JP6183163B2 - 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. 4 and 5, for example. An input shaft 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two output side disks 3, 3 are attached to the outer periphery of the input shaft 1. . 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 is rotatably held 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. .

  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 AA 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 a pair of bent wall portions 20, 20 formed at both ends in the longitudinal direction (vertical direction in FIG. 5) of the support plate portion 16 so as to be bent toward the inner surface side of the support plate portion 16. have. 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 23 supported at the center of each trunnion 15, 15 can be adjusted. Each power roller 11 is rotatably supported via a radial needle bearing 35 around the tip 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. 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. 5), 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 a spherical post 68 and a cylinder for supporting the same. The upper cylinder body 61 of the body 31 is supported so as to be swingable.

  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 (thrust bearing) 24 that is a thrust rolling bearing is sequentially formed from the outer surface side of the power roller 11. A thrust needle bearing 25 is provided. 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. Each of the drive pistons 33 and 33 is oil-tightly fitted in a cylinder body 31 constituted by an upper cylinder body 61 and a lower cylinder body 62. The drive pistons 33 and 33 and the cylinder body 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 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 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 rotational speed 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 a machine such as a toroidal-type continuously variable transmission, for assembling each member, for example, in a portion where the shaft passes through the member, a gap between the inner diameter of the through hole of the member and the outer diameter of the shaft Must be optimized. For example, it is necessary to consider the size of the gap depending on whether the shaft and the member are fixed, whether the shaft and the member move relatively along the axial direction of the shaft, or whether the shaft rotates.

  For example, when the shaft and the member move relative to each other in the axial direction as described above, if the gap is narrow, when the shaft or the member is elastically deformed by an external force during operation, the member is sandwiched between the shaft and the member. Therefore, there is a possibility that the movement becomes difficult.

  Further, when the shaft rotates relative to the member via the bearing, the clearances between the outer peripheral surface of the shaft, the outer peripheral surface of the bearing ball or needle, and the inner peripheral surface of the through hole of the member are aligned. If the gap is narrow, if the shaft or member is elastically deformed by an external force during operation, the member may be sandwiched between the bearing and the shaft, which may make rotation difficult. In addition, if the vibration based on the gap as described above, the deviation between the center axis of the member and the center of rotation, or the like occurs, it may cause fretting.

  As such a toroidal-type continuously variable transmission, for example, one in which the input side disks 2 and 2 are fixed to the input shaft 1 has been proposed (for example, see Patent Document 1). Further, a toroidal continuously variable transmission has been proposed in which a cylindrical member having an output gear 44 on the outer peripheral side is press-fitted into a through hole through which the input shaft 1 of the pair of output side disks 3 and 3 passes (for example, , See Patent Document 2).

  A bearing in which a radial gap between the input shaft 1 of the bearing that rotatably supports the input shaft 1 and the bearing (needle or sphere) is disposed between the input shaft 1 and the output side disk 3 A toroidal continuously variable transmission has been proposed in which the clearance is larger than the gap along the radial direction with the supported member (input shaft 1 or output side disk 3) supported by this bearing (see, for example, Patent Document 3). ).

  In the input side disk 2 provided with the oil chamber of the hydraulic pressing device 12 on the back surface, the outer peripheral surface of the input side disk 2 is substantially in contact with the inner peripheral surface of the covered cylindrical first cylinder constituting the oil chamber. And the inner peripheral surface of the first cylinder is arranged so that the outer peripheral surface of the input shaft 1 is substantially in contact with the inner peripheral surface of the through hole through which the input shaft 1 of the input side disk 2 passes. A toroidal continuously variable transmission in which a clearance (clearance) between the input side disk 2 and the outer peripheral surface of the input side disk 2 is larger than a clearance between the inner peripheral surface of the through hole of the input side disk 2 and the outer peripheral surface of the input shaft 1. It has been proposed (see, for example, Patent Document 4).

  Further, in a structure in which the loading nut 9 is disposed on the back side of the input side disk 2 and the movement of the input side disk 2 to the back side is restricted, the loading nut 9 is disposed between the rotating nut and the input side disk 2. There has been proposed a toroidal continuously variable transmission that prevents fretting wear on the back surface of the input side disk 2 by supplying oil by providing an oil groove in the washer (see, for example, Patent Document 5).

