JP2003065408A - Troidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a troidal type continuously variable transmission capable of effectively preventing a trunnion from elastic deformation. SOLUTION: The troidal type continuously variable transmission is furnished with a coupling member 33 to couple together a pair of folded wall parts 8, 8, and the coupling member 33 has a pressure receiving part 33b to abut on the inner surface of a pocket part P in the direction approximately perpendicular to the thrust direction and receive a pressing force acting in such a way as crushing the pocket part P.

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, FIGS.
In part, the use of a toroidal type continuously variable transmission as schematically shown in FIG. 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 in which the toroidal type continuously variable transmission is housed, there are provided trunnions 6 and 6 which swing around pivots 5 and 5 which are twisted with respect to the input shaft 1 and the output shaft 3.

That is, each trunnion 6, 6 is shown in FIG.
Further, as shown in FIG. 12 described later, a state in which the support plate portion 7 is bent at both ends in the longitudinal direction (left and right direction in FIGS. 10 and 12) of the support plate portion 7 on the inner side surface side (upper side in FIG. 10). 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. 8 and 9), and the same is applied to the outer surface (the right side surface of FIGS. 8 and 9) of the input side disk 2. Cam surface 17 is formed. And the plurality of rollers 15, 15 are
It is supported so that it can rotate around 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.
As shown in FIG. 8, the displacement shafts 9 and 11a are arranged so that the a and 11a respectively come into contact with the central portion of the inner side surface 2a of the input side disk 2 and the outer peripheral portion of the inner side surface 4a of the output side disk 4. Tilt 9.

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 displacement shafts 9 and 9 are tilted so as to contact the outer peripheral portion of the inner side surface 2a and the central portion of the inner side surface 4a of the output disk 4, respectively. If the inclination angles of the displacement shafts 9, 9 are set in the middle between FIGS. 8 and 9, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.

Further, FIG. 11 and FIG.
1 shows a more specific toroidal type continuously variable transmission described in a microfilm of No. -69293 (Jaikaihei 1-173552). The input side disk 2 and the output side disk 4 are respectively supported around a circular tubular input shaft 18 via needle bearings 19 and 19 so as to be rotatable and axially displaceable. Further, a cam plate 13 for constituting the loading cam type pressing device 12 is provided.
Is spline-engaged with the outer peripheral surface of the end portion (the left end portion in FIG. 11) of the input shaft 18, and the collar 20 allows the input-side disk 2 to
Movement away from is blocked. An output gear 21 is connected to the output side disk 4 by keys 22 and 22, and the output side disk 4 and the output gear 2 are connected to each other.
1 and 1 rotate in synchronization with each other.

Both ends of the pair of trunnions 6 and 6 having the structure shown in FIG. 10 are swingable with respect to the pair of support plates 23 and 23 and axially (see FIG. 11).
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 and 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 (FIG. 12). In the left and right directions). 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.

Further, one end of each trunnion 6, 6 (see FIG. 1)
A drive rod 29 is coupled to each of the left end portions of the drive rods 2, 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. 12 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. 8 and 9, the peripheral surfaces 11a and 11 of the power rollers 11 and 11, respectively.
The contact position between a and each inner 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. , Slightly rotate around the base end 9a of each displacement shaft 9. 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.

[0019]

When the toroidal type continuously variable transmission as described above is in operation, the power roller 11 is rotatably supported on the inner side surface (the pocket portion P side) of each trunnio 6,6. Is applied with thrust loads from the inner side surfaces 2a, 4a of both the input side and output side disks 2, 4.
Then, this thrust load is transmitted to the inner side surface of the support plate portion 7 constituting each trunnion 6 via the thrust ball bearing 24 and the thrust needle bearing 25. Therefore, during operation of the toroidal type continuously variable transmission, the trunnions 6, 6 are elastically deformed, though slightly, in a direction in which the inner side surface on which the power roller 11 is located is concave, as exaggeratedly shown in FIG. .

