JP5768400B2 - Toroidal continuously variable transmission - Google Patents

Description

  The present invention relates to a toroidal continuously variable transmission that can be used for transmissions of automobiles and various industrial machines.

  For example, a double-cavity toroidal continuously variable transmission used as a transmission for an automobile is configured as shown in FIGS. As shown in FIG. 4, an input shaft (center shaft) 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two outputs are provided on the outer periphery of the input shaft 1. Side disks 3 and 3 are attached. An output gear 4 is rotatably supported on the outer periphery of the intermediate portion of the input shaft 1. Output side disks 3 and 3 are connected to cylindrical flange portions 4a and 4a provided at the center of the output gear 4 by spline coupling.

  The input shaft 1 is rotationally driven by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate 7 located on the left side in the drawing. . The output gear 4 is supported in the casing 50 via a partition wall 13 formed by coupling two members, so that the output gear 4 can rotate around the axis O of the input shaft 1 while the axis O. Directional displacement is prevented.

  The output side disks 3 and 3 are supported by needle bearings 5 and 5 interposed between the input shaft 1 so as to be rotatable about the axis O of the input shaft 1. Further, the left input side disk 2 in the figure is supported on the input shaft 1 via a ball spline 6, and the right side input disk 2 in the figure is splined to the input shaft 1. Rotates with the input shaft 1. Further, the power roller 11 (see FIG. 5) is rotatable between the inner side surfaces (concave surfaces) 2a, 2a of the input side discs 2, 2 and the inner side surfaces (concave surfaces) 3a, 3a of the output side discs 3, 3. Is sandwiched between.

  A step 2b is provided on the inner peripheral surface 2c of the input disk 2 located on the right side in FIG. 4, and the step 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step 2b. At the same time, the back surface (the right surface in FIG. 4) of the input side disk 2 is abutted against the loading nut 9. Thereby, the displacement of the input side disk 2 in the direction of the axis O with respect to the input shaft 1 is substantially prevented. Further, a disc spring 8 is provided between the cam plate 7 and the flange 1d of the input shaft 1, and this disc spring 8 is a concave surface 2a, 2a, 3a of each disk 2, 2, 3, 3. , 3a and the contact surface between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 are applied with a pressing force.

  FIG. 5 is a cross-sectional view taken along line BB in FIG. As shown in FIG. 5, a pair of trunnions 15, 15 that swing around a pair of pivots 14, 14 that are twisted with respect to the input shaft 1 are provided inside the casing 50. In addition, illustration of the input shaft 1 is abbreviate | omitted in FIG. Each trunnion 15, 15 is formed at a pair of ends formed in the longitudinal direction (vertical direction in FIG. 5) of the support plate 16 that supports the power roller 11 in a state of being bent toward the inner side of the support plate 16. It has the bent wall parts 20 and 20. The bent wall portions 20 and 20 form concave pocket portions P for accommodating the power rollers 11 in the trunnions 15 and 15. Further, the pivot shafts 14 and 14 are concentrically provided on the outer side surfaces of the bent wall portions 20 and 20, respectively.

  A circular hole 21 is formed in the central portion of the support plate portion 16, and the base end portion 23 a of the displacement shaft 23 is supported in the circular hole 21. Then, by swinging each trunnion 15, 15 about each pivot 14, 14, the inclination angle of the displacement shaft (shaft) 23 supported at the center of each trunnion 15, 15 can be adjusted. It has become. In addition, each power roller 11 is rotatably supported via a radial needle bearing 99 around the distal end portion 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, 15. 11 is sandwiched between the input disks 2 and 2 and the output disks 3 and 3. In addition, the base end part 23a and the front-end | tip part 23b of each displacement shaft 23 and 23 are mutually eccentric.

  The pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable and displaceable in the axial direction (vertical direction in FIG. 5) with respect to the pair of yokes 23A and 23B, respectively. The horizontal movement of the trunnions 15 and 15 is restricted by 23B. Each yoke 23A, 23B is formed in a rectangular shape by pressing or forging a metal such as steel. Four circular support holes 18 are provided at the four corners of each of the yokes 23 </ b> A and 23 </ b> B, and the pivot shafts 14 provided at both ends of the trunnion 15 swing through the radial needle bearings 30. It is supported freely. In addition, a circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (left and right direction in FIG. 4). The inner peripheral surface of the locking hole 19 is a cylindrical surface, and is a spherical post. 64 and 68 are fitted inside. That is, the upper yoke 23A is swingably supported by the spherical post 64 supported by the casing 50 via the fixing member 52, and the lower yoke 23B is supported by the spherical post 68 and the drive for supporting the same. The upper valve body (cylinder body) 61 of the cylinder 31 is swingably supported.

