WO2018096983A1 - トロイダル無段変速機 - Google Patents

トロイダル無段変速機 Download PDF

Info

Publication number
WO2018096983A1
WO2018096983A1 PCT/JP2017/040956 JP2017040956W WO2018096983A1 WO 2018096983 A1 WO2018096983 A1 WO 2018096983A1 JP 2017040956 W JP2017040956 W JP 2017040956W WO 2018096983 A1 WO2018096983 A1 WO 2018096983A1
Authority
WO
WIPO (PCT)
Prior art keywords
axial
diameter
fitting surface
surface portion
axial direction
Prior art date
Application number
PCT/JP2017/040956
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
井上　智博
吉平 松田
秀幸 今井
謙一郎 田中
Original Assignee
日本精工株式会社
川崎重工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日本精工株式会社, 川崎重工業株式会社 filed Critical 日本精工株式会社
Publication of WO2018096983A1 publication Critical patent/WO2018096983A1/ja

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/09—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
    • F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
    • F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces

Definitions

  • the present invention relates to a toroidal continuously variable transmission incorporated in various industrial machines such as generators including aircraft generators, pumps, vehicles including automobiles, and construction machines.
  • a toroidal continuously variable transmission having a structure described in Japanese Patent Laid-Open No. 2003-214516 has already been used as a transmission for automobiles.
  • a power split system in which the adjustment range of the gear ratio is widened by combining a toroidal continuously variable transmission and a planetary gear mechanism as described in Japanese Patent Application Laid-Open No. 2004-169719 has been already known.
  • FIG. 4 shows an example of a conventional toroidal continuously variable transmission.
  • This conventional structure includes a rotating shaft 1 and a pair of outer disks 2a and 2b supported via respective ball splines 3 around portions near both ends of the rotating shaft 1 in the axial direction.
  • Each of the pair of outer disks 2a and 2b has axial side surfaces (inner side surfaces) each formed by a toroidal curved surface having a circular arc cross section, and is disposed in a state where these axial side surfaces face each other. .
  • the pair of outer disks 2 a and 2 b can be moved far and away from each other by the ball spline 3, and can be rotated in synchronization with each other via the rotating shaft 1.
  • a cylindrical member 4 is supported around an intermediate portion in the axial direction of the rotating shaft 1 so as to be able to rotate relative to the rotating shaft 1.
  • a gear 5 is fixed at the axial center of the outer peripheral surface of the cylindrical member 4, and the inner disk 6 is synchronized with the cylindrical member 4 at both axial ends of the outer peripheral surface of the cylindrical member 4. Supported for rotation.
  • the inner disk 6 is constituted by a pair of elements 56.
  • the pair of elements 56 constituting the inner disk 6 have axial side surfaces each formed by a toroidal curved surface having an arc cross section, and the axial side surfaces of the pair of elements 56 are defined as a pair of outer disks. It arrange
  • Each of the portions between the pair of outer disks 2a and 2b disposed at the axially opposite ends of the rotating shaft 1 and the inner disk 6 disposed at the axially intermediate portion of the rotating shaft 1 has a plurality of powers.
  • a roller 7 is sandwiched.
  • Each of the plurality of power rollers 7 has a circumferential surface made of a partially spherical convex surface.
  • the plurality of power rollers 7 are individually and rotatably supported by corresponding trunnions 8.
  • the plurality of power rollers 7 sandwiched between the pair of outer disks 2a, 2b and the inner disk 6 are rotated in accordance with the rotation of the pair of outer disks 2a, 2b. Power is transmitted from the disks 2a, 2b to the inner disk 6.
  • the plurality of power rollers 7 transmit power from the inner disk 6 to the pair of outer disks 2 a and 2 b while rotating with the rotation of the inner disk 6.
  • the pair of outer disks 2a and 2b supported on the axially opposite ends of the rotating shaft 1 rotate synchronously while being pressed in a direction approaching each other.
  • the rotation of the pair of outer disks 2 a and 2 b is transmitted to the inner disk 6 through a plurality of power rollers 7 on both sides and taken out from the gear 5.
  • power from a drive source is input to the inner disk 6 via the gear 5 and the cylindrical member 4, and a pair of outer disks 2 a, via a plurality of power rollers 7 disposed on both sides of the inner disk 6, Power can be transmitted to 2b and power can be extracted from the pair of outer disks 2a and 2b.