When this elastic deformation amount becomes large,
Balls 26 and 2 that are rolling elements that constitute the thrust ball bearing 24
6 and the thrust load applied to the needles forming the thrust needle bearing 25 becomes uneven. That is, as a result of the elastic deformation of each trunnion 6, the distance between the inner side surface of the support plate portion 7 forming each trunnion 6 and the outer side surface of each power roller 11 becomes uneven. Then, instead of reducing the thrust load applied to the rolling element present in the portion where the distance between these two surfaces is increased, the thrust load applied to the rolling element present in the portion where the distance is decreased increases. As a result, an excessive thrust load is applied to a part of the rolling elements, and the contact pressure between this part of the rolling elements and the raceway surface with which the rolling surface of the rolling element abuts becomes excessive. Fatigue life of moving surfaces and raceways is significantly shortened.

Further, the connecting portions A between the respective pivot shafts 5 and 5 which are rolling surfaces of the tilt bearings provided at both ends of the trunnion 6 and the supporting plate portion 7 for supporting the power roller 11 (see FIG. 1).
3)), stress is likely to concentrate, and when excessive torque is input and the trunnion 6 elastically deforms as described above, damage such as cracks is likely to occur at the joint portion A.
Therefore, conventionally, the wall thickness of the trunnion 6 is increased,
Although such damage is prevented, it is not preferable because the size is increased, the weight is increased, and the cost is increased. Further, it is necessary to connect the pivot 5 and the support plate portion 7 with a larger radius than necessary, which causes a problem in processing.

When the trunnion 6 is elastically deformed as shown in FIG. 10, the displacement shaft 9 is inclined with respect to the trunnion 6. In that case, stress concentrates on the engaging portion B (see FIG. 13) between the base end 9a of the displacement shaft 9 and the trunnion 6, and damage such as cracks easily occurs at this portion. Further, when the displacement shaft 9 is inclined with respect to the trunnion 6, the position of the power roller 11 supported by the tip portion 9b of the displacement shaft 9 is displaced, so that the peripheral surface 11a of the power roller 11 and the inner surface 2a of each disk 2, 4 are displaced. , 4a deviates from the predetermined position and the gear shifting operation becomes unstable.

Therefore, a pair of bent wall portions 8 and 8 are provided on the inner side surface of the trunnion 6 where the power roller 11 is located.
There is also proposed a technique for providing a connecting member for connecting the distal end portions of the above and restricting elastic deformation in the direction in which the inner side surface of the trunnion 6 becomes a concave surface by this connecting member (see Japanese Patent Application No. 2000-122648). . However, in this technique, since the tip ends of the pair of bent wall portions 8 are simply connected to each other by the connecting member, elastic deformation of the trunnion 6 may not be effectively prevented. That is, since there is a recessed pocket portion P in which the power roller 11 is accommodated on the side of the trunnion 6 where the connecting member is located (inner side surface side), the trunnion 6 is elastically deformed in the direction in which the pocket portion P is crushed. Although it is easy to perform, the connecting member simply connects the front end portions of the bent wall portions 8 and 8, so that the pocket portion P
Cannot be well received in that direction (the regulating force of the connecting member that regulates the elastic deformation of the trunnion 6 does not effectively act in the direction against the force that crushes the pocket portion P). Therefore, the elastic deformation of the trunnion 6 may not be effectively prevented. Therefore, it may be necessary to secure a large strength of the connecting member.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a toroidal type continuously variable transmission which can effectively prevent elastic deformation of a trunnion.