JP 2000-337466 A JP-A-10-196754 Japanese Patent No. 4725768 JP 2008-261470 A JP 2008-261472 A

  By the way, in each of the above-mentioned patent documents 1 to 5, the gap between the outer peripheral surface of the input shaft 1 and the inner peripheral surface of the through hole of the disc (input-side disc 2) supported by the input shaft 1, The relationship between the gaps such as the bearing gaps of the disk (output side disk 3) that is rotatably supported with respect to the shaft 1 via the bearing is not described.

  For example, in the pair of input side disks 2 and 2, when one input side disk 2 on the pressing device 12 side is pressed by the pressing device 12, the axis of the input shaft 1 is based on the pressing of the pressing device 12. Must be able to move in the direction. The other input side disk 2 is in a state of relatively pulling the input shaft when the one input side disk 2 is pushed by the pressing device 12, and the other input side disk 2 is connected to the input shaft 1 correspondingly. It can rotate integrally and move in the axial direction. That is, the other input side disk 2 is fixed to the input shaft 1. Therefore, even for the same input side disks 2 and 2, the situation with respect to the input shaft is different, and the above-described gap needs to be taken into consideration. In addition, with respect to these gaps, the relationship of the bearing gaps in the output side disk 3 that is rotatably supported by the input shaft 1 via the bearings also becomes a problem.

  However, as described above, since the relationship between the gaps is not defined, for example, when the gaps described above of the pair of input side disks 2 and 2 are made the same, in one input side disk 2, When the input side disk 2 is elastically deformed, there is a possibility that it is difficult to move along the axial direction with the input shaft 1 interposed therebetween. Further, since the gap is too large in the other input side disk 2, there is a possibility that the input side disk 2 is slightly inclined and causes fretting. Further, in the case of the output side disk 3, there is a possibility that the input shaft 1 and the bearing are sandwiched so that rotation is difficult.

  The present invention has been made in view of the above circumstances, and a relationship such as a direct gap between each disk on the input side or the output side and a shaft supporting these disks, an indirect gap via a bearing, or the like. An object of the present invention is to provide a toroidal-type continuously variable transmission capable of making the above-mentioned appropriate.

  In order to achieve the above object, a toroidal continuously variable transmission according to the present invention includes a pair of input-side disks and a pair of disks provided concentrically and rotatably with their inner surfaces facing each other. Sandwiched between the input side disk and the output side disk, an output side disk, a shaft that passes through the center of the input side disk and the output side disk and supports the input side disk and the output side disk In a toroidal type continuously variable transmission comprising a power roller and a pressing device that applies a pressing force to the input side disk, the output side disk, and the power roller, a pair of the input side disk and a pair of the output side disk An integrated disk in which the other pair of disks is integrated is disposed between one of the pair of disks, and the front A radial bearing is disposed between the integrated disk and the shaft so that the integrated disk is rotatable with respect to the shaft, and one of the pair of the disks is provided on the back side of the disk. The pressing device that presses the disc against the shaft along the axial direction of the shaft is provided, and the inner peripheral surface of the disc on which the pressing device is provided and the outer peripheral surface of the shaft that passes through the disc Is larger than the gap Y between the inner peripheral surface of the other disc of the pair of discs and the outer peripheral surface of the shaft passing through the disc, and the integrated disc A clearance Z of a radial bearing portion between the shaft and the shaft is larger than the clearance Y.

  According to such a configuration, one disk provided with the pressing device for one pair of discs moves in the axial direction with respect to the shaft when pressed by the pressing device, whereas the other pressing device For example, the disk without the device moves in the axial direction together with the shaft. In this case, if the gap X between the disk moving with respect to the shaft is small, the disk is sandwiched when the disk is elastically deformed by an external force during operation, and the movement of the disk with respect to the shaft is hindered.

  Also. The clearance Y between the disk and the shaft that is not provided with a pressing device and does not move with respect to the shaft does not move with respect to the shaft. Therefore, even if the disk is elastically deformed and sandwiches the shaft, no problem occurs. On the other hand, if the gap Y is too large, fretting may occur due to vibration or the like based on the large gap Y on the disk. For these reasons, the gap X needs to be larger than the gap Y.

  Also, in the gap Z of the radial bearing portion between the integrated disk and the shaft, when the integrated disk is elastically deformed when the gap Z is too narrow, the radial bearing is sandwiched between the integrated disk and the shaft. Rotation is impeded. Therefore, the gap Z needs to be larger than the gap Y described above. In this way, by designing the gaps X, Y, and Z so that the gap X and the gap Z are larger than the gap Y, the above-described problems can be prevented.

