion of the thrust trace which does not contact the trunnion. Is characterized by.

According to the fourth aspect of the present invention, even if the chamfering of the thrust trace is performed by a press, it is possible to prevent the protrusion of the outer peripheral portion, the flat surface side, and the width direction due to the escape of the meat.

According to a fifth aspect of the invention, in the invention according to the second aspect, the thrust trace is
A mark for distinguishing the chamfered position is provided at a position visible after assembly.

According to the fifth aspect of the invention, it is possible to inspect the misassembly in the final inspection after assembly.

[0037]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. A feature of the present invention is a structure capable of effectively and inexpensively preventing the outer periphery of the thrust trace from riding on the corner of the pocket portion of the trunnion as the thrust trace moves when the power roller swings. Since the configuration and the operation thereof are the same as the above-described conventional configuration and operation, only the characteristic part of the present invention will be described below, and the other parts are denoted by the same reference numerals as those in FIGS. 10 to 16. The detailed description will be omitted.

FIG. 1 shows a first embodiment of the present invention. FIG. 1A shows a plan view of the thrust trace, and FIG. 1C shows a side view. As shown in the enlarged view of FIGS. 1B and 1E, the thrust trace 25 according to the present embodiment.
A chamfer 60 is formed on the outer peripheral edge of A. Therefore, as shown in FIG. 1D, even when the power roller 11 swings and the thrust trace 25A comes into contact with the wall of the trunnion 6, the trunnion is formed by the chamfer 60 formed on the outer peripheral portion of the thrust trace 25A. Since the corner R'of the pocket portion P of 6 and the thrust trace 25A can be allowed to interfere with each other, the outer periphery of the thrust trace 25A is prevented from riding on the corner R'of the pocket portion P of the trunnion 6, and the trunnion 6 The side corner R'can be enlarged (corner R '
Need not be formed at a right angle). On the other hand, as in the conventional case shown in FIG. 2, unless the outer peripheral portion of the thrust trace 25a is chamfered, as shown in FIG. 2D, the trunnion 6 is provided to prevent the thrust trace 25a from climbing up. The corner R of the pocket P must be made small, and therefore the tool for machining the corner R is worn or chipped, which shortens the tool life and increases the inspection load. The cost increases. The configuration of this embodiment does not cause such a problem.

FIG. 3 shows a second embodiment of the present invention. As shown in the figure, in this embodiment, a chamfer 60 is formed on the outer peripheral edge of the thrust trace 25A 'of the round bearing (thrust needle bearing) 25'. Therefore, as shown in FIG. 3C, even when the power roller 11 swings and the thrust trace 25A ′ comes into contact with the wall of the trunnion 6, the chamfer 60 formed on the outer peripheral portion of the thrust trace 25A ′ causes Since the interference between the corner R ′ of the pocket P of the trunnion 6 and the thrust trace 25A ′ can be afforded, the outer periphery of the thrust trace 25A ′ is prevented from riding on the corner R ′ of the pocket P of the trunnion 6. At the same time, the corner R ′ on the trunnion 6 side can be increased (the corner R ′ need not be formed at a right angle). On the other hand, as in the conventional case shown in FIG.
If the chamfer is not formed on the outer peripheral portion of 5a ', as shown in FIG.
As shown in (c), the corner R of the pocket P of the trunnion 6 is provided to prevent the thrust race 25a 'from riding up.
Therefore, the tool for machining the corner R is worn or chipped, which shortens the life of the tool and increases the inspection load, which increases the manufacturing cost. The configuration of this embodiment does not cause such a problem.

By the way, the thrust traces 25A, 25
If chamfering 60 is processed on both sides of A ′, not only the processing cost increases but also the contact width W (see (d) of FIG. 1) between the thrust traces 25A, 25A ′ and the wall of the trunnion 6 decreases. The thrust traces 25A and 25A 'may bite into the wall of the trunnion 6. Therefore, in order to prevent the thrust traces 25A and 25A ′ from biting, it is desirable that the chamfer of the thrust traces 25A and 25A ′ on the trunnion 6 side be larger than the chamfer of the thrust traces 25A and 25A ′ on the power roller 11 side. Particularly, when using a thin thrust trace, it is desirable to provide the chamfer 60 only on the trunnion 6 side. Further, in order to secure the proof stress of the backup bearing, the thrust traces 25A, 25
It is desirable that the wall thickness difference of A ′ is 0.03 mm or less.

