JP2013108511A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission capable of supplying lubricating oil efficiently to power rollers, achieving miniaturization and reduction in manufacturing cost, and widening the degree of flexibility of design.SOLUTION: In this toroidal type continuously variable transmission, pumps 210 for supplying the lubricating oil to thrust ball bearings 24 are incorporated in support plates 16 of trunnions 15. The pumps 210 are disposed in housings 240 in which lubricating oil paths 200a, 200b are formed and assembled desirably detachably at the inner surface side of the support plates 16 facing pockets P as integral pump units 200. The pumps 210 are driven by power rollers 11.

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. 2 and 3 (two cavities 221 and 222 are shown in FIG. 2). As shown in FIG. 2, 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, a power roller 11 (FIG. 3) is provided between the inner side surfaces (concave surfaces) 2a and 2a of the input side disks 2 and 2 and the inner side surfaces (concave surface; also referred to as a traction surface) 3a and 3a of the output side disks 3 and 3. (See below) is rotatably held.

  A step 2b is provided on the inner peripheral surface 2c of the input disk 2 located on the right side in FIG. 2, 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 (right surface in FIG. 2) 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. 3 is a cross-sectional view taken along line EE in FIG. As shown in FIG. 3, 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 FIG. 3, the input shaft 1 is not shown. Each trunnion 15, 15 is formed at a pair of ends formed in the longitudinal direction (vertical direction in FIG. 3) 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, a displacement shaft (supporting the power roller 11 rotatably) supported by the center of each trunnion 15, 15. The inclination angle of the shaft 23 can be adjusted. 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.

  Further, the pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable and axially displaceable 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. Further, a circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (the left-right direction in FIG. 2), and the inner peripheral surface of the locking hole 19 is a cylindrical surface. 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 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 and 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 and 3 (up and down in FIG. 3). (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, driving rods (trunnion shafts) 29 and 29 are provided at one end portions (lower end portions in FIG. 3) of the trunnions 15 and 15, respectively, and a driving piston ( Hydraulic pistons) 33, 33 are fixed. Each of these drive pistons 33 and 33 is oil-tightly fitted in a drive cylinder 31 constituted by an upper cylinder body 61 and a lower cylinder body 62. 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. It 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 of FIG. 3 is displaced downward in the figure, and the power roller 11 on the right side of FIG. 3 is displaced upward 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 (traction 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. To do. 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 power transmission between the power roller 11 and the input / output side disks 2 and 3 is caused by a traction force through an oil film to prevent damage to the surface of these members. (Hereinafter, the interface between the power roller 11 formed by the oil film and the input / output side disks 2 and 3 is referred to as a traction surface. In this specification, for convenience, the peripheral surface 11a of the power roller 11 is referred to as a traction surface. May be referred to as a traction surface). Therefore, it is necessary to supply a sufficient amount of lubricating oil (traction oil) that can form an oil film for transmitting torque in a non-contact manner on the traction surface formed between the power roller 11 and the input / output side disk. is there.

  Furthermore, in the power transmission between the discs 2 and 3 and the power roller 11 through such an oil film, the contact portion between the discs 2 and 3 and the power roller 11 and the bearing portion of the power roller 11 (for example, a thrust ball bearing) 24 etc.), so that heat is generated. Therefore, it is necessary to sufficiently supply the lubricating oil to the bearing portion of the power roller 11.

  Conventionally, supply of lubricating oil to the thrust ball bearing 24 and the like is performed by a pump that is driven by rotation on the input side of the engine as disclosed in, for example, Patent Document 1 and Patent Document 2. Then, the lubricating oil supplied by the pump is sent to the thrust ball bearing 24 and the like through the oil passages processed in the trunnion 15 and the displacement shaft 23 via the control valve and the shift control valve.

JP 2002-327836 A JP 2000-9197 A

  However, lubricating oil is sent from the pump driven by rotation on the input side of the engine to the thrust ball bearing 24 and the like through the oil passages processed into the trunnion 15 and the displacement shaft (support shaft) 23 via the control valve and the shift control valve. Several problems arise with the lubricating oil supply configuration. That is, since it is necessary to provide an oil passage in the speed change control valve or the like, the degree of freedom in designing the control line and the hydraulic line of the hydraulic loader line is reduced. Further, since it is necessary to form an oil passage (hole) in the displacement shaft 23 or the like, the diameter of the displacement shaft 23 is inevitably increased, and as a result, the size of the power roller portion is also increased. Furthermore, since burrs are generated by such drilling, a great deal of labor is required for quality assurance. In addition, since the oil passage is formed long over various parts, the number of parts such as a seal ring and an O-ring increases, and the manufacturing cost increases.