  The displacement shafts 23 and 23 provided in the trunnions 15 and 15 are provided at positions 180 degrees opposite to the input shaft 1. Further, the direction in which the distal end portion 23b of each of the displacement shafts 23, 23 is eccentric with respect to the base end portion 23a is the same direction as the rotational direction of both the disks 2, 2, 3, 3 (in FIG. (Reverse direction). Further, the eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 is disposed. Accordingly, the power rollers 11 and 11 are supported so that they can be slightly displaced in the longitudinal direction of the input shaft 1. As a result, even if each power roller 11, 11 tends to be displaced in the axial direction of the input shaft 1 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 an excessive force to the member.

  Further, between the outer surface of the power roller 11 and the inner surface of the support plate portion 16 of the trunnion 15, a thrust ball bearing 24 that is a thrust rolling bearing, and a thrust needle bearing, in order from the outer surface side of the power roller 11. 25. Among these, the thrust ball bearing 24 supports the rotation of each power roller 11 while supporting the load in the thrust direction applied to each power roller 11. Each of such thrust ball bearings 24 includes a plurality of balls (hereinafter referred to as rolling elements) 26, 26, an annular retainer 27 that holds the rolling elements 26, 26 in a freely rolling manner, And an annular outer ring 28. Further, the inner ring raceway of each thrust ball bearing 24 is formed on the outer side surface (large end surface) of each power roller 11, and the outer ring raceway is formed on the inner side surface of each outer ring 28.

  The thrust needle bearing 25 is sandwiched between the inner surface of the support plate portion 16 of the trunnion 15 and the outer surface of the outer ring 28. Such a thrust needle bearing 25 supports the thrust load applied to each outer ring 28 from the power roller 11, while the power roller 11 and the outer ring 28 swing around the base end portion 23 a of each displacement shaft 23. Allow.

  Further, drive rods (trunnion shafts) 29 and 29 are provided at one end portions (lower end portions in FIG. 5) of the trunnions 15 and 15, respectively, and a drive piston ( Hydraulic pistons) 33, 33 are fixed. The drive pistons 33 and 33 are oil-tightly fitted in a drive cylinder 31 constituted by an upper valve body (cylinder body) 61 and a lower valve body (cylinder body) 62, respectively. The drive pistons 33 and 33 and the drive cylinder 31 constitute a drive device 32 that displaces the trunnions 15 and 15 in the axial direction of the pivots 14 and 14 of the trunnions 15 and 15.

  In the case of the toroidal continuously variable transmission configured as described above, the rotation of the input shaft 1 is transmitted to the input side disks 2 and 2 via the pressing device 12. Then, the rotation of the input side disks 2 and 2 is transmitted to the output side disks 3 and 3 via the pair of power rollers 11 and 11, and the rotation of the output side disks 3 and 3 is further transmitted to the output gear 4. Is taken out more.

  When changing the rotational speed ratio between the input shaft 1 and the output gear 4, the pair of drive pistons 33, 33 are displaced in opposite directions. As the drive pistons 33 and 33 are displaced, the pair of trunnions 15 and 15 are displaced in directions opposite to each other. For example, the power roller 11 on the left side in FIG. 5 is displaced to the lower side in the figure, and the power roller 11 on the right side in the figure is displaced to the upper side in the figure. As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 act on contact portions of the input side disks 2 and 2 and the inner side surfaces 2a, 2a, 3a and 3a of the output side disks 3 and 3, respectively. The direction of the tangential force changes. As the force changes, the trunnions 15 and 15 swing (tilt) in opposite directions around the pivots 14 and 14 pivotally supported by the yokes 23A and 23B.