  Another aspect of the toroidal continuously variable transmission of the present invention is a pair of input disks and a pair of output sides that are concentrically and rotatably provided with their inner surfaces facing each other. A disk, a shaft that passes through the center of the input side disk and the output side disk and supports the input side disk and the output side disk, and a power roller sandwiched between the input side disk and the output side disk And a toroidal continuously variable transmission comprising a pressing device that applies a pressing force to the input side disk, the output side disk, and the power roller, of the pair of the input side disk and the pair of the output side disks. The other pair of disks is disposed between one pair of disks, and between the other pair of the disks and the shaft. A radial bearing is disposed so that the other pair of the disks can rotate with respect to the shaft, and a cylindrical portion of a gear member that rotates integrally with the other pair of the disks includes the shaft of the other pair of the disks. Is inserted into a hole penetrating the other pair of disks so as to be rotatable integrally with the other pair of disks, and the disk is placed on the back side of one of the pair of disks with respect to the shaft. The pressing device for pressing along the axial direction of the shaft is provided, and a gap X between the inner peripheral surface of the disk provided with the pressing device and the outer peripheral surface of the shaft penetrating the disk is The radial gap between the other pair of the disk and the shaft is larger than the gap Y between the inner circumferential surface of the other disk of the pair of disks and the outer circumferential surface of the shaft passing through the disk. Bearing part The gap Z is larger than the gap Y, and the gap W between the inner circumferential surface of the other pair of the disks and the outer circumferential surface of the cylindrical portion of the gear member is smaller than the gap X and the gap Z. And

  According to such a configuration, the gap Z needs to be larger than the gap Y described above. In this way, by designing the gaps X, Y, and Z so that the gap X and the gap Z are larger than the gap Y, the same effects as those of the present invention described above can be achieved.

Further, since the gap W between the inner peripheral surface of the disk and the outer peripheral surface of the cylindrical portion of the disk that rotates integrally with the cylindrical portion of the gear member rotates integrally with the cylindrical portion, there is no problem even if the gap W is small. However, like the gap Y described above, if the gap W is large, fretting occurs.
From the above, by designing the gaps W, X, and Y so that the gap W is smaller than the gaps X and Z, problems such as pinching due to elastic deformation and occurrence of fretting are caused. Can be resolved.

  Another aspect of the toroidal continuously variable transmission according to the present invention includes a single input side disk and a single output side that are concentrically and rotatably provided with their inner surfaces facing each other. A disk, a shaft that passes through the center of the input side disk and the output side disk and supports the input side disk and the output side disk, and a power roller sandwiched between the input side disk and the output side disk And a toroidal-type continuously variable transmission including a pressing device that applies a pressing force to the input side disk, the output side disk, and the power roller. The pressing device that presses the disc against the shaft along the axial direction of the shaft is provided on the back side of one of the discs. A radial bearing is disposed between the other disk and the shaft, the other disk is rotatable with respect to the shaft, and the cylindrical portion of the gear member that rotates integrally with the other disk is the other. In the hole through which the shaft of the disk penetrates, the other disk is rotatably fitted integrally, and the radial bearing portion gap Z between the other disk and the shaft is the pressing device. It is larger than the clearance X between the inner peripheral surface of the provided disc and the outer peripheral surface of the shaft that passes through the disc, and the inner peripheral surface of the other disc and the outer peripheral surface of the cylindrical portion of the gear member The gap W is smaller than the gap X and the gap Z.

  According to such a configuration, the gap Z in the radial bearing portion of the disc that is rotatable with respect to the shaft via the radial bearing is a gap X between the disc and the shaft that is pushed by the pressing device and moves in the axial direction. Since it is larger, the disc can be smoothly rotated through the radial bearing even if the disc is elastically deformed, and the disc X provided with the pressing device and the shaft X are prevented from becoming too large, The occurrence of fretting can be suppressed.

  Further, fretting in this portion can be suppressed by making the gap W between the disk and the cylinder portion that are rotatably fitted integrally with the cylinder portion smaller than the gap Z and the gap X described above. Further, it is possible to prevent the radial bearing from being caught in the gap Z and the shaft from being caught in the gap X based on the elastic deformation of the disk, and the disks can be rotated smoothly. That is, by designing the gaps W, X, and Z to have the above-described differences, it is possible to prevent fretting and smoothly rotate the disk.

