JP5051438B2 - 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 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two output side disks 3 are disposed on the outer periphery of the input shaft 1. 3 is 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 driven to rotate by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate (loading cam) 7 located on the left side in the drawing. It has become. 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 (see, for example, Patent Document 1), and the right side input disk 2 in the figure is splined to the input shaft 1. These input side disks 2 rotate together with the input shaft 1. A power roller is provided between the inner side surfaces (concave surface; also referred to as a traction surface) 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 disks 3 and 3. 11 (see FIG. 4) is rotatably held.

  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 a loading nut 9 screwed into a screw portion 1 e formed on the outer peripheral surface of the input shaft 1. 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.

  As shown in FIG. 4, which is a cross-sectional view taken along the line AA in FIG. 3, both the disks 3 and 3 are sandwiched from both sides inside the casing 50 and at the side positions of the output side disks 3 and 3. The pair of yokes 23A and 23B is supported in the state. The pair of yokes 23A and 23B are formed in a rectangular shape by pressing or forging a metal such as steel. In order to support pivots 14 provided at both ends of the trunnion 15 to be described later in a swingable manner, circular support holes 18 are provided at the four corners of the yokes 23A and 23B, and the width direction of the yokes 23A and 23B. A circular locking hole 19 is provided at the center of the.

  The pair of yokes 23 </ b> A and 23 </ b> B are supported so as to be slightly displaceable by support posts 64 and 68 formed on portions of the inner surface of the casing 50 facing each other. These support posts 64 and 68 are provided so as to face the first cavity 221 and the second cavity 222, respectively, between the inner side surface 2a of the input side disk 2 and the inner side surface 3a of the output side disk 3. Yes.

  Therefore, the yokes 23 </ b> A and 23 </ b> B are supported by the support posts 64 and 68, and one end thereof faces the outer peripheral portion of the first cavity 221, and the other end faces the outer peripheral portion of the second cavity 222. doing.

  Since the first and second cavities 221 and 222 have the same structure, only the first cavity 221 will be described below.

  As shown in FIG. 4, inside the casing 50, the first cavity 221 is provided with a pair of trunnions 15 and 15 that swing about a pair of pivots 14 and 14 that are twisted with respect to the input shaft 1. It has been. In FIG. 4, the input shaft 1 is not shown. Each trunnion 15, 15 is a pair of bent portions formed in a state where the trunnions 15, 15 are bent toward the inner side surface of the support plate 16 at both ends in the longitudinal direction (vertical direction in FIG. 4) of the support plate 16. Wall portions 20 and 20 are provided. 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 center portion of the support plate portion 16, and a base end portion (first shaft 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. In addition, each power roller 11 is rotatably supported around the tip end portion (second shaft 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.

  As described above, the pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable with respect to the pair of yokes 23A and 23B and displaceable in the axial direction (vertical direction in FIG. 4). The trunnions 15 and 15 are restricted from moving in the horizontal direction by the yokes 23A and 23B. As described above, four circular support holes 18 are provided at the four corners of each of the yokes 23 </ b> A and 23 </ b> B. The pivot shafts 14 provided at both ends of the trunnion 15 are respectively provided in the support holes 18 with the radial needle bearings 30. It is supported so as to be able to swing through. Further, as described above, the circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (left and right direction in FIG. 4), and the inner peripheral surface of the locking hole 19 is cylindrical. Support posts 64 and 68 are internally fitted as surfaces. 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, 4, 4 (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 the thrust ball bearings 24 is composed of a plurality of balls 26, 26, an annular retainer 27 for holding the balls 26, 26 in a freely rolling manner, and an annular outer ring 28. ing. 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 (shaft portions extending from the pivot shaft) 29 and 29 are respectively provided at one end portions (lower end portions in FIG. 4) of the trunnions 15 and 15, and outer peripheral surfaces of intermediate portions of the drive rods 29 and 29. The drive pistons (hydraulic pistons) 33, 33 are fixedly provided. 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 drive shaft 22 is transmitted to the input side disks 2 and 2 and the input shaft 1 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. 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 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 such a toroidal type continuously variable transmission, power is transmitted by the shearing force of oil between the input / output side disks 2 and 3 and the power roller 11. Therefore, it is necessary to apply a large load to the contact point between the input / output side disks 2 and 3 and the power roller 11.