  As a result, the contact position between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a changes, and the gear ratio between the input shaft 1 and the output gear 4 changes. Further, when the torque transmitted between the input shaft 1 and the output gear 4 fluctuates and the amount of elastic deformation of each component changes, the power rollers 11 and 11 and the outer rings attached to the power rollers 11 and 11 will be described. 28 and 28 slightly rotate around the base end portions 23a and 23a of the displacement shafts 23 and 23, respectively. Since the thrust needle bearings 25 and 25 exist between the outer side surfaces of the outer rings 28 and 28 and the inner side surfaces of the support plate portions 16 constituting the trunnions 15 and 15, respectively, the rotation is performed smoothly. Is called. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 23, 23 can be small.

  By the way, in the toroidal-type continuously variable transmission having the above-described configuration, the yokes 23A and 23B for supporting the pivot shaft 14 of the trunnion 15 so as to be swingable and displaceable in the axial direction have been conventionally known in various structures. In general, however, when the gear is shifted, it oscillates around the spherical posts 64 and 68 so that, for example, one trunnion 15 (for example, the right trunnion 15 in FIG. 5) is displaced upward. Accordingly, the other trunnions 15 (for example, the left trunnion 15 in FIG. 5) are displaced downward so that the movements of the pair of trunnions 15 facing each other in the same cavity are synchronized like a seesaw. It has a function of displacing in the reverse direction.

  For example, when the left drive piston 33 in FIG. 5 is displaced downward in the figure and the right drive piston 33 is displaced upward in the figure, the trunnions 15 and 15 coupled to these drive pistons 33 are mutually connected. Displaced in the opposite direction (the left trunnion 15 is displaced downward and the right trunnion 15 is displaced upward), whereby the upper yoke 23A tilts (oscillates) so that the right side is up. ). Similarly, the lower yoke 23B tilts (swings) in the same direction as the upper yoke 23A. Conversely, when the left drive piston 33 in FIG. 5 is displaced upward in the figure and the right drive piston 33 is displaced downward in the figure, the upper yoke 23A is inclined in a direction in which the left side is upward. Similarly, the lower yoke 23B tilts (swings) in the same direction as the upper yoke 23A.

  The problem here is that depending on the hydraulic control of the drive piston 33, the end surface 33a of the drive piston 33 and the end surface 61a of the drive cylinder 31 (61) may come into contact with each other at the time of the above shift. That is, the drive piston 33 tilts together with the trunnion 15 and the power roller 11 while being in contact with each other. When such a situation occurs, there is a concern that the contact portion between the end faces 33a and 61a may be worn, or that a bolt for fixing the drive piston 33 may be loosened due to frictional resistance due to contact. Therefore, for example, in Patent Document 1 and Patent Document 2, it is proposed to provide a displacement restricting means that restricts the displacement of the yokes 23A and 23B in the tilt axis direction (and thus restricts the axial displacement of the trunnion). Yes. Specifically, in Patent Document 1, a cube-shaped stopper is provided integrally with the valve body 61 as the displacement restricting means. Moreover, in patent document 2, the stopper surface as said displacement control means is provided in the yoke support member.

JP 2004-84712 A JP 2008-138762 A

  However, when the stopper is provided integrally with the valve body 61 as disclosed in Patent Document 1, it is difficult to reduce the weight of the valve body 61 (62). That is, in general, since the material for forming the yokes 23A and 23B whose displacement is to be restricted is iron, the stopper as the displacement restricting means must be made of a hard material that can abut against the iron material and restrict its movement. Therefore, the valve body 61 (62) integrated with the stopper also needs to be formed of such a hard material, and as a result, it is inevitably difficult to reduce the weight of the valve body 61 (62).

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a toroidal continuously variable transmission capable of regulating the tilt displacement (swing) of the yoke while reducing the weight of the valve body.

In order to achieve the above object, the invention according to claim 1 is directed to an input side disk and an output side disk that are supported concentrically and rotatably with the respective inner surfaces facing each other, and A power roller sandwiched between the input-side disk and the output-side disk; and the power roller tilted about a pivot that is twisted with respect to a central axis of the input-side disk and the output-side disk. A trunnion that rotatably supports each of the trunnions, a hydraulically actuated drive device that displaces each trunnion in the axial direction of the pivot, and each pivot of each trunnion that is tiltable and axially displaceable. A toroidal-type stepless unit comprising a pair of yokes that oscillate by the displacement of the trunnion and a valve body that constitutes a hydraulic cylinder of the drive device In the speed machine, the valve body is provided with a stopper separately from the valve body for regulating the swing of the yoke due to the axial displacement of the trunnion, and the material forming the stopper forms the valve body hard der than the material is,
The stopper has a cylindrical shape,
A support member for supporting the stopper with respect to the valve body is further provided, wherein the cylindrical stopper is coaxially inserted into a circular mounting hole of the valve body, and the support member is a central axis of the stopper. The stopper is supported at a position eccentric from the center .

