JP2006112518A - Toroidal continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a toroidal continuously variable transmission with inexpensive protruded portions serving as the rocking fulcrum of yokes. <P>SOLUTION: The toroidal continuously variable transmission comprises the yokes 113a, 113b for supporting the pivotal shafts of trunnions, respectively, in a freely rocking and axially displaceable manner and the protruded portions 320 provided thereon abutting on members opposed to the yokes and serving as the rocking fulcrum of the yokes. The protruded portions 320 are formed separately from the yokes 113a, 113b and mounted on the yokes 113a, 113b. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

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

  The use of a toroidal type continuously variable transmission as schematically shown in FIGS. 7 and 8 is partially implemented as a transmission for an automobile. This toroidal continuously variable transmission supports an input side disk 2 concentrically with an input shaft 1, and an output side disk 4 is fixed to an end of an output shaft 3 disposed concentrically with the input shaft 1. Inside the casing containing the toroidal-type continuously variable transmission, trunnions 6 and 6 are provided that swing around pivots 5 and 5 that are twisted with respect to the input shaft 1 and the output shaft 3. A power roller 11 is rotatably supported on each trunnion 6, 6, and each power roller 11, 11 is sandwiched (rolled) between both the input side and output side disks 2, 4. .

  The cross sections of the inner side surfaces 2a and 4a facing each other of the input and output side disks 2 and 4 each form a concave surface obtained by rotating an arc centering on the pivot 5 or a curve close to such an arc. ing. And the peripheral surface 11a, 11a of each power roller 11, 11 formed in the spherical convex surface is contact | abutted to each inner surface 2a, 4a.

  Between the input shaft 1 and the input side disk 2, a loading cam type pressing device 12 is provided. The pressing device 12 elastically presses the input side disk 2 toward the output side disk 4. The pressing device 12 includes a cam plate 13 that rotates together with the input shaft 1 and a plurality of (for example, four) rollers 15 held by a cage 14. In addition, a cam surface 16 that is a concavo-convex surface is formed on one side surface (the left side surface in FIGS. 7 and 8) of the cam plate 13, and the outer surface (see FIGS. 7 and 8) of the input side disk 2 is formed. A similar cam surface 17 is also formed on the right side surface of FIG. The plurality of rollers 15 are supported so as to be rotatable about an axis extending in the radial direction with respect to the input shaft 1.

  In the toroidal type continuously variable transmission having such a configuration, when the input shaft 1 is rotated, the cam plate 13 is rotated along with the rotation of the input shaft 1, and the plurality of rollers 15, 15 are connected to the input side disk by the cam surface 16. 2 is pressed by the cam surface 17 provided on the outer side surface of the head. As a result, the input side disk 2 is pressed against the plurality of power rollers 11, 11, and at the same time, based on the pressing between the pair of cam surfaces 16, 17 and the rolling surfaces of the plurality of rollers 15, 15. The input side disk 2 rotates. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the power rollers 11 and 11, and the output shaft 3 fixed to the output side disk 4 rotates.

  When the rotational speeds of the input shaft 1 and the output shaft 3 are changed, and when deceleration is performed between the input shaft 1 and the output shaft 3, the trunnions 6 and 6 are swung around the pivot shafts 5 and 5. As shown in FIG. 7, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 are arranged near the center of the inner surface 2a of the input side disk 2 and the outer periphery of the inner side surface 4a of the output side disk 4, respectively. The displacement shafts 9 and 9 are inclined so as to abut each other.

  On the other hand, when the speed is increased, the trunnions 6 and 6 are swung so that the peripheral surfaces 11a and 11a of the power rollers 11 and 11 have the inner surface 2a of the input side disk 2 as shown in FIG. Each of the displacement shafts 9 and 9 is inclined so as to come into contact with the outer peripheral portion and the central portion of the inner side surface 4 a of the output side disk 4. If the inclination angle of each of the displacement shafts 9 and 9 is set intermediate between those shown in FIGS. 7 and 8, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.

  9 and 10 show an example of a more specific double cavity type toroidal continuously variable transmission. In addition, about the structural member which is common in FIG.7 and FIG.8, the same code | symbol is attached | subjected below and the detailed description or illustration is abbreviate | omitted.