  As the method of applying the load, there are a case where the above-described loading cam type pressing device 12 which mechanically generates a load proportional to the input torque is used, and a case where a hydraulic type pressing device 130 as shown in FIG. 5 is used. There is. When only the loading cam type pressing device 12 is used, a thrust proportional to only the input torque (the pressing force of the input side disk) is generated. An excessive pressing force may act on the contact portion, leading to a decrease in transmission efficiency and a decrease in durability. On the other hand, when the hydraulic pressing device 130 is used, an optimum pressing force can be applied according to the speed change, the oil temperature, the number of revolutions, and the like, so that the transmission is more efficient than the loading cam type pressing device 12. Can be realized.

  Here, the hydraulic pressing device 130 will be briefly described with reference to FIG. 5. The pressing device 130 is a first cylinder portion 141 coupled to the base end portion (left end portion in FIG. 5) of the input shaft 1. And a second cylinder portion 159 provided on the input side disk 2, an annular first piston portion 161, and an annular second piston portion 160.

  The first cylinder portion 141 is formed in a substantially bottomed cylindrical shape, the cylindrical portion is located on the outer periphery outside of the second cylinder portion 159, and the bottom portion is the back surface (outer surface) 2d of the input side disk 2. It is arranged in a state of facing. Further, the bottom portion of the first cylinder portion 141 is fixed by being externally fitted to the input shaft 1. The second cylinder part 159 is formed in a cylindrical shape and extends from the outer peripheral edge of the input side disk 2 toward the first cylinder part 141.

  The second piston portion 160 has an inner peripheral surface fitted to the outer peripheral surface of the input shaft 1, and an outer peripheral surface fitted to the inner peripheral surface of the second cylinder portion 159. It is arranged in a state facing the rear surface 2d of the. The first piston portion 161 has an inner peripheral surface fitted to the outer peripheral surface of the input shaft 1, and an outer peripheral surface fitted to the inner peripheral surface of the first cylinder portion 141. The piston portion 160 and the first cylinder portion 141 are arranged.

  A space surrounded by the inner surface of the first cylinder portion 141, the first piston portion 161, and a part of the outer peripheral surface of the input shaft 1 constitutes a first hydraulic chamber (oil chamber) 170. . The first hydraulic chamber 170 is kept fluid tight by a plurality of seal members 171. The space surrounded by the inner peripheral surface of the second cylinder portion 159, the second piston portion 160, the back surface 2d of the input side disk 2 and a part of the outer peripheral surface of the input shaft 1 is the second The hydraulic chamber (oil chamber) 167 is configured. The second hydraulic chamber 167 is kept fluid tight by a plurality of seal members 168. In addition, on the inner peripheral side of the second cylinder portion 159, a space 175 located between the second piston portion 160 and the first piston portion 161 is an air chamber. The air chamber 175 is kept fluid tight by a plurality of seal members 168 and 171. Further, the second cylinder portion 159 has a gap S that also functions as a communication groove that allows the air chamber 175 to communicate with the outside. The piston portion 161 can be contacted. Then, using part of the first hydraulic chamber 170, a disc spring 200 for applying a preload is interposed between the first piston portion 161 and the first cylinder portion 141. The first piston portion 161 that is movable along the input shaft 1 is urged toward the input side disk 2 with respect to the cylinder portion 141.

  In addition, in order to supply oil to each of the hydraulic chambers 167 and 170, the input shaft 1 or the like has an oil passage 1f coaxial with the axis O or an oil hole 180 or the like extending in the radial direction so as to be orthogonal to the oil passage 1f. A road is formed.

  Here, when pressure oil is supplied to the first hydraulic chamber 170 to apply the hydraulic pressure, the first cylinder 141 fixed to the input shaft 1 is movable in the axial direction of the input shaft 1. The piston portion 161 moves toward the input side disk 2 along the axial direction. Then, the first piston portion 161 in contact with the second cylinder portion 159 applies a pressing force that presses the input side disc 2 provided with the second cylinder portion 159 toward the other input side disc 2.