  According to the present invention, it is possible to prevent fretting and to smoothly rotate the input side disk and the output side disk by providing a difference in each gap between the shaft and the disk.

It is principal part sectional drawing which shows the toroidal type continuously variable transmission in the 1st Embodiment of this invention. It is principal part sectional drawing which shows the toroidal type continuously variable transmission in the 2nd Embodiment of this invention. It is principal part sectional drawing which shows the toroidal type continuously variable transmission in the 3rd Embodiment of this invention. It is sectional drawing which shows an example of the conventional toroidal type continuously variable transmission. It is sectional drawing which follows the AA line in FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
The feature of the toroidal type continuously variable transmission according to the present embodiment is that the inner peripheral surface of the through hole of the input side disk in the input side disk (disk) through which the input shaft (shaft) passes, and the outer peripheral surface of the input shaft Of clearance between each other, and the clearance of the radial needle bearing portion of the output side disk (disk) that can rotate with respect to the input shaft via a radial needle bearing (radial bearing). Therefore, in the following, this point will be described in detail, and the other parts will be denoted by the same reference numerals as those in the prior art, and the description thereof will be omitted or simplified.

(First embodiment)
As shown in FIG. 1, the toroidal-type continuously variable transmission according to the first embodiment has a pair of output side disks 3 and 3 and an output gear 4 integrated between a pair of input side disks 2 and 2. An integrated output side disk (integrated disk) 34 is arranged, and the input shaft (shaft) 1 is in a state of passing through the center between the pair of input side disks 2 and 2 and the integrated output side disk 34.

  A hydraulic pressing device 12 having a hydraulic chamber 80 on the back surface of one input side disk 2 is provided on the back surface of one input side disk 2 (the left disk in the figure). The hydraulic pressing device 12 is configured to push one input side disk 2 toward the integrated output side disk 34 with respect to the input shaft 1. In other words, the pressing device 12 is configured to pull the input shaft 1 with respect to one input side disk 2.

  Accordingly, one input side disk 2 is movable in the axial direction with respect to the input shaft 1. In this embodiment, the ball spline 6 allows one input side disk 2 to move in the axial direction with respect to the input shaft 1 and cannot rotate. The one input side disk 2 is integrated with the input shaft 1. Rotate to.

  The gap between the inner peripheral surface 2d of one input side disk 2 provided with such a pressing device 12 on the back surface and the inner peripheral surface 2d of the outer peripheral surface 1a of the input shaft 1 is defined as a gap X. To do. In this case, the gap X is a gap of the ball spline 6 where there is no ball. For example, in the splined portion, the maximum value (minimum value) of the inner diameter of the inner peripheral surface 2d and the outer peripheral surface 1a A value ½ of the difference from the maximum value (minimum value) of the outer diameter can be set as the gap X. Note that the gap X is ½ of the difference between the inner diameter of the inner peripheral surface 2d of one input-side disk 2 and the outer diameter of the outer peripheral surface 1a of the input shaft 1 opposed thereto in the ball portion of the ball spline 6. The diameter of the ball spline 6 may be subtracted from this value.

  The hydraulic pressing device 12 can rotate integrally with the input shaft 1, and the input side disc 2 is rotated by spline coupling the hydraulic pressing device 12 and the outer peripheral side of one input side disc 2. May be. In this case, it is not necessary to provide spline grooves on the inner peripheral surface 2d of the one input side disk 2 and the outer peripheral surface 1a of the input shaft 1, and these are arranged in a portion where the outer peripheral surface 1a and the inner peripheral surface 2d face each other. It is good also as a cylindrical shape with a fixed diameter. In this case, for example, the gap X may be a value that is ½ of the difference between the inner diameter of the inner peripheral surface 2d and the outer diameter of the outer peripheral surface 1a at the portion where the outer peripheral surface 1a and the inner peripheral surface 2d face each other.

  The other input side disk 2 includes a step 2b whose diameter changes on the inner peripheral surface 2c of the through hole through which the input shaft 1 passes, and this step 2b engages with the step 1d on the outer peripheral surface 1a of the input shaft 1, Movement (position) closer to the pressing device 12 along the axial direction of the input shaft 1 is restricted. A cotter groove 73 is provided on the back side of the other input side disk 2 of the input shaft 1, and a cotter 72 is attached to the cotter groove 73 and the cotter 72 is held by the cotter holder 74.