Further, in order to reduce the processing cost of the thrust traces 25A and 25A ', it is desirable to form the chamfer 60 by pressing with a press. However, when the chamfer 60 of the thrust traces 25A and 25A 'is processed by a press in this way, protrusions occur in each direction as shown in FIG. That is, during press working of the chamfer 60, the meat escapes to the outer peripheral portions of the thrust traces 25A, 25A 'to form a protrusion 65 at this portion (the state of FIG. 5A), or the thrust traces 25A, 25A'. The meat escapes to the flat surface side of and the protrusion 66 is generated at this portion (state of (b) of FIG. 5), or the thrust trace 25
Meat escapes in the width direction of A, 25A 'and protrudes in this area 6
7 occurs (state of FIG. 5C). The thrust trace can reduce the protrusion from the trunnion 6 during swinging by reducing the gap between the trussion 6 and the pocket P of the trunnion 6. Therefore, it is necessary to reduce the dimensional tolerance of the outer diameter of the thrust trace. However, when the chamfering of the outer peripheral portion of the thrust trace is processed by a press, if a protrusion 65 is formed in the outer peripheral direction as shown in FIG. 5A, the assembly becomes impossible or the swing amount becomes large. Will end up. Also, as shown in FIG.
If this occurs, the surface pressure distribution of the thrust trace and the backup bearing will not be uniform, and there is a risk of separation.
That is, the proof stress of the thrust trace is reduced. Further, when the protrusion 67 is formed in the width direction as shown in FIG. 5C, the thrust trace and the disks 2 and 4 may interfere with each other.

Therefore, as shown in FIGS. 6 and 7, the thrust traces 25A which do not contact the trunnion 6,
It is desirable to provide the meat relief portion 70 of the press at the portion 25A '. Specifically, as shown in FIG. 6, meat escape portions 70 are provided on both sides of the thrust trace 25A (F portion in FIG. 6A) that does not contact the trunnion 6. 6C shows the shape of the chamfer 60 before pressing, and FIG. 6D shows the shape after pressing. By doing so, as shown in (d) of FIG. 6 during press working, the meat escapes in the meat escape portion 70 and a protrusion 79 occurs in the meat escape portion 70, so that FIG. As shown in (b), protrusion does not occur in the outer peripheral portion, the flat surface side, and the width direction. Note that FIG. 7 shows a case where a concave meat relief portion 70 is provided in the central portion of the thrust trace 25A, and FIG.
Shows the shape of the chamfer 60 before pressing, and (d) shows the shape after pressing. Also in this case, the same effect as that of FIG. 6 can be obtained.

Note that the chamfer 60 is generally hidden after assembly, and it is not possible to inspect for a wrong assembly later. Therefore, as shown in FIG. 9, the front and back can be seen at the position visible even after assembly. It is desirable to attach a mark 80 (so that the chamfer position can be seen). This allows
It becomes possible to inspect misassembly in the final inspection.

[0044]

As described above, according to the toroidal type continuously variable transmission of the present invention, the outer circumference of the thrust trace is located at the corner of the pocket portion of the trunnion as the thrust trace moves when the power roller swings. It is possible to effectively and inexpensively prevent riding.

[Brief description of drawings]

1A and 1B show a thrust trace according to a first embodiment of the present invention, FIG. 1A is a plan view of the thrust trace, FIG. 1B is an enlarged view of an F portion of FIG. 1A, and FIG. 3D is a side view of the thrust trace, FIG. 7D is a cross-sectional view of a main part of the thrust trace when assembled, and FIG. 6E is an enlarged view of the outer peripheral edge portion of the thrust trace of FIG.

FIG. 2 shows a conventional thrust trace, (a) is a plan view of the thrust trace, (b) is an enlarged view of an E portion of (a),
(C) is a side view of the thrust trace of (a), (d) is a principal part sectional view at the time of assembling of the thrust trace.

3A and 3B show a thrust trace according to a second embodiment of the present invention, wherein FIG. 3A is a plan view of the thrust trace, FIG. 3B is a side view of the thrust trace shown in FIG. 3A, and FIG. FIG. 3D is a cross-sectional view of a main part at the time of assembly, and FIG.