  As shown in FIG. 9, the input shaft 1 is rotatably supported inside the casing 101. The first and second input side disks 2 and 2 are supported at portions near both ends of the input shaft 1, respectively. In this case, the first and second input side disks 2 and 2 are concentrically arranged with their inner side surfaces 2a and 2a facing each other, and can rotate in synchronization with each other inside the casing 101. .

  Around the intermediate portion of the input shaft 1, first and second output side disks 4, 4 are supported via a sleeve 109. An output gear 110 is integrally provided on the outer peripheral surface of the intermediate portion of the sleeve 109. The output gear 110 is disposed concentrically with the input shaft 1 and has an inner diameter larger than the outer diameter of the input shaft 1. The output gear 110 is rotatably supported by a support wall (intermediate wall) 111 provided in the casing 101 via a pair of rolling bearings 112.

  The first and second output side disks 4 and 4 are splined to both ends of the sleeve 109. In this case, the output side disks 4 and 4 are arranged with their inner side surfaces 4a and 4a facing in opposite directions. Accordingly, the input side disk 2 and the output side disk 4 have their inner side surfaces 2a, 4a facing each other.

  As shown in FIG. 10, a pair of yokes 113a and 113b are supported inside the casing 101 and laterally of the output side disks 4 and 4 with both the disks 4 and 4 being sandwiched from both sides. . The pair of yokes 113a and 113b are formed in a rectangular shape by pressing or forging a metal such as steel. In order to support the pivots 5 provided at both ends of the trunnion 6 to be described later in a swingable manner, circular support holes 118 are provided at the four corners of the yokes 113a and 113b, and the width direction of the yokes 113a and 113b. A circular locking hole 119 is provided at the center of the.

  The pair of yokes 113a and 113b are supported so as to be slightly displaceable by support posts 20a and 20b formed on portions of the inner surface of the casing 101 facing each other. These support posts 20a and 20b are respectively provided so as to face the first cavity 21 and the second cavity 22 between the inner side surface 2a of the input side disk 2 and the inner side surface 4a of the output side disk 4, respectively. Yes.

  Accordingly, the yokes 113 a and 113 b are supported by the support posts 20 a and 20 b, and one end thereof faces the outer peripheral portion of the first cavity 21 and the other end faces the outer peripheral portion of the second cavity 22. is doing.

  Since the first and second cavities 21 and 22 have the same structure, only the first cavity 21 will be described below.

  The first cavity 21 is provided with a pair of trunnions 6. Concentric shafts 5 are provided concentrically at both ends of the trunnion 6, and these pivots 5 are supported by one end portions of a pair of yokes 113a and 113b so as to be swingable and axially displaceable. That is, the pivot 5 is supported by the radial needle bearing 26 inside the support hole 118 formed at one end of the yokes 113a and 113b. The radial needle bearing 26 includes an outer ring 27 whose outer peripheral surface is a spherical convex surface and whose inner peripheral surface is a cylindrical surface, and a plurality of needles 28.

  A circular hole 30 is provided in each intermediate portion of the trunnion 6. A displacement shaft 31 is supported in each circular hole 30. Each of the displacement shafts 31 includes a support shaft portion 33 and a pivot shaft portion 34 that are parallel to each other and eccentric. Among these, the support shaft portion 33 is supported inside the circular hole 30 via a radial needle bearing 35. The power roller 11 is supported around the pivot shaft 34 via another radial needle bearing 38.

  A pair of displacement shafts 31 provided for each of the first and second cavities 21 and 22 is provided at a position 180 degrees opposite to the input shaft 1 for each of the first and second cavities 21 and 22. It has been. In addition, the direction in which each pivot shaft 34 of the displacement shaft 31 is eccentric with respect to each support shaft 33 is the same as the rotational direction of the input disks 2, 2 and the output disks 4, 4. The eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 is disposed. Therefore, the power roller 11 is supported so that it can be slightly displaced along the longitudinal direction of the input shaft 1. As a result, when the power roller 11 tends to be displaced in the axial direction of the input shaft 1 due to fluctuations in the amount of elastic deformation of the constituent members based on fluctuations in torque transmitted by the toroidal continuously variable transmission. However, an excessive force is not applied to the constituent members, and the displacement can be absorbed.