  The cotter 72 regulates the position (movement) of the back surface of the other input-side disk 2 in a state where the step 1d and the step 2b are in contact with each other and are positioned. Thereby, the movement of the other input side disk 2 along the axial direction of the input shaft 1 is restricted. Moreover, the input shaft 1 and the other input side disk 2 are spline-coupled, and the input shaft 1 and the other input side disk 2 rotate integrally.

  A gap between the inner peripheral surface 2c of the other input side disk 2 and a portion of the outer peripheral surface 1a of the input shaft 1 facing the inner peripheral surface 2c is defined as a clearance Y. This gap Y is a gap in a portion that is not spline-coupled, and the gap Y is defined as ½ of the difference between the inner diameter of the inner peripheral surface 2c and the outer diameter of the outer peripheral surface 1a facing the inner peripheral surface 2c. To do. In the spline connection portion, 1 / of the difference between the maximum value (minimum value) of the inner diameter of the inner peripheral surface 2c and the maximum value (minimum value) of the outer diameter of the outer peripheral surface 1a facing the inner peripheral surface 2c. 2 may be the gap Y.

  The integrated output side disk 34 is formed by integrally forming a pair of conventional output side disks 3 and 3 and the output gear 4. The integrated output side disk 34 has the above-described inner side surfaces 3a and 3a, both surfaces of which face one of the pair of input side disks 2 and 2, respectively. Further, teeth 41 as the output gear 4 are provided on the outer peripheral surface of the integrated output side disk 34.

  A pair of radial needle bearings 5 is provided between the inner peripheral surface 77 of the integrated output side disk 34 and the inner peripheral surface 77 of the outer peripheral surface 1 a of the input shaft 1. These radial needle bearings 5 are respectively provided at both ends in the axial direction of the integrated output side disk 34. A gap in the radial needle bearing 5 is defined as a gap Z.

  In this case, for example, the inner diameter 77 of the integrated output side disk 34 (portion of the radial needle bearing 5) and the outer diameter of the outer peripheral face 1 a of the input shaft 1 at the part opposed via the radial needle bearing 5. The gap Z is a value obtained by subtracting twice the diameter of the needle of the radial needle bearing 5 from the difference value.

  In the present embodiment, the gap X> the gap Y, and the gap Z> the gap Y, and the gap Y is smaller than the gap X and the gap Z. In other words, the gap X and the gap Z are larger than the gap Y.

  Here, the gap X is a gap in one input side disk 2 that is movable in the axial direction with respect to the input shaft 1. If this gap X is too small, the input shaft 1 and the input side disk 2 are elasticized by an external force. In the case of deformation, there is a possibility that the input side disk 2 sandwiches the input shaft 1 and one input side disk 2 cannot move with respect to the input shaft 1.

  On the other hand, the other input side disk 2 does not move or rotate in the axial direction with respect to the input shaft 1 and operates substantially integrally with the input shaft 1. There is no problem even if it becomes in a state where 1 is sandwiched and cannot move relative to the input shaft 1. Therefore, it is preferable to make the gap Y smaller than the gap X. Further, if the gap Y is too large, the other input side disk 2 may be slightly inclined with respect to the input shaft 1 to cause fretting, and it is preferable to make the gap Y smaller than the gap X.

  Similarly, if the gap Z is too narrow, the integrated output-side disk 34 may not be able to rotate while sandwiching the radial needle bearing 5 and the input shaft 1. There is a need.

  According to such a toroidal-type continuously variable transmission, the relationship between the gaps X, Y, and Z becomes appropriate, and the smooth movement of the one input side disk 2 in the axial direction and the integral type output side disk 34 are reduced. Smooth rotation can be ensured and fretting of the other input side disk 2 can be prevented.

(Second Embodiment)
As shown in FIG. 2, in the toroidal transmission according to the second embodiment, as in the conventional case shown in FIG. 4, the pair of output side disks 3 and 3 and the output gear 4 are composed of separate members. ing. Similarly to the conventional case, the cylindrical flange portion (cylinder portion) 4a of the output gear 4 is inserted into the inner peripheral surface 77b of each large-diameter portion of the pair of output side disks 3 and 3, for example, by spline coupling, The flange portion 4a and the pair of output side disks 3 and 3 rotate integrally. Further, the inner peripheral surface 77b of the output side disks 3 and 3 and the outer peripheral surface of the flange portion 4a have an inlay structure. The smaller diameter side of the spigot structure is splined to the input shaft 1.