  In the first aspect of the present invention, since the stopper is provided separately from the valve body, the valve body forming material is different from the stopper forming material and does not depend on the yoke forming material. That is, the material for forming the stopper can be made harder than the material for forming the valve body, and the valve body can be formed of a lightweight material. In other words, according to the above configuration, the tilt displacement (swing) of the yoke can be regulated while reducing the weight of the valve body.

Further , since the stopper has a cylindrical shape, when the stopper is inserted into the mounting hole of the valve body, it is not necessary to position the stopper in accordance with the shape of the mounting hole (as in Patent Document 1 described above). If the stopper has a cubic shape, it is necessary to position the stopper according to the shape of the mounting hole during insertion.) Also, since the mounting hole is processed in a circular shape, high-precision and easy processing is possible. Can be implemented.

In addition , the cylindrical stopper is inserted coaxially into the circular mounting hole of the valve body, and the support member that supports the stopper with respect to the valve body supports the stopper at a position eccentric from the central axis of the stopper. It is possible to easily restrict the rotation of the stopper without providing a separate means for restricting the rotation.

According to a second aspect of the present invention, in the first aspect of the present invention, the valve body is made of aluminum and the stopper is made of iron.

In the second aspect of the invention, the object of regulating the tilt displacement (swing) of the yoke while reducing the weight of the valve body can be achieved at low cost and effectively.

  According to the toroidal type continuously variable transmission of the present invention, the stopper for restricting the swing of the yoke is provided separately from the valve body, and the material forming the stopper is harder than the material forming the valve body. Therefore, it is possible to regulate the tilt displacement (swing) of the yoke while reducing the weight of the valve body.

(A) is a top view of a valve body which has a separate stopper concerning an embodiment of the present invention, and (b) is a sectional view which meets an AA line of (a). (A) is a sectional view of the yoke and the valve body in a state before tilting (swinging), and (b) is a sectional view of the yoke and the valve body in a state after tilting (swinging). (A) is sectional drawing of the valve body which has a stopper which concerns on a 1st modification, (b) is sectional drawing of the valve body which has a stopper which concerns on a 2nd modification. It is sectional drawing which shows an example of the specific structure of the half toroidal type continuously variable transmission conventionally known. It is sectional drawing which follows the AA line of FIG.

Embodiments of the present invention will be described below with reference to the drawings.
The feature of the present invention lies in the structure for restricting the displacement of the trunnion in the direction of the tilt axis, and the other configurations and functions are the same as the conventional configurations and functions described above. Only the characteristic part of FIG. 5 will be referred to, and other parts will be simply described with the same reference numerals as those in FIGS.

  1 and 2 show an embodiment of the present invention. As shown in these drawings, the valve body 61 (62) constituting the hydraulic cylinder of the hydraulically actuated drive device 32 (see FIG. 5) has a yoke 23B as a result of axial displacement of the trunnion 15 (see FIG. 5). At least one stopper 200 that restricts swinging (in the figure, two facing each other) is provided separately from the valve body 61 (62).

  Each stopper 200 has a cylindrical shape, and a part of the stopper 200 is coaxially inserted into the circular mounting hole 215 of the valve body 61 (62). Further, in order to support the stopper 200 with respect to the valve body 61 (62), a support member 210 made of a bolt or the like is inserted into the through hole 205 of the valve body 61 (62). The through hole 205 communicates with the attachment hole 215, and the central axis thereof is eccentric with respect to the central axis of the attachment hole 215. Further, the stopper 200 inserted coaxially into the mounting hole 215 is formed with a support hole 200 a that is positioned eccentrically from the central axis of the stopper 200 with an eccentricity corresponding to the eccentricity of the through hole 205 with respect to the mounting hole 215. ing. Therefore, by inserting the support member 210 inserted through the through hole 205 into the support hole 200a of the stopper 200, the stopper 200 is supported by the support member 210 at a position eccentric from the central axis, and at the same time, the valve body 61 ( 62) is restricted. The support member 210 may be screwed and fixed to the valve body 61 (62), or may be screwed and fixed to the stopper 200.