[0025]

To achieve the above object, a toroidal type continuously variable transmission according to a first aspect of the present invention is provided.
First and second discs that are concentrically and rotatably supported in a state where their inner side surfaces face each other,
A trunnion that swings around a pivot that is in a twisted position with respect to the central axes of the first and second disks, and a central portion of a support plate portion that configures the trunnion, from an inner surface of the support plate portion. The displacement shaft supported in a protruding state and the first shaft in a state of being rotatably supported around the displacement shaft.
And a power roller sandwiched between the second and second disks, and provided on the outer surface of the power roller so as to support the load in the thrust direction applied to the power roller while rotating the power roller. With bearings that allow
A pair of bent wall portions is formed at both ends of the support plate portion in the longitudinal direction so as to be bent toward the inner side surface of the support plate portion so as to form a pocket portion for accommodating the power roller, and each of these bent wall portions is formed. In a toroidal type continuously variable transmission in which the respective pivots are concentrically provided on the outer surface of the portion, a connecting member that connects the pair of bent wall portions is provided, and the connecting member is substantially orthogonal to the thrust direction. It has a pressure receiving portion which is in contact with the inner surface of the pocket portion in a direction to receive a pressing force which acts so as to crush the pocket portion.

According to the invention described in claim 1,
The pressure receiving portion that is in contact with the inner surface of the pocket portion can directly receive the force that crushes the pocket portion in that direction. Therefore, the elastic deformation of the trunnion can be effectively prevented, and the stress acting on the connecting portion between the pivot of the trunnion and the support plate portion can be reduced.

Further, in the toroidal type continuously variable transmission according to a second aspect of the present invention, in the invention of the first aspect, the connecting member has an abutment surface that abuts the trunnion outside the pocket portion in the thrust direction. It is characterized by having.

According to the invention described in claim 2,
Since the abutment surface can prevent the trunnion from falling in the thrust direction, it is possible to further reduce the stress acting on the connecting portion between the pivot of the trunnion and the support plate portion.

Further, in the toroidal type continuously variable transmission according to claim 3, in the invention according to claim 1 or 2, the pressure receiving portion of the connecting member and the inner surface of the pocket portion to which the pressure receiving portion is joined. A tightening margin is provided therebetween, and the pressure receiving portion is press-fitted into the pocket portion by an interference fit.

According to the invention described in claim 3,
Since the pressure receiving portion is press-fitted into the pocket portion by an interference fit, bending deformation of the trunnion can be relieved. Further, the tightening allowance can prevent the connecting member from coming off from the trunnion in the thrust direction.

Further, in the toroidal type continuously variable transmission described in claim 4, in the invention described in claim 1 or 2, the connecting member is a means for preventing the connecting member from coming off from the trunnion in the thrust direction. It is characterized by having.

According to the invention described in claim 4,
The connecting member can be firmly fixed to the trunnion.

Further, in the toroidal type continuously variable transmission according to claim 5, in the invention according to claim 1 or 2, at least the pressure receiving portion of the connecting member and the joining surface of the trunnion joined thereto. One is characterized by being inclined at a predetermined angle with respect to the thrust direction.

According to the invention described in claim 5,
When the trunnion is deformed, the inclined surface bites into the mating member like a wedge, so that the deformation of the trunnion can be further suppressed. In addition, the inclined surface is wedge-shaped so that the connecting member can be prevented from coming off the trunnion in the thrust direction.

[0035]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. The feature of the present invention is that when the toroidal type continuously variable transmission is in operation, the thrust load applied from the power roller 11 to the inner surface of the support plate portion 7 of the trunnion 6 via the thrust ball bearing 24 and the thrust needle bearing 25 causes Since the support plate portion 7 is effectively prevented from elastically deforming, and other configurations and actions are similar to the above-described conventional configurations and actions, only the characteristic portions of the present invention will be described below. However, other parts are denoted by the same reference numerals as those in FIGS. 8 to 13, and detailed description thereof will be omitted.