  • Preload springs 11a and 11b are provided in the vicinity of both ends in the axial direction of the rotary shaft 1 so as to sandwich the pair of outer disks 2a and 2b from both sides in the axial direction. Even when 10 is not in operation (when the drive shaft 9 is stopped), the rolling contact portions (traction portions) of the peripheral surfaces of the plurality of power rollers 7 and the side surfaces of the pair of outer disks 2a and 2b and the inner disk 6 Contact pressure is secured only to the minimum necessary. Therefore, each rolling contact portion can start power transmission without causing excessive slip immediately after the start of operation of the toroidal continuously variable transmission.
  • the elastic force for securing the necessary minimum surface pressure can be obtained only by the preload spring 11b disposed on the inner diameter side of the pressing device 10 on the axial base end side of the rotating shaft 1. .
  • the preload spring 11a disposed between the loading nut 12 screwed to the axial front end (one end) of the rotary shaft 1 and the outer surface of the outer disk 2a alleviates the impact applied when the pressing device 10 is suddenly operated. Therefore, from the viewpoint of reducing the number of parts and improving the assembly work efficiency, as described in JP-A-2003-139209, rotation is possible.
  • the structure is such that the preload spring 11a on the tip side (one end side) of the shaft 1 is omitted, and the outer disk 2a is supported relative to the rotating shaft 1 so as not to be relatively rotatable by spline engagement without the ball spline 3 being interposed. Proposed. Further, in place of the loading nut 12, a structure in which an outward flange-like flange is provided at the tip of the rotating shaft 1, a structure in which a locking ring called a cotter is locked at the tip of the rotating shaft 1, etc. are also known. It has been.
  • the female spline portion provided in the hole is spline-engaged to support the outer disk so as to be able to rotate in synchronization with the rotation axis.
  • the stress caused by the elastic deformation of the outer disk caused by the pressing force of the power roller is easily concentrated on the spline engaging part between the male spline part of the rotating shaft and the female spline part of the outer disk.
  • fretting wear is likely to occur due to a gap existing in the spline engaging portion.
  • an outer cylindrical surface portion 15 is provided in a state adjacent to the female spline portion 14 in the center hole 13 of the outer disk 2c disposed on one end side (tip side) in the axial direction of the rotating shaft 1a, and
  • An inner cylindrical surface portion 17 is provided on the outer peripheral surface of the rotating shaft 1 a so as to be adjacent to the male spline portion 16.
  • the female spline portion 14 and the male spline portion 16 are spline-engaged, but also the outer cylindrical surface portion 15 and the inner cylindrical surface portion 17 are fitted with an interference fit over the entire axial length.
  • the disc-side step surface 18 provided in the center hole 13 of the outer disc 2c and the shaft-side step surface 19 provided on the outer peripheral surface of the rotating shaft 1a abut on each other in the axial direction.
  • the structure shown in FIG. 5 still has room for improvement in terms of improving the assembly work efficiency of the toroidal continuously variable transmission. That is, when the outer disk 2c is assembled around the rotary shaft 1a, the outer cylinder 2c of the outer disk 2c comes before the female spline part 14 of the outer disk 2c and the male spline part 16 of the rotary shaft 1a are spline-engaged. The surface portion 15 and the inner cylindrical surface portion 17 of the rotating shaft 1a are fitted with an interference fit. For this reason, the operation
  • the axial length ⁇ from the disc-side stepped surface 18 to one axial end portion (right end portion in FIG. 6) of the female spline portion 14a is set to the shaft side. It can be considered that the axial length from the step surface 19 to the other axial end portion (left end portion in FIG. 6) of the inner cylindrical surface portion 17 is longer than the axial length ⁇ . However. If such a configuration is simply adopted, a new problem arises that the outer disk 2c becomes unnecessarily large.
  • the present invention is a structure capable of suppressing the occurrence of fretting wear at the spline engaging portion, and can improve the assembly work efficiency without increasing the size of the outer disk.
  • the purpose is to realize the structure of the transmission.
  • the toroidal continuously variable transmission of the present invention includes a rotating shaft, a pair of outer disks, an inner disk, and a plurality of power rollers.
  • the rotating shaft has a male spline portion and an axial other end side in order from one axial end side to the other axial end side of the rotating shaft on one axial end portion of the rotating shaft on the outer peripheral surface.
  • a shaft-side step surface that is directed, and a large-diameter inner fitting surface portion and an inner fitting surface portion including a small-diameter inner fitting surface portion having a smaller outer diameter than the large-diameter inner fitting surface portion.
  • the “axial direction” means the axial direction of the rotating shaft unless otherwise specified.