  The present invention has been made in view of the above circumstances, and can efficiently supply lubricating oil to the power roller portion, and can achieve downsizing and reduction in manufacturing cost, and can widen design freedom. An object is to provide a toroidal type continuously variable transmission.

  In order to achieve the above object, the present invention provides an input disk and an output disk that are supported concentrically and rotatably with their inner surfaces facing each other, and are sandwiched between these two disks. A power roller, 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 the power roller A bearing that supports the rotation of the power roller while supporting the applied load in the thrust direction, and the bearing is rotatably held by a cage between an inner ring and an outer ring formed by the power roller. In a toroidal continuously variable transmission including a plurality of rolling elements, a pump for supplying lubricating oil to the bearing is incorporated in the trunnion, and the pump There characterized in that it adapted to be driven by the power rollers.

  According to the above configuration, the lubricating oil supply pump is built in the trunnion, and the pump is driven by the power roller, so that the drilling of the lubricating oil passage for various control valves is simplified, and the transmission control valve There is no need to provide an oil passage. Therefore, the generation of burrs associated with drilling can be suppressed, quality assurance measures can be simplified, and the degree of freedom in designing the hydraulic lines of the control line and hydraulic loader line can be expanded. In addition, the number of parts such as seal rings and O-rings can be reduced by reducing the number of oil passages (therefore, the control valve and the like can be downsized (thinned)), and the manufacturing cost can be reduced. That is, it is possible to efficiently supply lubricating oil to the power roller portion, to reduce the size and to reduce the manufacturing cost, and to increase the degree of design freedom.

In the above configuration, it is preferable that the pump is configured as a unit including an oil passage for supplying lubricating oil and is detachably incorporated in the trunnion. If comprised in this way, assembly workability | operativity will become favorable and is beneficial.
In the above configuration, a second bearing is provided between the outer ring and a support shaft that passes through the outer ring and rotatably supports the power roller, and the second bearing communicates with the oil passage of the unit. The lubricating oil may be supplied from the oil passage of the unit to the bearing through the second bearing. This eliminates the need to form oil passages (holes) in the support shaft and the like, inevitably reducing the diameter of the support shaft, and as a result, reducing the size of the power roller portion (variator portion).
Furthermore, in the said structure, it is preferable that a filter is provided in the upstream or downstream oil path of the said pump. Thereby, it is possible to supply a lubricating oil free of contaminants, which is beneficial.

  According to the toroidal continuously variable transmission of the present invention, the pump for supplying the lubricating oil to the power roller portion is built in the trunnion, and the pump is driven by the power roller, so that the lubricating oil can be efficiently supplied to the power roller portion. In addition, the size and the manufacturing cost can be reduced, and the degree of freedom in design can be expanded.

It is sectional drawing of the principal part of the toroidal type continuously variable transmission which concerns on embodiment of this invention. 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 supply form of the lubricating oil, and other configurations and operations are almost the same as the conventional configuration and operation described above. Therefore, in the following, only the features of the present invention will be referred to. Other parts will be described briefly with the same reference numerals as those in FIGS.

  FIG. 1 shows an embodiment of the present invention. As shown in the figure, in the toroidal type continuously variable transmission of the present embodiment, a pump 210 for supplying lubricating oil to the thrust ball bearing 24 is built in the support plate portion 16 of the trunnion 15. In particular, in this embodiment, the pump 210 is disposed in the housing 240 in which the lubricating oil passages 200a and 200b are formed, and faces the pocket portion P as an integral pump unit 200 (opposite the end of the support shaft 23). It is preferably detachably assembled to the inner surface side of the support plate portion 16. In this example, the support shaft 23 that rotatably supports the power roller 1 is formed integrally with the power roller 11 and penetrates the outer ring 28.

  Here, the pump 210 is configured as a positive displacement pump interposed between a first lubricating oil passage 200 a and a second lubricating oil passage 200 b provided in the housing 240, and is driven by the power roller 11. It has become so. Specifically, for example, a connecting shaft portion 23e that is connected to the driving shaft of the pump 210 is provided at the end of the support shaft 23, and the connecting shaft portion 23e rotates as the power roller 11 rotates, The pump 210 is driven. The second lubricating oil passage 200b located on the discharge side of the pump 210 communicates with the radial needle bearing 99 (more precisely, the gap between the outer ring 28 provided with the radial needle bearing 99 and the support shaft 23). In addition, the first lubricating oil passage 200 a located on the suction side of the pump 210 communicates with the first lubricating oil supply passage 112 provided in the trunnion 15. The first lubricating oil supply path 112 communicates with a second lubricating oil supply path 110 formed in the drive rod 29, and the second lubricating oil supply path 110 is connected to a lubricating oil supply source (not shown). .