FIG. 1 shows a first embodiment of the present invention. As shown in the figure, the trunnion 6 that constitutes the toroidal type continuously variable transmission of the present embodiment is provided at both end portions in the longitudinal direction (left and right direction in FIG. 1) of the support plate portion 7 as in the case of the conventional structure described above. The support plate portion 7 has a pair of bent wall portions 8 formed on the inner side surface side (upper side in FIG. 1) in a bent state. The pivots 5 and 5 are concentrically provided on the outer side surfaces of the bent wall portions 8 and 8, respectively.

Further, in this embodiment, the base end portion 9a of the displacement shaft 9 and the outer ring 28 in the conventional structure are integrally formed, and the tip end portion 9b of the displacement shaft 9 and the power roller 11 are integrally formed. ing. In addition, the base end portion 9a of the displacement shaft 9
The circular hole 10 in the central portion of the support plate portion 7 that supports the is not formed to penetrate, and is formed in a bag shape with one end side (the side opposite to the pocket portion P in which the power roller 11 is accommodated) closed. There is.

Further, in the trunnion 6 of the present embodiment, the inner side surface of the trunnion 6 on which the power roller 11 is located (the pocket portion P side) is elastically deformed in the direction in which the inner side surface of the trunnion 6 becomes a concave surface. Controlling connecting member 3
3 is provided. The connecting member 33 is formed on both ends of the main body portion 33a so as to be installed between the front end portions of the pair of bent wall portions 8 and 8 and the inner surface of the pocket portion P (specifically, , Bent wall part 8,
8) and a pressure receiving portion 33b, 33b which is capable of directly receiving a pressing force for crushing the pocket portion P in that direction by abutting it in a sufficiently wide range. In this case, the pressure receiving portion 3
3b is a pocket portion P in a direction substantially orthogonal to the thrust direction.
It comes into contact with the inner surface of and is joined to the trunnion 6 by welding or the like. The connecting member 33 is formed in a bridge shape by subjecting a material having sufficient rigidity, such as steel, to a processing such as forging that provides a large rigidity.

The connecting member 33 is assembled with the displacement shaft 9, the power roller 11, the thrust ball bearing 24, and the thrust needle bearing 25 on the trunnion 6 and then fixedly coupled to the trunnion 6. That is, the pressure receiving portion 33b
Is inserted into the pocket portion P to abut against the inner surface of the pocket portion P, and the end portion of the pressure receiving portion 33b is abutted against the step portion 59 formed in the pocket portion P, for example, so as to straddle the power roller 11. The part 33a is extended. Then, in this state, the pressure receiving portion 33b is joined to the trunnion 6 by welding or the like from the side opening of the pocket portion P, for example.

With the connecting member 33 fixedly connected to the trunnion 6, the power roller 11 is placed between the connecting member 33 and the support plate portion 7 of the trunnion 6. However, in the power roller 11, the inner side surfaces 2a and 4a of both the input side and output side disks 2 and 4 (see FIG. 8,
9 and 11) is exposed from the side edge of the connecting member 33 (side opening of the pocket P). A part of the peripheral surface 11a of the power roller 11 is formed by connecting the connecting member 33
Since the part exposed from the side edge of the connecting member 33 can be brought into contact with the inner side surfaces 2a and 4a, the shape and size of the connecting member 33 should not interfere with the discs 2 and 4 regardless of the swing of the trunnion 6. Set the height.