  Further, when pressure oil is supplied to the second hydraulic chamber 167 to apply hydraulic pressure, the input can move along the axial direction of the input shaft 1 with respect to the second piston portion 160 fixed to the input shaft 1. The second cylinder portion 159 provided on the side disk 2 moves together with the input side disk 2 in the direction toward the other input side disk 2, and presses the other input side disk 2 toward the input side disk 2. A pressing force is applied.

  In order to prevent the ball spline 6 from coming out of the central through hole 301, an annular protrusion 160 a of the second piston portion 160 is provided between the input side disk 2 and the outer peripheral surface of the input shaft 1 on the pressing device 130 side. Between the input side disk 2 on the small diameter side of the input side disk 2 and the outer peripheral surface of the input shaft 1 from the support posts 64 and 68, respectively, on the small diameter side of the input side disk 2 Retaining members 250, 250 extending between the side disk 2 and the outer peripheral surface of the input shaft 1 are provided.

Japanese Utility Model Publication No. 1-122550

  By the way, in the toroidal type continuously variable transmission, the elastic deformation of the disks 2 and 3 generated by the two-point pushing load from the power roller 11 is large. In particular, when the disks 2 and 3 are in contact with the power roller 11 on the inner side in the radial direction, the force in the direction perpendicular to the axis (direction perpendicular to the axial direction) at the contact point increases, and the radial direction of the disks 2 and 3 increases. The inner diameter of the inner part (smaller diameter part) becomes smaller. That is, as exaggeratedly shown in FIG. 6, when the input side disk 2 comes into contact with the power roller 11 on the inner side in the radial direction (low speed side), the inner diameter of that portion (the small diameter side portion on the right side in FIG. 6) is tapered. (The disk 2 is deformed from the dotted line state to the solid line state in FIG. 6). Further, when the input side disk 2 is viewed from the inner side surface 2a side, as shown in an exaggerated manner in FIG. 7, the state is changed from a solid line state to a chain line state. In this case, the through hole 301 provided at the center of the input side disk 2 is deformed into an elliptical shape, but the input shaft 1 remains circular, and there is a wide gap between the through hole 301 and the input shaft 1. There are narrow places. Of course, even when the input side disk 2 is in contact with the power roller 11 on the outer side in the radial direction (high speed side), the input side disk 2 warps on the back surface 2d side and is elliptical when viewed from the inner side surface 2a side. Deform.

  Therefore, when the ball spline 6 is used as the axial sliding guide means (bearing means for reducing the axial resistance) between the input side disk 2 and the input shaft 1 as in the configuration described above. When the deformation of the input side disk 2 at a high load is particularly large, for example, when the power transmission force is relatively large, but the rigidity of the input side disk 2 cannot be increased so much due to the layout, the ball spline 6 A large force is applied to the rolling elements (balls), and permanent deformation due to excessive surface pressure may occur. Such permanent deformation serves as a friction element that prevents the smooth operation of the ball spline 6 as an axial sliding guide means. Due to this friction, the pressing force of the pressing device 130 decreases, the pressing force against the traction portion becomes insufficient, and there is a possibility that gloss slip or the like occurs.

  The present invention has been made in view of the above circumstances, and is a toroidal type continuously variable that can smoothly slide and guide a disc with respect to an input shaft with a simple configuration and without causing a decrease in the pressing force of the pressing device. An object is to provide a transmission.

In order to achieve the above object, a toroidal continuously variable transmission according to the present invention includes an input shaft to which rotational torque is input, and an elastic made of hard rubber, Teflon (registered trademark), resin or copper-based material on the input shaft. Provided between the input side disk and the input side disk that is provided only through the member and rotates integrally with the input shaft and is slidable in the axial direction of the input shaft with respect to the input shaft. An output-side disk that receives the rotational force of the input-side disk at a predetermined speed ratio via a power roller; and a pressing device that is disposed on the back side of the input-side disk and presses the input-side disk in the axial direction. It is characterized by that.
The said structure WHEREIN: It is preferable that the said elastic member is provided with the slit opened to the small diameter side of the said input side disk.