  A gap between the outer peripheral surface of the flange portion 4a and the inner peripheral surface 77b of the output side disks 3 and 3 in this inlay structure is defined as a clearance W. This gap W is basically ½ of the difference between the inner diameter of the inner surface 77b of the output side disks 3 and 3 in the spigot structure portion and the outer diameter of the flange portion 4a of the spigot structure portion.

  Further, a radial needle bearing 5 is provided between the inner peripheral surface 77a of the small-diameter portion of the output side disks 3 and 3 and the outer peripheral surface 1a of the input shaft 1 of the portion facing it. The clearance of the radial needle bearing 5 is defined as the clearance Z in the same manner as the clearance Z of the first embodiment.

  Further, the gap between the inner peripheral surface 2d of the one input side disk 2 to which the pressing device 12 is attached and the outer peripheral surface 1a of the input shaft 1 is defined as the gap X in the same manner as the gap X in the first embodiment.

  Further, the gap between the inner peripheral surface 2c of the other input side disk 2 on the side where the pressing device 12 is not attached and the outer peripheral surface 1a of the input shaft 1 is set to the gap Y in the same manner as the gap Y in the first embodiment. To do.

  In the second embodiment, as in the first embodiment, the gap X> the gap Y and the gap Z> the gap Y, and the gap Y is smaller than the gap X and the gap Z. ing. In other words, the gap X and the gap Z are larger than the gap Y. Thereby, there can exist an effect similar to 1st Embodiment.

  Furthermore, in the second embodiment, the clearance X> the clearance W and the clearance Z> the clearance W are set. If the gap X is too small as described above, when the input side disk 2 is elastically deformed by an external force, the input side disk 2 sandwiches the input shaft 1 so that one input side disk 2 is opposed to the input shaft 1. There is a possibility that it cannot move.

  As described above, the gap Z is a gap between the radial needle bearing 5 provided between the inner peripheral surface 77a of the small-diameter portion of the output side disks 3 and 3 and the outer peripheral surface 1a of the portion of the input shaft 1 facing it. If it is too small, when the output side disks 3 and 3 are elastically deformed, the radial needle bearing 5 is sandwiched and rotation becomes difficult.

  Further, the gap W is a gap between the outer peripheral surface of the flange portion 4a of the output gear 4 and the inner peripheral surface 77b of the output side disks 3 and 3, and the output gear 4 and the output side disks 3 and 3 are integrated. Since it rotates, there is no problem even if the gap W is narrow. On the other hand, if the gap W is too large, there is a risk of causing fluffing. Therefore, by setting the gap X> the gap W and the gap Z> the gap W as described above, each gap can be made appropriate so that the above-described problems can be solved.

(Third embodiment)
As shown in FIG. 3, in the third embodiment, the toroidal-type continuously variable transmission of the first embodiment is a double-cavity type, whereas the single-cavity-type toroidal-type continuously variable transmission. It has become.

  In the single cavity type, one input side disk 2 and one output side disk 3 are provided, and a power roller 11 is sandwiched between the input side disk 2 and the output side disk 3.

  In this example, a loading cam type pressing device 12 is provided on the back side of the input side disk 2. While the pressing device 12 can rotate integrally with the input shaft 1, the input side disk 2 provided with the pressing device 12 on the back side can freely rotate with respect to the input shaft 1 via a radial needle bearing 78. Yes. In a state where the input torque does not change, the pressing device 12 (input shaft 1) and the input side disc 2 rotate substantially integrally with a pressing force acting on the input side disc 2 by the pressing device 12. However, when the input side disk 2 does not rotate with respect to the loading cam when torque is input (changed), the pressing force of the pressing device 12 cannot be changed. Further, the input side disk 2 is movable in the axial direction of the input shaft 1.