As described above, in the toroidal type continuously variable transmission according to the present embodiment, the pair of bent wall portions 8, 8 provided at both longitudinal ends of the trunnion 6 are connected by the connecting member 33. Trunnion 6
The bending rigidity of is improved. Therefore, when the toroidal type continuously variable transmission is operated, the trunnion 6 is less likely to be elastically deformed even when an upward thrust load in FIG. 1 is applied to the inner side surface of the support plate portion 7 forming the trunnion 6. In particular, the connecting member 33 of the present embodiment is brought into contact with the inner surface of the pocket portion P (specifically, the inner surfaces of the bent wall portions 8 and 8) in a sufficiently wide range so that the force for crushing the pocket portion P is applied in that direction. Since the pressure receiving portions 33b and 33b that can be directly received by the are provided, it is possible to effectively prevent the elastic deformation of the trunnion 6. That is, since the pressure receiving portion 33 can effectively receive and support the force that crushes the pocket P in that direction, the regulating force of the connecting member 33 that regulates the elastic deformation of the trunnion 6 crushes the pocket P. Effectively works against force. Therefore, the change in the interval between the tip edges of the pair of bent wall portions 8 and 8 is restricted,
Elastic deformation of the trunnion 6 is effectively prevented. Also,
Since the pressure receiving portion 33 can receive the force for crushing the pocket P in a relatively wide area, this force can be dispersed and transmitted to the main body portion 33a. Therefore, the connecting member 33
Since no concentrated stress is generated in the joint, damage to the connecting member 33 can be prevented.

Further, if the elastic deformation of the trunnion 6 can be effectively prevented as described above, stress is concentrated on the joint portion A between the pivots 5 and 5 and the support plate portion 7 even if an excessive torque is input. (Reducing the stress) and without increasing the wall thickness of the trunnion 6 in particular,
It is possible to prevent damage such as cracks from occurring at the base end portion of the. Therefore, the weight and cost can be reduced, and the trunnion can be downsized. Further, it is possible to prevent the displacement shaft 9 from tilting due to the deformation of the trunnion 6 and to prevent the position of the power roller 11 supported by the distal end portion 9b of the displacement shaft 9 from being displaced, so that the shifting operation can be stabilized. it can. In the present embodiment, the base end portion 9 of the displacement shaft 9 is
Since the circular hole 10 in the central portion of the support plate portion 7 that supports a is not penetrated and is formed in a bag shape with one end side closed, the displacement shaft 9 may be inclined with respect to the trunnion 6. Even if there is, the base end 9a of the displacement shaft 9 and the trunnion 6
It is possible to avoid a situation in which stress is concentrated on the engaging portion B with and the damage such as a crack occurs in this portion.

FIG. 2 shows a second embodiment of the present invention. Since the present embodiment is a modification of the first embodiment, the same components as those of the first embodiment will be designated by the same reference numerals and the description thereof will be omitted.

As shown, the connecting member 33 of this embodiment.
The trunnion 6 outside the pocket P of the trunnion 6.
The contact surface 33c that receives the force in the bending direction of the trunnion 6 in the thrust direction by contacting the inner end portion (the end surface portion of the trunnion located at the peripheral edge of the pocket P) in the thrust direction (vertical direction in FIG. 2). Have

According to this structure, the abutment surface 33c can prevent the trunnion 6 from falling in the thrust direction, so that the stress at the connecting portion A between the pivot 5 of the trunnion 6 and the support plate 7 can be further reduced. Can be lowered. In addition, in the present embodiment, the trunnion 6 and the contact surface 33.
In order to bring them into close contact with c, the bolt 50 may be inserted from the thrust direction in the area of the contact surface 33c to fasten the trunnion 6 and the connecting member 33.

FIG. 3 shows a third embodiment of the present invention. Since the present embodiment is a modification of the first embodiment, the same components as those of the first embodiment will be designated by the same reference numerals and the description thereof will be omitted.

As shown in the figure, in this embodiment, a tightening margin is provided between the pressure receiving portion 33b of the connecting member 33 and the pocket portion P (concave hole). That is, the inner diameter L of the pocket portion P is set smaller than the outer diameter of the pressure receiving portion 33b. Therefore, the pressure receiving portion 33b is elastically deformed inward in the longitudinal direction of the connecting member 33, and is press-fitted into the pocket portion P by an interference fit.

With such a structure, even if a large thrust load acts on the trunnion 6,
The bending deformation can be relaxed, and the stress at the bonding site A can be reduced. Further, the tightening allowance can prevent the connecting member 33 from coming off from the trunnion 6 in the thrust direction. Therefore, the bolt 50 in the thrust direction as shown in FIG. 2 is unnecessary, and the reliability is improved. The interference fit may be formed by inclining the pressure receiving portion 33b inward in the longitudinal direction of the connecting member 33.

