JP5772026B2 - 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 an automobile transmission is configured as shown in FIGS. As shown in FIG. 3, 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. 4) is rotatable between the inner side surfaces (concave surfaces) 2a, 2a of the input side disks 2, 2 and the inner side surfaces (concave surfaces) 3a, 3a of the output side disks 3, 3. Is sandwiched between.

  A step portion 2b is provided on the inner peripheral surface 2c of the input side disk 2 located on the right side in FIG. 3, and the step portion 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step portion 2b. At the same time, the back surface (right surface in FIG. 3) 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.

  4 is a cross-sectional view taken along line AA in FIG. As shown in FIG. 4, a pair of trunnions 15, 15 that swing about a pair of pivots 14, 14 that are twisted with respect to the input shaft 1 are provided inside the casing 50. In FIG. 4, the input shaft 1 is not shown. Each trunnion 15, 15 is a pair of ends formed in the longitudinal direction (vertical direction in FIG. 4) of the support plate portion 16 that supports the power roller 11 in a state of being bent toward the inner surface side of the support plate portion 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. 4) 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 (the left-right direction in FIG. 3), 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, 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, driving rods (trunnion shafts) 29 and 29 are provided at one end portions (lower end portions in FIG. 4) 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. 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. 4 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 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.

  Conventionally, supply of lubricating oil to the traction surface of the power roller 11 is performed through an oil passage formed in the trunnion and extending to the traction surface of the power roller 11 as disclosed in, for example, Patent Documents 1 to 3 and the like. .

JP 2007-154952 A JP 2010-25280 A JP-A-8-28646

  However, since the power roller rotates at a high speed, even if the lubricating oil is discharged and brought into contact with the power roller, the lubricating oil is immediately repelled by the rotating power roller. Therefore, in order to sufficiently cool the power roller, it is necessary to discharge a large amount of lubricating oil toward the power roller.

  Generally, since the amount of lubricating oil is proportional to the input torque and the engine speed, the amount of lubricating oil increases as the input torque increases. Therefore, in the high torque region, that is, in the region where the transmission power is large, the amount of lubricating oil increases, and the dynamic torque due to oil agitation resistance increases.

  The present invention has been made in view of the above circumstances, and a toroidal continuously variable transmission capable of efficiently and effectively cooling a power roller without increasing the amount of lubricating oil discharged toward the power roller. The purpose is to provide.

In order to achieve the object, the invention according to claim 1 is directed to a power provided between an input side disk coupled to an input shaft that receives a rotational force and rotates integrally with the input shaft, and the input side disk. An output-side disk that receives the rotational force of the input-side disk through a roller at a predetermined speed ratio, and tilts about a pivot that is twisted with respect to the central axis of the input-side disk and the output-side disk; And a trunnion that rotatably supports the power roller, wherein the trunnion supports the power roller in a toroidal continuously variable transmission in which power transmission between the power roller and the disk is performed via an oil film. And a support plate portion that is bent to the power roller side at both ends of the support plate portion in the axial direction of the pivot, and the power roller is sandwiched therebetween. And a pair of bent wall portions with the pivots provided on the outer surface, and the pair of bent wall portions transmit power via an oil film to the disk. According to the magnitude of the power transmitted from the input side disk to the output side disk via the power roller, a lubricating oil hole is provided for discharging lubricating oil to the traction surface of the power roller. The direction of lubricating oil discharge to the traction surface of the power roller is changed ,
The transmission power has a relatively small low torque region and a relatively large high torque region, and in the low torque region, the discharge direction of the lubricating oil from the lubricating oil hole is directed to the rotation direction of the power roller. It is characterized by.

  In the first aspect of the invention, in view of the fact that the amount of lubricating oil is proportional to the input torque and the engine speed, the magnitude of the power transmitted from the input side disk to the output side disk via the power roller. The direction of the lubricating oil discharged to the traction surface of the power roller can be changed accordingly, so that the power roller can be efficiently operated without increasing the amount of lubricating oil discharged (spouted) toward the power roller. And it can cool (lubricate) effectively.

Also, in the low torque region, the discharge direction of the lubricating oil from the lubricating oil hole is directed to the rotation direction of the power roller (the oil is lubricated in the order of rotation of the power roller). Can be reduced.
According to a second aspect of the present invention, an input side disk coupled to an input shaft that receives rotational force and rotates integrally with the input shaft and a power roller provided between the input side disk and the input side disk are provided. An output-side disk that receives the rotational force of the disk at a predetermined speed ratio, and tilts about a pivot that is twisted with respect to the central axis of the input-side disk and the output-side disk, and the power roller is rotatable. A toroidal continuously variable transmission in which power transmission between the power roller and the disk is performed through an oil film.
The trunnion is provided on a support plate portion that supports the power roller, and is bent to the power roller side at both ends in the axial direction of the pivot of the support plate portion, and the power roller is sandwiched between the trunnions. A pair of bent wall portions that are opposed to each other on the inner surface and provided with the pivot on the outer surface, and the pair of bent wall portions transmit power to the disk via an oil film. Lubricating oil holes are provided for discharging lubricating oil to the traction surface of the power roller, and the power according to the magnitude of power transmitted from the input disk to the output disk via the power roller. The direction of lubricating oil discharge to the traction surface of the roller can be changed,
The transmission power has a relatively small low torque region and a relatively large high torque region, and in the high torque region, the discharge direction of the lubricating oil from the lubricating oil hole is opposite to the rotation direction of the power roller. It is characterized by heading in the direction.