  A thrust ball bearing 39 and a thrust bearing 40 such as a slide bearing or a needle bearing are provided between the outer peripheral surface of the power roller 11 and the inner peripheral surface of the trunnion 6 in order from the outer surface of the power roller 11. It has been. Among these, the thrust ball bearing 39 allows rotation of the power roller 11 while supporting a load in the thrust direction applied to the power roller 11. The thrust bearing 40 allows the pivot shaft 34 and the outer ring 41 to swing around the support shaft 33 while supporting a thrust load applied to the outer ring 41 of the thrust ball bearing 39 from the power roller 11. .

  A drive rod 42 is coupled to one end of the trunnion 6. A drive piston 43 as a drive device is fixed to the outer peripheral surface of the intermediate portion of these drive rods 42. The drive piston 43 is oil-tightly fitted in the drive cylinder 44. The drive piston 43 constitutes an actuator for displacing the trunnion 6 in the axial direction.

  As shown in FIG. 9, a loading cam type pressing device 45 is provided between the drive shaft 200 that receives power from the engine and the one input side disk 2. The pressing device 45 includes a cam plate 46 and a plurality of rollers 48, and rotates one input side disk 2 while pressing it toward the other input side disk 2 based on the rotation of the drive shaft 200. In this case, the cam plate 46 is engaged with the drive shaft 200 and rotates together with the drive shaft 200. The plurality of rollers 48 are held by a holder 47 so as to be freely rollable.

  During operation of the toroidal continuously variable transmission configured as described above, the rotation of the drive shaft 200 is transmitted to one input side disk 2 via the pressing device 45, and this input side disk 2 and the other input side disk are transmitted. The disk 2 and the input shaft 1 rotate in synchronization with each other. The rotation of the input side disks 2 and 2 is transmitted to the output side disks 4 and 4 via the power roller 11. The rotation of the output side disks 4 and 4 is taken out by the output gear 110 and transmitted to the output shaft 201.

  When the rotational speed ratio between the input shaft 1 and the output gear 110 is changed, a pair is provided corresponding to the first and second cavities 21 and 22 based on switching of control valves (not shown). The drive piston 43 thus moved is displaced by the same distance in the opposite directions for each of the cavities 21 and 22. Along with the displacement of these drive pistons 43, a total of four trunnions 6 are displaced in the opposite direction, and one power roller 11 is displaced downward and the other power roller 11 is displaced upward. As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 act on contact portions between the inner side surfaces 2a and 2a of the input side disks 2 and 2 and the inner side surfaces 4a and 4a of the output side disks 4 and 4, respectively. The direction of the tangential force changes. As the direction of the force changes, the trunnion 6 swings in the reverse direction around the pivot shaft 5 pivotally supported by the yokes 113a and 113b. As a result, the contact position between the peripheral surface of the power roller 11 and the input side disks 2 and 2 and the output side disks 4 and 4 changes, and the rotational speed ratio between the input shaft 1 and the output gear 110 changes. .

  By the way, the yokes 113a and 113b, which support the pivot shaft 5 of the trunnion 6 so as to be swingable and axially displaceable, swing themselves around the support posts 20a and 20b. A pair of trunnions facing each other in the same cavity so that the other trunnion 6 (for example, the left trunnion in FIG. 10) is displaced downward in accordance with the upward displacement of 6 (for example, the right trunnion in FIG. 10) 6 has a function to synchronize the movements of the 6 like a seesaw and displace them in opposite directions.

  FIG. 11 shows a specific example of conventional yokes 113a and 113b. As shown in the figure, the yokes 113a and 113b are formed in a rectangular shape, and have circular support holes 118 at the four corners for swingably supporting the pivot shaft 5 of the trunnion 6, and support posts 20a and 20b are formed in the inside. A locking hole 119 to be fitted is provided at the center in the width direction.