FIG. 4 shows a fourth embodiment of the present invention. Since the present embodiment is a modification of the second embodiment, the same components as those of the second embodiment will be designated by the same reference numerals and the description thereof will be omitted.

As shown, the connecting member 33 of this embodiment.
At the end of the pressure receiving portion 33b, a protruding portion 33d extending in a direction orthogonal to the thrust direction (outward in the radial direction of the connecting member 33) is formed. And this protrusion 33d
Is inserted into the hole 61 of the trunnion 6 extending in the axial direction of the pivot 5.

According to this structure, the connecting member 33 is engaged with the trunnion 6 by the engagement of the projecting portion 33d and the hole 61.
Can be prevented from coming off in the thrust direction. Therefore, the bolt 50 in the thrust direction as shown in FIG. 2 is unnecessary, and the reliability is improved. As another means for preventing the connecting member 33 from coming off from the trunnion 6 in the thrust direction, as shown in FIG.
It is also considered that a key groove is provided in a predetermined portion of the pressure receiving portion 33b of the connecting member 33 and a portion of the trunnion 6 facing the pressure receiving portion 33b, and the movement of the connecting member 33 in the thrust direction is restricted by the key 55 inserted in the key groove. To be

FIG. 6 shows a fifth embodiment of the present invention. Since the present embodiment is a modification of the second embodiment, the same components as those of the second embodiment will be designated by the same reference numerals and the description thereof will be omitted.

In this embodiment, the pressure receiving portion 3 of the connecting member 33 is used.
The joint surface between 3b and the trunnion 6 is inclined at a predetermined angle with respect to the thrust direction. Specifically, the joint surface 60 of the pressure receiving portion 33b that abuts the trunnion 6 is inclined toward the inner side in the longitudinal direction of the connecting member 33, and the joint surface 62 of the trunnion 6 that abuts the pressure receiving portion 33b has the same direction. Is inclined to.

According to this structure, when the trunnion 6 is deformed, the inclined surfaces 60 and 62 bite into each other like wedges, so that the deformation of the trunnion 6 can be further suppressed. In addition, the inclined surfaces 60 and 62 bite into each other in a wedge shape, so that the connecting member 33 can be prevented from coming off the trunnion 6 in the thrust direction. The inclination directions of the inclined surfaces 60 and 62 may be opposite to those in the case of FIG. 6, as shown in FIG.

It is needless to say that the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the invention. For example, in the above-described embodiment, the circular hole 10 of the trunnion 6 on which excessive stress may act.
The present invention is applied to a structure in which the bag is formed in a bag shape, but the present invention can also be applied to a structure in which the circular hole 10 penetrates as in the related art. Further, in the above-described embodiment, the present invention is applied to the structure in which the inner ring and the outer ring of the power roller 11 are supported via bearings, but both the inner ring and the outer ring are supported by the pivot shaft as in the conventional case. The present invention can be applied to the above structure.

[0056]

As described above, according to the invention described in claim 1, the pressure receiving portion abutting against the inner surface of the pocket portion directly receives the force for crushing the pocket portion in that direction. You can Therefore, the elastic deformation of the trunnion can be effectively prevented, and the stress acting on the connecting portion between the pivot of the trunnion and the support plate portion can be reduced.

According to the second aspect of the present invention, the same action and effect as those of the first aspect can be obtained, and since the abutment surface can prevent the trunnion from falling in the thrust direction, It is possible to further reduce the stress acting on the connecting portion with the support plate portion.

According to the third aspect of the present invention, the same effect as that of the first or second aspect can be obtained, and the pressure receiving portion is press-fitted into the pocket portion by the interference fit. The bending deformation of the trunnion can be relaxed. Further, the tightening allowance can prevent the connecting member from coming off from the trunnion in the thrust direction.