The invention according to claim 3 is the invention according to claim 1, wherein the invention has a low torque region in which the transmission power is relatively small and a high torque region in which the transmission power is relatively large. The discharge direction of the lubricating oil from the lubricating oil hole is directed in the direction opposite to the rotation direction of the power roller.

In the invention according to claim 2 or claim 3, in the high torque region, the cooling performance is regarded as important, and the discharge direction of the lubricating oil from the lubricating oil hole is directed in the direction opposite to the rotation direction of the power roller. (Lubrication is discharged from the reverse rotation order of the power roller), so that the relative lubrication speed (the discharge speed of the lubricating oil with respect to the rotation speed of the power roller) is increased, and the cooling effect can be further enhanced.

  According to the toroidal type continuously variable transmission of the present invention, the power roller can be efficiently and effectively cooled without increasing the amount of lubricating oil discharged toward the power roller.

It is principal part sectional drawing of the toroidal type continuously variable transmission which concerns on embodiment of this invention. (A) is a plan view of the vicinity of the traction surface showing the direction of lubricant discharge in the low torque region of the toroidal type continuously variable transmission of FIG. 1, and (b) is a high torque region of the toroidal type continuously variable transmission of FIG. It is a top view of the traction surface vicinity which shows the discharge direction of the lubricating oil. 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 form of supplying the lubricating oil to the traction surface, and other configurations and operations are the same as the conventional configurations and operations described above. Therefore, only the features of the present invention will be mentioned below. However, the other portions are simply described with the same reference numerals as those in FIGS.

  FIG. 1 shows a cross-sectional view of a main part of a toroidal type continuously variable transmission according to an embodiment of the present invention. Similar to the conventional structure described above, the trunnion 15 of the toroidal-type continuously variable transmission according to the present embodiment also includes a support plate portion 16 that supports the power roller 11 and axial ends of the pivot 14 of the support plate portion 16. A pair of bent wall portions 20 and 20 are provided which are bent on the power roller 11 side and are opposed to each other with the inner surface facing each other with the power roller 11 sandwiched therebetween and a pivot shaft 14 provided on the outer surface. A plurality of lubricating oils for discharging lubricating oil to the traction surface 11a of the power roller 11 that transmits power to the pair of bent walls 20 and 20 via the oil film between the disks 2 and 3 are provided. Holes 200a and 200b are provided. Specifically, in the present embodiment, the bent wall portions 20 and 20 of the trunnion 15 are provided with a pair of lubricating oil holes 200a and 200b on both sides of the central axis of the pivot shafts 14 and 14, respectively. The lubricating oil holes 200 a and 200 b are opened toward the traction surface 11 a of the power roller 11. In particular, in the present embodiment, the first lubricating oil hole 200a opens toward the rotation direction of the power roller 11, while the second lubricating oil hole 200b extends in the direction opposite to the rotation direction of the power roller 11. Open toward. In addition, the first lubricating oil hole 200a provided in one bent wall portion 20 is opposed to the second lubricating oil hole 200b provided in the other bent wall portion 20 with the power roller 11 interposed therebetween, and one bent portion. The second lubricating oil hole 200b provided in the wall portion 20 is opposed to the first lubricating oil hole 200a provided in the other bent wall portion 20 with the power roller 11 interposed therebetween.

  Moreover, the lubricating oil supply means for supplying lubricating oil toward each lubricating oil hole 200a, 200b is as follows. That is, as shown in FIG. 1, an oil passage 29a is provided in the drive rod 29 integrally joined to one pivot 14 of the trunnion 15, and lubricating oil is supplied to the trunnion 15 side by this oil passage 29a. It has become. The oil passage 29a extends from the pivot shaft 14 on the drive rod 29 side of the trunnion 15 to one bent wall portion 20 formed integrally with the pivot shaft 14 to correspond to the first and second lubricating oil holes 200a, The first connection oil passage 210 communicates with the first connection oil passage 210 and reaches the pivot 14 on the opposite side of the drive rod 29 through the support plate portion 16. A second connecting oil passage 220 that extends to the other bent wall portion 20 formed integrally with the pivot 14 and communicates with the corresponding first and second lubricating oil holes 200a and 200b communicates with each other. In this case, a switching valve (not shown) for switching the flow of the lubricating oil to the corresponding first and second lubricating oil holes 200a and 200b is inserted into the first connecting oil passage 210, and Also, a switching valve (not shown) for switching the flow of the lubricating oil to the first and second lubricating oil holes 200a, 200b corresponding to the second connecting oil passage 220 is inserted.