According to the toroidal-type continuously variable transmission of the present invention, the elastic member is interposed between the input side disk on the pressing device side and the input shaft. It can be elastically deformed following the elastic deformation of the input side disk. Therefore, even if the input side disk is elastically deformed, the input side disk can slide smoothly with respect to the input shaft without causing a decrease in the pressing force of the pressing device.
Further, since only an elastic member is interposed between the input side disk and the input shaft, it is not necessary to form ball grooves or the like on the input side disk and the input shaft, so that the manufacturing cost can be reduced. When a bending load is applied, no stress concentration portion is generated, and the strength can be improved.
Further, when a hydraulic pressing device is used, the sliding portion of the elastic member can be lubricated by oil leaking from the high pressure oil chamber of the pressing device to the sliding portion of the elastic member.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The feature of the present invention lies in the structure for rotating the input side disk integrally with the input shaft and supporting the input shaft so as to be slidable in the axial direction of the input shaft. Since it is the same as the conventional configuration and operation described above, hereinafter, only the characteristic part of the present invention will be referred to, and other parts will be briefly described with the same reference numerals as those in FIGS. Keep on.

  As shown in FIG. 1, in the embodiment of the present invention, a hydraulic pressing device 130 similar to that shown in FIG. 5 is used as a pressing device for pressing the input side disk 2 in the axial direction. The input side disk 2 on the left side in the figure, in which the pressing device 130 is disposed on the back surface (outer side surface) 2d side, is supported by the input shaft 1 via an elastic member 500, whereby the input side disk 2 is input. It rotates integrally with the shaft 1 and is slidable in the direction of the axis O of the input shaft 1 with respect to the input shaft 1. The input side disk 2 is pressed toward the output side disk 4 along the axis O of the input shaft 1 by the pressing device 130. An annular protrusion 160a of the second piston portion 160 is fitted between the input side disk 2 and the outer peripheral surface of the input shaft 1 on the pressing device 130 side so that the elastic member 500 does not escape from the through hole 301 in the center. Further, a retaining ring 501 as a retaining member is provided between the input side disk 2 on the small diameter side of the input side disk 2 and the outer peripheral surface of the input shaft 1. The retaining ring 501 is attached to a groove provided on the inner peripheral surface of the through hole 301 of the input side disk 2.

  When the driving force is transmitted from the pressing device 130 to the input disk 2 on the pressing device 130 side (left side in FIG. 1) on the outer diameter side, the sliding movement of the input disk 2 in the direction of the axis O with respect to the input shaft 1 It is not necessary to transmit torque, and it is sufficient that the input side disk 2 and the input shaft 1 can be aligned while the input side disk 2 slides. Therefore, if the elastic coefficient of the elastic member 500 is too small (too soft), the function of aligning the core between the input side disk 2 and the input shaft 1 is lost. Rigid ones having an elastic modulus are preferred. Further, the elastic member 500 is required to function as an axial sliding guide means (bearing means for reducing axial resistance) for sliding the input side disk 2 with respect to the input shaft 1, so that it slides to some extent. A material having a small friction coefficient is desired. Therefore, the elastic member 500 can be made of, for example, hard rubber, Teflon (registered trademark), resin, or the like. Particularly, when made of, for example, HNBR (hydrogenated nitrile rubber), the elastic member 500 is an oil having strong chemical activity. Compatibility with traction oil is good and preferable.

  In the present embodiment, since the elastic member 500 is interposed between the input side disk 2 on the pressing device 130 side and the input shaft 1, the input side disk 2 as shown in FIGS. Even if this elastic deformation occurs, the elastic member 500 can elastically deform following the elastic deformation of the input side disk 2. In this case, between the input side disk 2 and the input shaft 1, although radial force is generated due to elastic deformation of the input side disk 2, no radial force is generated due to torque transmission or the like. This is because the torque transmission by the power roller is a couple and the radial force acting on the disk is canceled out in principle. For this reason, even if the sliding movement of the input side disk 2 by the elastic member 500 involves a slip, the friction loss is not so large. Therefore, even if the elastic deformation of the input side disk 2 as described above occurs, the input side disk 2 can slide smoothly with respect to the input shaft 1 without causing a decrease in the pressing force of the pressing device 130.