  Further, in order to allow the yokes 113a and 113b to swing smoothly around the support posts 20a and 20b, a protrusion 220 serving as a swinging fulcrum is provided on one side of each locking hole 119. , 113b (see, for example, Patent Document 1). Specifically, on the outer side in the longitudinal direction of each locking hole 119 of the first yoke 113a located on the upper side in FIG. 10, as shown in FIG. 220 is integrally formed. Similarly, protrusions 220 projecting toward the upper cylinder body 230 of the cylinder 44 are integrally formed on the outer sides in the longitudinal direction of the respective locking holes 119 of the second yoke 113b located on the lower side in FIG. Has been.

  Therefore, for example, when the left drive piston 43 in FIG. 10 is displaced downward and the right drive piston 43 is displaced upward in FIG. 10, the trunnions 6, 6 coupled to these drive pistons 43. Are displaced in the opposite directions (the left trunnion 6 is displaced downward and the right trunnion 6 is displaced upward). As a result, as shown in FIG. The projections 220 are inclining about the protrusions 220 that are in contact with the fixing member 225 of the casing 101 in the direction in which the right side is upward. Similarly, the second yoke 113b is also inclined in the same direction as the first yoke 113a, with each protrusion 220 in contact with the upper cylinder body 230 of the cylinder 44 as the center. Conversely, when the left drive piston 43 is displaced upward in FIG. 10 and the right drive piston 43 is displaced downward in FIG. 10, as shown in FIG. 113a is inclined in the direction in which the left side is up, centering on each protrusion 220 that is in contact with the fixing member 225 of the casing 101. Similarly, the second yoke 113b is also in the same direction as the first yoke 113a. Tilt.

JP 2003-343673 A

  However, the conventional yokes 113a and 113b shown in FIG. 11 are formed integrally with the main bodies of the yokes 113a and 113b in the protruding portions 220 as the swing fulcrum. Therefore, it is necessary to process the protrusion 220 into the yoke body with high accuracy so as to function as a swing fulcrum. Accordingly, there arises a problem that the processing work becomes troublesome and complicated, and the manufacturing cost increases.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a toroidal-type continuously variable transmission in which a projection serving as a swing fulcrum of a yoke can be provided at low cost.

  In order to achieve the object, the toroidal continuously variable transmission according to claim 1 is supported concentrically and rotatably in a state in which the inner surfaces of the toroidal continuously variable transmission face each other inside the casing. The input side disk and the output side disk, the plurality of power rollers sandwiched between the two disks, and the twisted position with respect to the central axis of the input side disk and the output side disk, and concentric with each other A plurality of trunnions that swing about a pair of pivots provided on the shaft and that rotatably support the power rollers, a drive device that displaces the trunnions in the axial direction of the pivots, and The pivot shaft includes a pair of yokes that support the pivots so as to be swingable and displaceable in the axial direction, and swing by the displacement of the trunnion. In the idal-type continuously variable transmission, a projection serving as a fulcrum for the swing of each yoke is provided on each of the yokes or a facing member facing each of the yokes. Or it is formed and attached separately from the said opposing member, It is characterized by the above-mentioned.

  In the first aspect of the present invention, each yoke or an opposing member (for example, a casing or a cylinder that houses a piston for displacing the trunnion) has a protrusion serving as a fulcrum for the swing of the yoke. Is provided. Therefore, when each yoke swings so as to synchronize the displacement operation of each trunnion supported by these yokes, the swinging operation is smooth because the yoke swings around the projection. Therefore, the displacement operation of each trunnion supported by each yoke is stabilized, and the transmission characteristics of the toroidal continuously variable transmission are stabilized.

  In addition, since the protrusion is attached to the yoke or the counter member separately from the yoke or the counter member, the processing conditions of the protrusion and the processing conditions of the yoke or the counter member can be set separately, and there are various situations. In addition to being able to set both materials individually according to the process, it is possible to loosen the dimensional accuracy and simplify the machining process, etc., compared to the case where the yoke and the projection are integrally formed as in the prior art. it can. As a result, the degree of freedom in design can be increased, and manufacturing can be simplified and manufacturing cost can be reduced.