  In the present embodiment, as indicated by an arrow in FIG. 2, the traction of the power roller 11 depends on the magnitude of the power transmitted from the input side disk 2 to the output side disk 3 via the power roller 11. The discharge direction of the lubricating oil with respect to the surface 11a can be changed. Specifically, the toroidal continuously variable transmission of the present embodiment has a low torque region where the transmission power is relatively small and a high torque region where the transmission power is relatively large. As shown in (a), the lubricating oil is discharged from the first lubricating oil holes 200a of the bent wall portions 20 and 20 (the discharging direction of the lubricating oil faces the rotational direction of the power roller 11), while the high In the torque region, as shown in FIG. 2B, the lubricating oil is discharged from the second lubricating oil holes 200b of the bent wall portions 20 and 20 (the lubricating oil discharge direction is the rotation of the power roller 11). Head in the opposite direction). Such switching control of the discharge direction of the lubricating oil is performed by switching the above-described switching valve (not shown) via a control device (not shown).

  As described above, according to the present embodiment, in view of the fact that the amount of lubricating oil is proportional to the input torque and the engine speed, the oil is transmitted from the input side disk 2 to the output side disk 3 via the power roller 11. Since the discharge direction of the lubricating oil with respect to the traction surface 11a of the power roller 11 can be changed according to the magnitude of the power to be increased, the amount of the lubricating oil discharged (spouted) toward the power roller 11 is increased. Therefore, the power roller can be cooled (lubricated) efficiently and effectively. In particular, in the present embodiment, in the low torque region, the lubricant discharge direction from the lubricant hole 200 (200a) is directed to the rotation direction of the power roller 11 (the lubrication is performed in the rotation order of the power roller 11). Therefore, dynamic torque due to oil agitation resistance can be reduced. Further, in the present embodiment, in the high torque region, the cooling performance is regarded as important, and the discharge direction of the lubricating oil from the lubricating oil hole 200 (200b) is directed in the direction opposite to the rotation direction of the power roller. (The lubrication is discharged from the reverse of the rotation order of the power roller 11), the relative lubrication speed (the discharge speed of the lubricating oil with respect to the rotation speed of the power roller) is increased, and the cooling effect can be further enhanced.

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

DESCRIPTION OF SYMBOLS 1 Input shaft 2 Input side disk 3 Output side disk 11 Power roller 11a Traction surface 14 Pivot 15 Trunnion 16 Support plate part 20 Bending wall part 200a, 200b Lubricating oil hole

Claims (3)

An input side disk coupled to an input shaft receiving rotational force and rotating integrally with the input shaft, and a power roller provided between the input side disk, receives the rotational force of the input side disk at a predetermined speed ratio. An output-side disk; and 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. In the toroidal continuously variable transmission in which power transmission between the disc and the disk is performed through an oil film,
The trunnion is provided on a support plate portion that supports the power roller, and is bent to the power roller side at both ends in the axial direction of the pivot of the support plate portion, and the power roller is sandwiched between the trunnions. And having a pair of bent wall portions facing each other on the inner surface and provided with the pivot on the outer surface,
The pair of bent wall portions are provided with lubricating oil holes for discharging lubricating oil to the traction surface of the power roller that performs power transmission via the oil film with the disk,
According to the magnitude of power transmitted from the input side disk to the output side disk via the power roller, the discharge direction of the lubricating oil to the traction surface of the power roller is changed ,
The transmission power has a relatively small low torque region and a relatively large high torque region, and in the low torque region, the discharge direction of the lubricating oil from the lubricating oil hole is directed to the rotation direction of the power roller. Toroidal-type continuously variable transmission. An input side disk coupled to an input shaft receiving rotational force and rotating integrally with the input shaft, and a power roller provided between the input side disk, receives the rotational force of the input side disk at a predetermined speed ratio. An output-side disk; and 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. In the toroidal continuously variable transmission in which power transmission between the disc and the disk is performed through an oil film,
  The trunnion is provided on a support plate portion that supports the power roller, and is bent to the power roller side at both ends in the axial direction of the pivot of the support plate portion, and the power roller is sandwiched between the trunnions. And having a pair of bent wall portions facing each other on the inner surface and provided with the pivot on the outer surface,
  The pair of bent wall portions are provided with lubricating oil holes for discharging lubricating oil to the traction surface of the power roller that performs power transmission via the oil film with the disk,
  According to the magnitude of power transmitted from the input side disk to the output side disk via the power roller, the discharge direction of the lubricating oil to the traction surface of the power roller is changed,
  The transmission power has a relatively small low torque region and a relatively large high torque region, and in the high torque region, the discharge direction of the lubricating oil from the lubricating oil hole is opposite to the rotation direction of the power roller. A toroidal-type continuously variable transmission characterized by heading in the direction. The transmission power has a relatively small low torque region and a relatively large high torque region, and in the high torque region, the discharge direction of the lubricating oil from the lubricating oil hole is opposite to the rotation direction of the power roller. The toroidal continuously variable transmission according to claim 1, wherein the toroidal continuously variable transmission is directed in a direction.

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