FIG. 4 shows a conventional thrust trace, (a) is a plan view of the thrust trace, (b) is a side view of the thrust trace of (a), and (c) is a cross-sectional view of a main part of the thrust trace when assembled. is there.

FIG. 5 is an enlarged view of an essential part showing a mode of occurrence of protrusion due to meat escape by press working.

6A and 6B show a first form of the meat relief portion, in which FIG. 6A is a plan view of a thrust trace, FIG. 6B is a side view of the thrust trace in FIG. 6A, and FIG. FIG. 6A is an enlarged view of the F portion of FIG. 9A showing the shape, and FIG. 8D is an enlarged view of the F portion of FIG.

7A and 7B show a second form of the meat relief portion, where FIG. 7A is a plan view of a thrust trace, FIG. 7B is a side view of the thrust trace shown in FIG. 7A, and FIG. An enlarged view showing the shape, (d) is an enlarged view showing the shape after press working.

FIG. 8 is a schematic view showing a state in which a protrusion due to meat escape does not occur in the outer peripheral portion, the plane side, and the width direction due to the formation of the meat escape portion.

FIG. 9 is a plan view of a thrust trace, showing a form in which a marking for determining the chamfer position is provided.
(B) is a side view of the thrust trace of (a), (c) is a side view which shows the Merkong position of the thrust needle after an assembly.

FIG. 10 is a side view showing a basic configuration known from the related art in a state at the time of maximum deceleration.

FIG. 11 is a side view showing a basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum acceleration.

FIG. 12 is a cross-sectional view showing a specific shape of the trunnion elastically deformed by a thrust load.

FIG. 13 is a sectional view showing an example of a conventional specific structure.

14 is a cross-sectional view taken along the line XX of FIG.

FIG. 15 shows a conventional power roller unit, (a)
Is a bottom view of the power roller unit, (b) is a plan view of the inside of the thrust needle bearing with the power roller removed, (c) is an enlarged view of a main part of (b), (d) is X- of (c). It is sectional drawing which follows an X-ray.

FIG. 16 shows another conventional power roller unit,
(A) is a bottom view of the power roller unit, (b) is a plan view of the inside of the thrust needle bearing with the power roller removed, (c) is an enlarged view of essential parts of (b), (d)
FIG. 7C is a sectional view taken along line XX in (c).

[Explanation of symbols]

1 input axis 2 Input side disk 2a Inside surface 3 output axes 4 Output side disc 4a inner surface 5 Axis 6 trunnions 7 Support plate 8 Bent walls 9 Displacement axis 9a base end 9b tip 10 circular holes 11 Power roller 11a peripheral surface 25 Thrust needle bearing 25A, 25A 'thrust trace 60 chamfer P pocket

Claims (5)

[Claims] 1. A first and a second which are concentrically and rotatably supported in a state in which their inner side surfaces face each other.
Disc, a trunnion that swings about a pivot that is in a twisted position with respect to the central axes of the first and second discs, and the support plate portion at the center of the support plate portion that constitutes the trunnion. A displacement shaft supported in a state of protruding from the inner side surface of the disk, a power roller sandwiched between the first and second disks in a state of being rotatably supported around the displacement shaft, and a power roller In a toroidal type continuously variable transmission, which is provided so as to be attached to the outer side surface of the roller, and which bears a load in the thrust direction applied to the power roller and allows the power roller to swing. A toroidal type continuously variable transmission characterized in that a chamfer is provided on an outer peripheral portion of a thrust trace provided between the trunnion and the trunnion. 2. The toroidal type continuously variable transmission according to claim 1, wherein the chamfer of the thrust trace on the side facing the trunnion is larger than the chamfer of the thrust trace on the side facing the power roller. Machine 3. The toroidal type continuously variable transmission according to claim 1, wherein the chamfer in the thrust trace is formed by press working. 4. The toroidal-type continuously variable transmission according to claim 3, wherein a meat escape portion for escaping meat during press working is provided at a portion of the thrust race that does not come into contact with the trunnion. 5. The toroidal type continuously variable transmission according to claim 2, wherein the thrust trace is provided with a mark for determining a chamfered position at a position visible after assembly.