  In the above configuration, the protrusion may be a sphere. Further, the protrusion may be a pin having an arcuate surface at an end thereof that contacts the opposing member or the yoke. The protrusion may be a cylindrical pin. Furthermore, the protrusion may be attached to the yoke or the opposing member by press-fitting or caulking (Claim 5).

  In the toroidal-type continuously variable transmission of the present invention, the projections serving as fulcrums for the swinging of the yokes are provided on the yokes or the opposing members facing the yokes, and the projections are arranged on the yokes or the opposing surfaces. Formed and attached separately from the member. For this reason, it is possible to provide a protrusion serving as a swing fulcrum at low cost.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The feature of the present invention lies in the formation of the protrusions that serve as the fulcrum of the swing of the yoke, and other configurations and functions are the same as the conventional configurations and functions described above. Only the characteristic part will be mentioned, and the other parts will be simply described with the same reference numerals as those in FIGS.

  1 and 2 show yokes 113a and 113b according to the first embodiment of the present invention. As shown in the figure, in the yokes 113a and 113b according to the present embodiment, recessed grooves (circular or cylindrical holes) 300 are formed on both sides of the locking holes 119 into which the support posts 20a and 20b are fitted. ing. In each of these grooves 300, a protrusion 320 as a sphere formed separately from the yokes 113a and 113b is attached by press-fitting or caulking. In addition, in the attached state, these protrusions 320 protrude outside the groove 300 by a predetermined amount, and are opposed members facing the respective yokes 113a and 113b (in the first yoke 113a, the casing 101 is fixed). The member 225 is a counter member, and in the second yoke 113b, the upper cylinder body 230 of the cylinder 44 is in contact with the counter member) and functions as a fulcrum for swinging of the yokes 113a and 113b. It is like that. That is, the same function as that of the protrusion 220 shown in FIG. 12 is achieved.

  Thus, in the present embodiment, each of the yokes 113a and 113b is provided with a protrusion 320 that abuts against a corresponding opposing member and serves as a fulcrum for the swing of the yokes 113a and 113b. Accordingly, when the yokes 113a and 113b swing to synchronize the displacement operation of the trunnions 6 supported by the yokes 113a and 113b, the yokes 113a and 113b swing about the protrusion 320, so that the swinging operation becomes smooth. Therefore, the displacement operation of each trunnion 6 supported by each yoke 113a, 113b is stabilized, and the shift characteristic of the toroidal type continuously variable transmission is stabilized. Further, since the protrusion 320 is attached to the yokes 113a and 113b separately from the yokes 113a and 113b, the processing conditions of the protrusion 320 and the processing conditions of the yokes 113a and 113b can be set separately. Both materials can be individually set in accordance with various situations, and the dimensional accuracy and the like are loosened compared to the case where the yokes 113a and 113b and the protrusion 320 are integrally formed, thereby simplifying the machining process and the like. You can also. As a result, the degree of freedom in design can be increased, and manufacturing can be simplified and manufacturing cost can be reduced. Further, since the protrusion 320 is attached to the yokes 113a and 113b by press fitting or caulking, the protrusion 320 does not fall out of the groove 300 of the yokes 113a and 113b.

  3 and 4 show yokes 113a and 113b according to the second embodiment of the present invention. This embodiment is a modification of the first embodiment, and pin-shaped protrusions 330 formed separately from the yokes 113a and 113b are attached to the recessed grooves 300 by press-fitting or crimping. ing. Further, in the mounted state, these projecting portions 330 project a predetermined amount outside the groove 300, and the projecting end surface 330a forms an arcuate surface to be an opposing member that faces each yoke 113a, 113b. It comes to contact. That is, also in this case, the protrusion 330 functions as a fulcrum for swinging of the yokes 113a and 113b. Therefore, the same effect as the first embodiment can be obtained.

  5 and 6 show yokes 113a and 113b according to a third embodiment of the present invention. This embodiment is also a modification of the first embodiment, and concave long grooves (rectangular holes) 300a are formed on both sides of the locking holes 119 of the yokes 113a and 113b. A columnar (pin-shaped) projection 340 formed separately from the yokes 113a and 113b is attached by press-fitting or caulking. Further, in the mounted state, these protrusions 330 protrude from the long groove 300a by a predetermined amount with the axial generatrix (side surface of the cylindrical body) facing outward, and the protruding end surface (one side surface of the cylindrical body). Part) 340a comes into contact with the opposing members facing the yokes 113a and 113b. Therefore, the same effect as the first embodiment can be obtained.