  Further, in the present embodiment, the material forming the stopper 200 is set to be harder than the material forming the valve body 61 (62) in connection with the stopper 200 being provided separately from the valve body 61 (62). Has been. Specifically, for example, the valve body 61 (62) is made of aluminum, and the stopper 200 is made of iron. Of course, any material can be selected as long as the material forming the stopper 200 is set to be harder than the material forming the valve body 61 (62).

  2A is a sectional view of the yoke and the valve body before tilting (swinging), and FIG. 2B is a sectional view of the yoke and the valve body after tilting (swinging). Respectively. As illustrated, the stopper 200 can regulate the swing of the yoke 23B while being stably supported by the valve body 61 (62).

  As described above, according to the present embodiment, since the stopper 200 is provided separately from the valve body 61 (62), the formation material of the valve body 61 (62) is different from the formation material of the stopper 200. Moreover, it is not necessary to depend on the material for forming the yoke 23B. That is, the material forming the stopper 200 can be made harder than the material forming the valve body 61 (62), and the valve body 61 (62) can be formed from a light material. That is, according to the present embodiment, the tilt displacement (swing) of the yoke 23B can be regulated while reducing the weight of the valve body 61 (62).

  Further, according to the present embodiment, since the stopper 200 has a cylindrical shape, when the stopper 200 is inserted into the mounting hole 215 of the valve body 61 (62), the stopper 200 is matched to the shape of the mounting hole 215. There is no need to position the. In addition, since the mounting hole 215 is processed into a circular shape, high-precision and easy processing can be performed.

  In addition, according to the present embodiment, the cylindrical stopper 200 is coaxially inserted into the circular mounting hole 215 of the valve body 61 (62), and the stopper 200 is positioned at a position eccentric from the central axis of the stopper 200. Therefore, it is possible to easily restrict the rotation of the stopper 200 without providing a separate means for restricting the rotation of the stopper 200.

  The present invention is not limited to the above-described embodiments, and can be implemented with various modifications without departing from the scope of the invention. For example, in the above-described embodiment, the stopper 200 has a cylindrical shape, but the stopper 200 can have an arbitrary shape such as a cube, a rectangular parallelepiped, or a sphere. That is, the stopper 200 may have a spherical surface that contacts the yoke 23B as shown in FIG. 3 (a), or the entire surface thereof is spherical as shown in FIG. 3 (b). May be.

  The present invention can be applied to various half-toroidal continuously variable transmissions such as a single cavity type and a double cavity type.

2 Input side disk 3 Output side disk 11 Power roller 14 Axis 15 Trunnion 23A, 23B Yoke 32 Drive device 61, 62 Valve body 200 Stopper 210 Support member 215 Mounting hole

Claims (2)

An input side disk and an output side disk that are supported concentrically and rotatably with their inner side surfaces facing each other, and a power roller sandwiched between the input side disk and the output side disk A trunnion that tilts about a pivot that is twisted with respect to a central axis of the input-side disk and the output-side disk and that rotatably supports the power roller; and each trunnion that is a pivot axis. A hydraulically actuated drive device that displaces in the direction, a pair of yokes that respectively support the pivots of the trunnions so as to be tiltable and axially displaceable, and swing by the displacement of the trunnions; In a toroidal continuously variable transmission comprising a valve body that constitutes a hydraulic cylinder of
The valve body is provided with a stopper for regulating the swing of the yoke accompanying the axial displacement of the trunnion, which is provided separately from the valve body, and the material forming the stopper is more than the material forming the valve body. hard der is,
The stopper has a cylindrical shape,
A support member for supporting the stopper with respect to the valve body is further provided, wherein the cylindrical stopper is coaxially inserted into a circular mounting hole of the valve body, and the support member is a central axis of the stopper. A toroidal-type continuously variable transmission, characterized in that the stopper is supported at a position eccentric from the center . The toroidal continuously variable transmission according to claim 1, wherein the valve body is made of aluminum and the stopper is made of iron.

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