  • Each of the pair of outer disks has axial side surfaces (inner side surfaces) each formed of a toroidal curved surface having an arcuate cross section, and the axial directions of the rotating shafts in a state where the axial side surfaces face each other. It is supported by the part near both ends so that the rotation synchronizing with this rotating shaft is possible.
  • the inner disk has axial side surfaces each formed of a toroidal curved surface having an arc cross section on both sides in the axial direction, and the rotation is performed with the axial side surfaces opposed to the axial side surfaces of the pair of outer disks.
  • the shaft is supported around an intermediate portion in the axial direction so as to be able to rotate relative to the rotation shaft.
  • an inner side structure can also take an integral structure, each can also be comprised by a pair of element provided with the said axial direction side surface.
  • the plurality of power rollers are individually and rotatably supported by a plurality of support members (for example, trunnions).
  • Each of the plurality of power rollers has a circumferential surface formed of a partially spherical convex surface, and the circumferential surface is in contact with an axial side surface of the inner disk and an axial side surface of the pair of outer disks.
  • one outer disk provided on one end side in the axial direction of the rotating shaft has an inner peripheral surface (center hole) in order from the other end side in the axial direction to one end side in the axial direction.
  • a small-diameter outer fitting surface portion, an outer fitting surface portion including a large-diameter outer fitting surface portion having a larger inner diameter than the small-diameter outer fitting surface portion, a disk-side step surface facing one end in the axial direction, and the outer fitting A female spline portion having an inscribed circle having a diameter larger than that of the mating surface portion.
  • the female spline portion is spline-engaged with the male spline portion
  • the large-diameter outer fitting surface portion is the large-diameter inner fitting.
  • the surface portion is fitted (press-fit) with an interference fit
  • the small-diameter outer fitting surface portion is fitted (press-fit) with the small-diameter inner fitting surface portion.
  • the toroidal continuously variable transmission according to the present invention further includes a pressing device
  • the pressing device is connected to the other outer disk provided on the other axial end side of the pair of outer disks. And the rotary shaft, and is configured to press the other outer disk toward one axial end (one outer disk).
  • a mechanical pressing device incorporating a loading cam or a hydraulic pressing device including a hydraulic cylinder and a piston is used.
  • the axial dimension from one axial end of the female spline portion to one axial end of the large-diameter outer fitting surface portion is determined from the other axial end of the male spline portion. It is preferable to make it larger than the axial dimension to the other axial end of the large-diameter inner fitting surface. Further, the axial dimension from one axial end portion of the female spline portion to one axial end portion of the small-diameter outer fitting surface portion, and the axial direction of the small-diameter inner fitting surface portion from the other axial end portion of the male spline portion. It is preferable to make it larger than the axial dimension to the other end.
  • the toroidal continuously variable transmission of the present invention it is possible to suppress fretting wear at the spline engaging portion and to improve the assembly work efficiency without increasing the size of one outer disk.
  • the outer fitting surface portion provided in the center hole of the one outer disk is divided into the large-diameter outer fitting surface portion of the axial one end portion and the axial other end portion. It is comprised by the small diameter outer fitting surface part.
  • the large-diameter outer fitting surface portion is fitted into the large-diameter inner fitting surface portion at one end portion in the axial direction, and the shaft
  • the small-diameter outer fitting surface portion is fitted into the small-diameter inner fitting surface portion of the other end portion in the direction by an interference fit.
  • the one outer disk is not only spline-engaged with the rotary shaft, but is also fitted by an interference fit at least at two axial positions (outside Therefore, the support rigidity of the outer disk with respect to the rotating shaft can be improved. For this reason, it becomes possible to suppress that fretting wear arises in this spline engaging part.
  • the large-diameter outer fitting surface portion of the outer fitting surface portions when the one outer disk is assembled around the rotation shaft from the other end side in the axial direction, the large-diameter outer fitting surface portion of the outer fitting surface portions. Is not required to be fitted to the small-diameter inner fitting surface portion provided at the other axial end portion of the inner fitting surface portion, and the large-diameter outer fitting surface portion is provided at the one axial end portion.
  • the one outer disk until it is fitted to the large-diameter inner fitting surface or until the small-diameter outer fitting surface is fitted to the small-diameter inner fitting surface provided at the other axial end portion. Can be moved toward one end in the axial direction.
  • the axial position of the one outer disk with respect to the rotating shaft is the axis of the outer fitting surface portion and the inner fitting surface portion. Compared to a cylindrical surface whose diameter dimension does not change over the direction, it can be shifted toward one end in the axial direction.
  • the outer fitting surface portion can be reduced.