According to the invention described in claim 4, it is possible to obtain the same effect as that of claim 1 or 2, and it is possible to firmly fix the connecting member to the trunnion.

According to the fifth aspect of the present invention, the same effect as that of the first or second aspect can be obtained, and when the trunnion is deformed, the inclined surface is formed like a wedge on the mating member. Since it bites into the trunnion, the deformation of the trunnion can be further suppressed. In addition, the inclined surface is wedge-shaped so that the connecting member can be prevented from coming off the trunnion in the thrust direction.

[Brief description of drawings]

FIG. 1 is an enlarged cross-sectional view showing a trunnion corresponding to the trunnion arranged on the upper side of FIG. 12 taken out from the toroidal type continuously variable transmission according to the first embodiment of the present invention.

FIG. 2 is an enlarged sectional view of a portion corresponding to FIG. 1 of a toroidal type continuously variable transmission according to a second embodiment of the present invention.

FIG. 3 is an enlarged cross-sectional view of a portion corresponding to FIG. 1 of a toroidal type continuously variable transmission according to a third embodiment of the present invention.

FIG. 4 is an enlarged sectional view of a portion corresponding to FIG. 1 of a toroidal type continuously variable transmission according to a fourth embodiment of the present invention.

FIG. 5 is an enlarged cross-sectional view according to a modified example of FIG.

FIG. 6 is an enlarged cross-sectional view of a portion corresponding to FIG. 1 of a toroidal type continuously variable transmission according to a fifth embodiment of the present invention.

7 is an enlarged cross-sectional view according to a modified example of FIG.

FIG. 8 is a side view showing a basic configuration known from the related art in a state at the time of maximum deceleration.

FIG. 9 is a side view showing a basic structure of a conventionally known toroidal type continuously variable transmission in a state at maximum acceleration.

FIG. 10 is a cross-sectional view showing a specific shape of the trunnion elastically deformed by a thrust load.

FIG. 11 is a sectional view showing an example of a conventional specific structure.

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

FIG. 13 is an enlarged sectional view showing a conventional structure of a trunnion and a power roller.

[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 33 Connection member 33a main body 33b Pressure receiving part 33c Abutment surface 33d protrusion 60,62 inclined surface 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 A bearing provided to be attached to the outer side surface of the roller and allowing the rotation of the power roller while supporting the load in the thrust direction applied to the power roller, is provided at both ends in the longitudinal direction of the support plate portion. Is
A pair of bent wall portions are formed on the inner side surface of the support plate portion so as to form a pocket portion for accommodating the power roller, and the respective pivots are concentrically formed on the outer surface of each of the bent wall portions. The toroidal type continuously variable transmission that is provided is provided with a connecting member that connects the pair of bent wall portions to each other, and the connecting member is in contact with the inner surface of the pocket portion in a direction substantially orthogonal to the thrust direction and the pocket. A toroidal-type continuously variable transmission having a pressure receiving portion that receives a pressing force that acts to crush the portion. 2. The toroidal type continuously variable transmission according to claim 1, wherein the connecting member has an abutment surface that abuts the trunnion in the thrust direction outside the pocket portion. 3. A tightening margin is provided between the pressure receiving portion of the connecting member and an inner surface of the pocket portion to which the pressure receiving portion is joined,
The toroidal type continuously variable transmission according to claim 1 or 2, wherein the pressure receiving portion is press-fitted into the pocket portion by an interference fit. 4. The toroidal type continuously variable transmission according to claim 1, wherein the connecting member has means for preventing the connecting member from being disengaged from the trunnion in a thrust direction. 5. The pressure receiving portion of the connecting member and at least one of the joining surfaces of the trunnions joined to the pressure receiving portion are inclined at a predetermined angle with respect to the thrust direction. The toroidal type continuously variable transmission described in.