  Therefore, in such a configuration, when the pump 210 is driven by the power roller 11, the lubricating oil from a lubricating oil supply source (not shown) is converted into the first and second lubricating oils as indicated by arrows in FIG. It flows into the pump unit 200 through the supply passages 110 and 112, and through the first and second lubricating oil passages 200a and 200b of the pump unit 200, the end of the radial needle bearing (second bearing) 99 is more accurate. Flows into the end of the gap between the outer ring 28 provided with the radial needle bearing 99 and the support shaft 23. The lubricating oil flowing into the end of the radial needle bearing 99 reaches the thrust ball bearing 24 via the radial needle bearing 99. In this case, contaminants in the lubricating oil are removed from the upstream or downstream oil passage of the pump 210 (for example, the end portion of the lubricating oil supply passage 110 (the end portion on the drive rod (trunnion shaft) 29 side)). A filter (not shown) is preferably provided.

  As described above, according to the present embodiment, the lubricating oil supply pump 210 is built in the trunnion 15 and the pump 210 is driven by the power roller 11. Is simplified, and there is no need to provide an oil passage in the speed change control valve. Therefore, the generation of burrs associated with drilling can be suppressed, quality assurance measures can be simplified, and the degree of freedom in designing the hydraulic lines of the control line and hydraulic loader line can be expanded. In addition, the number of parts such as seal rings and O-rings can be reduced by reducing the number of oil passages (therefore, the control valve and the like can be downsized (thinned)), and the manufacturing cost can be reduced. That is, it is possible to efficiently supply lubricating oil to the power roller portion, to reduce the size and to reduce the manufacturing cost, and to increase the degree of design freedom.

  Further, in this embodiment, the pump 210 is configured as a unit 200 including oil passages 200a and 200b for supplying lubricating oil, and is detachably incorporated into the trunnion 15, so that assembly workability is improved and beneficial. .

  In the present embodiment, a radial needle bearing (radial bearing) 99 is provided between the outer ring 28 and a support shaft 23 that passes through the outer ring 28 and rotatably supports the power roller 11. The lubricating oil is supplied to the thrust ball bearing 24 through the radial needle bearing 99 from the oil passage of the unit through the radial needle bearing 99 so as to face the oil passage of the unit. There is no need to form a path (hole). Therefore, the diameter of the support shaft 23 can inevitably be reduced, and as a result, the power roller portion can be reduced in size.

  Furthermore, in this embodiment, since the filter is provided in the oil path on the upstream side or the downstream side of the pump 210, it is beneficial to supply lubricating oil free of contaminants.

  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 Pivot 15 Trunnion 23 Support shaft 24 Thrust ball bearing (bearing)
26 Rolling element 27 Cage 28 Outer ring 99 Radial needle bearing (second bearing)
200 Pump unit 200a, 200b Lubricating oil passage 210 Pump

Claims (4)

An input side disk and an output side disk that are supported concentrically and rotatably with the inner side surfaces facing each other, a power roller sandwiched between both the disks, the input side disk, and the A trunnion that tilts around a pivot that is twisted with respect to the central axis of the output disk and that rotatably supports the power roller, and the power roller while supporting a load in the thrust direction applied to the power roller A toroidal-type continuously variable transmission including a plurality of rolling elements that are rotatably held by a cage between an inner ring and an outer ring formed by the power roller. In
A toroidal continuously variable transmission characterized in that a pump for supplying lubricating oil to the bearing is built in the trunnion, and the pump is driven by the power roller.   The toroidal continuously variable transmission according to claim 1, wherein the pump is configured as a unit including an oil passage for supplying lubricating oil and is detachably incorporated in the trunnion.   A second bearing is provided between the outer ring and a support shaft that passes through the outer ring and rotatably supports the power roller, and the second bearing communicates with an oil passage of the unit. The toroidal continuously variable transmission according to claim 1 or 2, wherein lubricating oil is supplied to the bearing from the road through the second bearing.   The toroidal continuously variable transmission according to any one of claims 1 to 3, wherein a filter is provided in an oil passage upstream or downstream of the pump.

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