  • the female spline portion can be spline-engaged with the male spline portion before the inner fitting surface portion is fitted. That is, before the outer fitting surface portion and the inner fitting surface portion are fitted with an interference fit, it is possible to perform an operation of matching the phases of the female spline portion and the male spline portion. Therefore, in the toroidal continuously variable transmission of the present invention, it is possible to improve the assembling work efficiency without enlarging one outer disk more than necessary.
  • FIG. 1 is a cross-sectional view of a toroidal continuously variable transmission showing an example of an embodiment of the present invention.
  • FIG. 2 is an enlarged cross-sectional view of a portion A in FIG.
  • FIG. 3 is a cross-sectional view similar to FIG. 2 for explaining the assembly work of one outer disk, and FIG. 3 (A) shows a state during the assembly of the one outer disk. B) shows the assembled state of the one outer disk.
  • FIG. 4 is a cross-sectional view showing a conventional toroidal continuously variable transmission.
  • FIG. 5 is a cross-sectional view showing an example of a support structure of the outer disk with respect to the rotating shaft, which the present inventors have devised before the present invention.
  • FIG. 6 is a cross-sectional view showing an example of a support structure for the outer disk with respect to the rotating shaft, which was devised by the present inventors prior to the present invention, as in FIG. 5.
  • the toroidal continuously variable transmission 20 of this example is used for an aircraft generator, for example, and includes a rotating shaft 1b, a pair of outer disks 2d and 2e, an inner disk 6a, and a plurality of power rollers 7. And a plurality of trunnions (not shown) and a hydraulic pressing device (loading device) 10a.
  • the pair of outer disks 2d and 2e corresponds to the input side disk
  • the inner disk 6a corresponds to the output side disk.
  • the rotary shaft 1b is supported on the upper side of the actuator case 21 through a pair of support columns 22 and the inner disk 6a so as to be rotatable only.
  • the inner disk 6a is rotatably supported by a thrust angular ball bearing 23 on a support ring provided in the middle part of the pair of support columns 22, and the rotating shaft 1b has an inner diameter of the inner disk 6a.
  • a pair of radial needle bearings 24 are rotatably supported on the side.
  • the “axial direction” means the axial direction of the rotating shaft 1b (the horizontal direction in FIGS. 1 to 3) unless otherwise specified.
  • the right side of FIGS. 1 to 3 that is the distal end side of the rotating shaft 1b corresponds to one axial end side
  • the left side of FIGS. 1 to 3 that is the proximal end side of the rotating shaft 1b is the other axial end side. It corresponds to.
  • Each of the pair of outer disks 2d and 2e has axial side surfaces (inner side surfaces) each formed by a toroidal curved surface having an arc cross section, and the rotating shaft 1b is in a state where the axial side surfaces face each other.
  • axial side surfaces inner side surfaces
  • the rotating shaft 1b is in a state where the axial side surfaces face each other.
  • the cylinder 25 is configured by coupling and fixing the outer peripheral edge portion of the inner diameter side cylinder element 26 and the inner peripheral edge portion of the outer diameter side cylinder element 27.
  • the inner diameter side cylinder element 26 is composed of the rotating shaft 1b.
  • the male spline part formed in the axial direction other end part part of the outer peripheral surface of this is spline-engaged.
  • a locking groove 28 is provided on the other end side in the axial direction of the rotating shaft 1b than the portion on which the inner diameter side cylinder element 26 is externally fitted.
  • a ring (cotter) 29 is locked.
  • One axial end surface of the locking ring 29 is in contact with the other axial end surface of the inner diameter side portion of the inner diameter side cylinder element 26, and the cylinder 25 is displaced in a direction away from the outer disk 2d (left side in FIG. 1). It is preventing that. Therefore, the inner diameter side cylinder element 26 does not rattle in a state where torque can be transmitted to the portion near the other end in the axial direction of the rotating shaft 1b and displacement to the other end in the axial direction is prevented. It is fitted.
  • the locking ring 29 is formed into a ring shape as a whole when a plurality of (for example, 2 to 4) partially arcuate elements are combined in the circumferential direction and locked in the locking groove 28. It is configured. Further, in order to prevent the plurality of elements constituting the locking ring 29 from coming out radially outward from the locking groove 28, the periphery of the plurality of elements is covered with a restraining ring 30.
  • the holding ring 30 is rotationally driven by a power source such as an engine, and the driving torque transmitted to the holding ring 30 is transmitted to the rotary shaft 1b and the outer disk 2e via the cylinder 25. .
  • two piston plates 31a and 31b are assembled.