  Further, the output gear 4 includes one cylindrical flange portion 4 a corresponding to one output side disk 3. The flange portion 4a is inserted into the inner peripheral surface 77b of the large-diameter portion of the output side disks 3 and 3, so that, for example, the flange portion 4a of the output gear 4 and the output side disks 3 and 3 rotate integrally by spline coupling. It has become. Further, the inner peripheral surface 77b of the output side disks 3 and 3 and the outer peripheral surface of the flange portion 4a have an inlay structure. The output side disks 3 and 3 are spline-coupled to the input shaft 1 on the smaller diameter side of the inlay structure.

  The output side disk 3 includes a radial needle bearing 5 between the input shaft 1 and is rotatable with respect to the input shaft 1. That is, in the output side disk 3, the output side disk 3 and the output gear 4 rotate integrally, and the output side disk 3 rotates with respect to the input shaft 1.

  The single-cavity toroidal-type continuously variable transmission has an input side angular bearing 81 that is supported by the casing 50 and receives a thrust load applied to the output side disk 3 based on the pressing force of the pressing device 12, and the pressing device 12. An input-side angular bearing 82 that receives a thrust load acting when the input shaft 1 is pulled into the side disk 2 is provided.

  In the third embodiment, a gap is formed between the inner peripheral surface 84 of the input side disk 2 where the radial needle bearing 78 is not provided and the portion of the outer peripheral surface 1a of the input shaft 1 facing the inner peripheral surface 84. Let X be. This gap X is the same gap as the gap X in the first and second embodiments described above.

  Further, a gap of the radial needle bearing 5 between the inner peripheral surface 77a of the small diameter portion of the output side disk 3 and the portion of the outer peripheral surface 1a of the input shaft 1 facing the inner peripheral surface 77a is defined as a clearance Z. This gap Z is the same as the gap Z in the first and second embodiments described above.

  A gap between the inner peripheral surface 77 b of the spigot portion of the large diameter portion of the output side disk 3 and the outer peripheral surface of the cylindrical flange portion 4 a of the output gear 4 is defined as a clearance W. This gap W is the same as the gap W of the above-described second embodiment.

  In the third embodiment, the gap Z> the gap X, the gap X> the gap W, and the gap Z> the gap W. That is, the gap Z in the radial needle bearing 5 portion of the output side disk 3 that is rotatable with respect to the input shaft 1 via the radial needle bearing 5 is pushed by the pressing device 12 and moves in the axial direction. Since it is larger than the gap X between the input shaft 1 and the output side disk 3 can be smoothly rotated via the radial needle bearing 5 even if the output side disk 3 is elastically deformed, the pressing device 12 is It is possible to suppress the gap X between the provided input side disk 2 and the input shaft 1 from becoming too large, and to suppress the occurrence of fretting and the like.

  Further, the gap W is smaller than the gap X and the gap Z. Here, the gap X is a gap between the input side disk 2 and the input shaft 1 that is rotatable with respect to the input shaft 1 and movable in the axial direction. If the gap X is too small, the input side disk 2 is caused by an external force. When elastically deformed, the input shaft 1 cannot be rotated and moved in the axial direction with the input shaft 1 interposed therebetween.

  Similarly, if the gap Z of the radial needle bearing 5 between the input shaft 1 and the output side disk 3 is too small, when the output side disk 3 is elastically deformed by an external force, the radial needle bearing 5 is sandwiched and input. The output side gear cannot rotate with respect to the shaft 1.

  On the other hand, the output-side disk 3 is not rotatable with respect to the flange portion 4a of the output gear 4 and is not allowed to move in the axial direction. That is, the output gear 4 and the output side disk 3 move together. Therefore, there is no problem even if the output side disk 3 is elastically deformed and the flange portion 4a is sandwiched, and the gap W at this portion can be made narrower than the gap X and the gap Z. Thus, by setting the gap Z> the gap X, the gap X> the gap W, and the gap Z> the gap W, each gap can be optimized.

  In the first to third embodiments, the arrangement of the input side disk 2 and the output side disk 3 and the relationship between the axes may be reversed. For example, a pair of input side disks 2 is disposed between a pair of output side disks 3, a pressing device 12 is provided on the back surface of the output side disk 3, the input shaft 1 is used as an output side shaft, the output gear 4 Instead of this, an input gear may be provided to rotate integrally with the input side disk 2. The pressing device 12 may be a hydraulic type or a loading cam type.

  The present invention can be applied to a full-toroidal continuously variable transmission without a trunnion in addition to various half-toroidal continuously variable transmissions of a single cavity type or a double cavity type.