  Further, since it is only necessary to interpose the elastic member 500 between the input side disk 2 and the input shaft 1, it is not necessary to form ball grooves or the like in the input side disk 2 and the input shaft 1, thereby reducing the manufacturing cost. In addition, when the bending load is applied, no stress concentration portion is generated, and the strength can be improved.

  Furthermore, since the hydraulic pressing device 130 is used and the inside of the oil chamber (the first hydraulic chamber 170 and the second hydraulic chamber 167) is at a high pressure, it is between the input side disk 2 and the annular projecting portion 160a. Since there is some oil leakage from the provided seal member 700, the sliding portion of the elastic member 500 can be lubricated using this leaked oil.

  In the present embodiment, a retaining ring 501 is provided on the small-diameter portion side of the input side disk 2 so that the elastic member 500 does not come out of the central through hole 301. Instead of this retaining ring 501, Similarly to FIG. 6, retaining members 250, 250 extending from the support posts 64, 68 between the input side disk 2 on the small diameter side of the input side disk 2 and the outer peripheral surface of the input shaft 1 may be provided.

  FIG. 2 is a diagram showing another embodiment of the present invention. In this embodiment, instead of the elastic member 500, a cylindrical elastic member 600 made of a copper-based material provided with a slit 601 is provided between the input side disk 2 and the input shaft 1. The input side disk 2 on the apparatus 130 side rotates integrally with the input shaft 1 and is slidable in the direction of the axis O of the input shaft 1 with respect to the input shaft 1. The slit 601 is formed in a cylindrical shape opened to the small diameter side of the input side disk 2, and the elastic member 600 can be elastically deformed by forming the slit 601. Since the deformation of the input side disk 2 caused by the two-point pushing load from the power roller 11 is larger in the small diameter side portion having low rigidity, the elastic member 600 has an opening side of the slit 601 on the small diameter side of the input side disk 2. It is incorporated so that it faces. Other configurations of the present embodiment are the same as those in FIG.

In the present embodiment, since the elastic member 600 is interposed between the input side disk 2 on the pressing device 130 side and the input shaft 1, the input side disk 2 as shown in FIGS. Even if elastic deformation occurs, the elastic member 600 can be elastically deformed following the elastic deformation of the input side disk 2, and therefore the same effect as the embodiment of FIG. 1 can be obtained.

  The present invention can be applied to a full toroidal continuously variable transmission that does not have a trunnion, in addition to a half-toroidal continuously variable transmission such as a double cavity type.

It is principal part sectional drawing of the toroidal type continuously variable transmission which concerns on embodiment of this invention. It is principal part sectional drawing of the toroidal type continuously variable transmission which concerns on other embodiment of this invention. It is sectional drawing which shows an example of the specific structure of the toroidal type continuously variable transmission conventionally known. It is sectional drawing which follows the AA line of FIG. It is sectional drawing corresponding to FIG. 3 of the toroidal type continuously variable transmission provided with the hydraulic pressing device. It is a principal part expanded sectional view which shows the conventional support structure which supports the input side disk so that sliding is possible with respect to the input shaft. It is the figure which exaggerates and shows the deformation | transformation state of an input side disk, Comprising: It is the figure which looked at the input side disk from the inner surface side.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Input shaft 2 Input side disk 3 Output side disk 11 Power roller 130 Press apparatus 500,600 Elastic member

Claims (2)

  An input shaft to which rotational torque is input, and the input shaft is provided only through an elastic member made of hard rubber, Teflon (registered trademark), resin or copper-based material, and rotates integrally with the input shaft and the input An input side disk that is slidable in the axial direction of the input shaft with respect to the shaft and a power roller provided between the input side disk and the rotational force of the input side disk is received at a predetermined speed ratio. A toroidal continuously variable transmission, comprising: an output-side disk; and a pressing device that is disposed on the back side of the input-side disk and presses the input-side disk in the axial direction. The toroidal continuously variable transmission according to claim 1, wherein the elastic member is provided with a slit opened on a small diameter side of the input side disk.

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