Needless to say, the present invention is not limited to the above-described embodiments, and can be variously modified without departing from the scope of the invention. For example, in the above-described embodiment, the grooves 300 and 300a for attaching the protrusions 320, 330, and 340 serving as the swing fulcrums of the yokes 113a and 113b are provided on both sides of each locking hole 119. It may be provided only on one side of the locking hole 119. Further, the material of the yoke and the material of the protrusion may be the same or different. The shape of the protrusion may be any shape other than a sphere or a pin as long as it functions as a swing fulcrum. In addition, as a form of attaching the protrusion to the yoke, any form (for example, adhesion, welding, etc.) other than press-fitting and caulking can be employed.
Further, in the above-described embodiment, the protrusions serving as the pivot points of the yoke are provided on the yokes 113a and 113b. However, the opposing members (fixing member 225 and upper cylinder body 230) facing the yoke are provided with the first portion. Even if a projection having the same shape as that of the third embodiment is provided, the same effect can be obtained.

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

It is a perspective view of the yoke which concerns on the 1st Embodiment of this invention. (A) is a top view of the yoke of FIG. 1, (b) is sectional drawing in alignment with the AA direction of (a), (c) is sectional drawing in alignment with the BB direction of (a). It is a perspective view of the yoke which concerns on the 2nd Embodiment of this invention. (A) is a top view of the yoke of FIG. 3, (b) is sectional drawing in alignment with CC direction of (a), (c) is sectional drawing in alignment with DD direction of (a). It is a perspective view of the yoke which concerns on the 3rd Embodiment of this invention. (A) is a top view of the yoke of FIG. 5, (b) is sectional drawing in alignment with the EE direction of (a), (c) is sectional drawing in alignment with the FF direction of (a). It is a side view which shows the fundamental structure of the toroidal type continuously variable transmission conventionally known in the state at the time of maximum deceleration. It is a side view which shows the basic structure of the toroidal type continuously variable transmission conventionally known in the state at the time of maximum acceleration. It is sectional drawing which shows an example of the conventional concrete structure. It is sectional drawing which follows the GG line of FIG. It is a top view of the conventional yoke. It is the schematic which shows the rocking | fluctuation state of the yoke of FIG.

Explanation of symbols

2 Input side disk 4 Output side disk 5 Axis 6 Trunnion 11 Power roller 43 Drive piston (drive device)
101 Casing 113a, 113b Yoke 320, 330, 340 Projection

Claims (5)

A casing, an input-side disk and an output-side disk that are supported concentrically and rotatably with the inner surfaces facing each other inside the casing, and a plurality of sandwiched between the two disks The power roller swings about a pair of pivots that are concentrically arranged with respect to the center axis of the input side disk and the output side disk, and each power roller is rotatable. A plurality of trunnions that are supported on the shaft, a drive device that displaces each trunnion in the axial direction of the pivot, and supports each pivot of each trunnion so as to be swingable and axially displaceable. In a toroidal continuously variable transmission comprising a pair of yokes that swing by displacement,
Protrusions that serve as fulcrums for the swinging of the yokes are provided on the yokes or opposing members that oppose the yokes, and the protrusions are formed separately from the yokes or the opposing members. A toroidal-type continuously variable transmission characterized by being mounted.   The toroidal continuously variable transmission according to claim 1, wherein the protrusion is a sphere.   2. The toroidal continuously variable transmission according to claim 1, wherein the protruding portion is a pin having an arc-shaped surface at an end portion thereof that abuts against the opposing member or the yoke.   The toroidal continuously variable transmission according to claim 3, wherein the protrusion is a cylindrical pin.   The toroidal continuously variable transmission according to any one of claims 1 to 4, wherein the protrusion is attached to the yoke or the opposing member by press-fitting or caulking.

Images