W Clearance X Clearance Y Clearance Z Clearance 1 Input shaft (axis)
1a Outer peripheral surface 2 Input side disk (disk)
2c Inner peripheral surface 2d Inner peripheral surface 3 Output side disc (disc)
4 Output gear (gear member)
4a Flange (Cylinder)
5 Radial needle bearing (radial bearing)
11 Power roller 12 Press device 34 Integrated output side disk (integrated disk)
77a Inner peripheral surface 77b Inner peripheral surface

Claims (3)

A pair of input-side disks and a pair of output-side disks provided concentrically and rotatably with the respective inner surfaces facing each other, and the center portions of these input-side disks and output-side disks are passed through. A shaft supporting the input side disk and the output side disk, a power roller sandwiched between the input side disk and the output side disk, and pressing against the input side disk, the output side disk and the power roller. In a toroidal continuously variable transmission provided with a pressing device that applies force,
An integrated disk in which the other pair of disks is integrated is disposed between one pair of the input side disk and the pair of output side disks, and the integrated disk and the shaft A radial bearing is disposed between the integrated disk and the shaft so as to be rotatable with respect to the shaft;
The pressing device that presses the disk against the shaft along the axial direction of the shaft is provided on the back side of the one of the pair of the disks,
A gap X between the inner peripheral surface of the disk on which the pressing device is provided and the outer peripheral surface of the shaft passing through the disk is an inner peripheral surface of the other of the pair of disks. Larger than the gap Y between the shaft and the outer peripheral surface of the shaft passing through the disk,
A toroidal continuously variable transmission, wherein a gap Z of a radial bearing portion between the integrated disk and the shaft is larger than the gap Y. A pair of input-side disks and a pair of output-side disks provided concentrically and rotatably with the respective inner surfaces facing each other, and the center portions of these input-side disks and output-side disks are passed through. A shaft supporting the input side disk and the output side disk, a power roller sandwiched between the input side disk and the output side disk, and pressing against the input side disk, the output side disk and the power roller. In a toroidal continuously variable transmission provided with a pressing device that applies force,
The other pair of disks is disposed between one pair of the pair of the input side disks and the pair of the output side disks, and a radial bearing is provided between the other pair of the disks and the shaft. And the other pair of the disks are rotatable with respect to the shaft,
A cylindrical portion of a gear member that rotates integrally with the other pair of disks is fitted into a hole through which the shaft of the other pair of disks penetrates, so as to be rotatable integrally with the other pair of disks.
The pressing device that presses the disk against the shaft along the axial direction of the shaft is provided on the back side of the one of the pair of the disks,
A gap X between the inner peripheral surface of the disk on which the pressing device is provided and the outer peripheral surface of the shaft passing through the disk is an inner peripheral surface of the other of the pair of disks. Larger than the gap Y between the shaft and the outer peripheral surface of the shaft passing through the disk,
The gap Z of the radial bearing portion between the other pair of the disc and the shaft is larger than the gap Y,
A toroidal continuously variable transmission characterized in that a gap W between an inner peripheral surface of the other pair of disks and an outer peripheral surface of the cylindrical portion of the gear member is smaller than the gap X and the gap Z. One input-side disk and one output-side disk provided concentrically and rotatably with the respective inner surfaces facing each other, and the center of these input-side disk and output-side disk are passed through. A shaft supporting the input side disk and the output side disk, a power roller sandwiched between the input side disk and the output side disk, and pressing against the input side disk, the output side disk and the power roller. In a toroidal continuously variable transmission provided with a pressing device that applies force,
The pressing device that presses the disc against the shaft along the axial direction of the shaft is provided on the back side of one of the input-side disc and the output-side disc one by one,
A radial bearing is disposed between the other disk and the shaft, and the other disk is rotatable with respect to the shaft;
A cylindrical portion of a gear member that rotates integrally with the other disk is fitted into a hole through which the shaft of the other disk passes so as to be rotatable integrally with the other disk,
The gap Z of the radial bearing portion between the other disk and the shaft is a gap between the inner peripheral surface of the disk on which the pressing device is provided and the outer peripheral surface of the shaft passing through the disk. Larger than X,
A toroidal continuously variable transmission, wherein a gap W between an inner peripheral surface of the other disk and an outer peripheral surface of the cylindrical portion of the gear member is smaller than the gap X and the gap Z.

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