  • a portion between the piston plate 31a on the one end side in the axial direction and the outer disk 2e and a portion between the piston plate 31b on the other end side in the axial direction and the bottom plate portion 32 of the cylinder 25 are double piston type pressing devices 10a.
  • the outer disk 2d provided on the right side in FIG. 1 which is one axial end side (tip side) of the rotating shaft 1b, is a shaft that is away from the outer disk 2e. It is supported by the rotating shaft 1b so that it cannot be displaced toward one end in the direction and can rotate in synchronization with the rotating shaft 1b.
  • the portion near the one end in the axial direction of the rotating shaft 1b is directed from the other end in the axial direction toward the one end (from the left side to the right side in FIGS. 1 to 3), and the small-diameter shaft portion 34 and the large-diameter shaft.
  • the portion 35 is configured in a stepped shape in which the shaft side step surface 36 is continuous.
  • the outer peripheral surface of the small diameter shaft portion 34 constitutes the inner fitting surface portion 37.
  • a male spline portion 38 having an outer diameter dimension larger than that of the remaining portion of the large diameter shaft portion 35 is provided at an axially intermediate portion of the large diameter shaft portion 35.
  • a clearance groove 39 that is recessed radially inward is provided in a portion adjacent to one end side in the axial direction of the male spline portion 38 over the entire circumference.
  • the shaft-side step surface 36 exists on a virtual plane that is orthogonal to the central axis of the rotation shaft 1b.
  • a central hole 40 penetrating in the axial direction for inserting the rotating shaft 1b is formed.
  • the center hole 40 is formed by connecting the small diameter hole portion 41 and the medium diameter hole portion 42 by the disk side step surface 43 from the other end side in the axial direction toward one end side (from the left side to the right side in FIGS. 1 to 3).
  • the medium-diameter hole portion 42 and the large-diameter hole portion 44 are formed in a stepped shape that is continuous with the disk-side flat surface 45.
  • a female spline portion 46 that can be spline-engaged with the male spline portion 38 is provided at an intermediate portion in the axial direction of the medium diameter hole portion 42.
  • the inner peripheral surface of the small diameter hole portion 41 constitutes an outer fitting surface portion 47 having an inner diameter dimension smaller than the diameter of the inscribed circle of the female spline portion 46.
  • the disk-side step surface 43 and the disk-side flat surface 45 exist on a virtual plane orthogonal to the central axis of the outer disk 2d.
  • the shaft-side step surface 36 formed on the outer peripheral surface of the rotating shaft 1b and the disk-side step surface 43 formed on the inner peripheral surface of the outer disk 2d are contacted in the axial direction.
  • the male spline portion 38 and the female spline portion 46 are spline engaged, and the inner fitting surface portion 37 and the outer fitting surface portion 47 are press-fitted or inlayed. Mates by interference fit.
  • the outer disk 2d is supported so as to be able to rotate in synchronization with the rotating shaft 1b in a state in which displacement toward one end in the axial direction is prevented with respect to a portion near the one end in the axial direction of the rotating shaft 1b. Yes.
  • the structure of the fitting portion 48 between the inner fitting surface portion 37 and the outer fitting surface portion 47 is improved as follows from the viewpoint of improving the assembly work efficiency of the toroidal continuously variable transmission 20. Is planned. That is, in the toroidal continuously variable transmission 20 of the present example, the inner fitting surface portion 37 is not a cylindrical surface whose outer diameter dimension does not change in the axial direction, but an outer periphery having a shape in which the outer diameter dimension varies depending on the axial position. It is composed of surfaces. Specifically, the inner fitting surface portion 37 includes a large-diameter inner fitting surface portion 49 at one axial end side portion, and an outer diameter smaller than the large-diameter inner fitting surface portion 49 at the other axial end portion.
  • a small-diameter inner fitting surface portion 50 having dimensions is provided. Further, an inner clearance having an outer diameter smaller than that of the small-diameter inner fitting surface portion 50 at an axially intermediate portion of the inner fitting surface portion 37 (a portion between the large-diameter inner fitting surface portion 49 and the small-diameter inner fitting surface portion 50). A part 51 is provided.
  • the outer peripheral surfaces of the large-diameter inner fitting surface portion 49 and the small-diameter inner fitting surface portion 50 are configured by cylindrical surfaces whose outer diameter dimensions do not change in the axial direction.
  • the outer fitting surface portion 47 is not a cylindrical surface whose inner diameter dimension does not change in the axial direction, but is formed by an inner peripheral surface having a different inner diameter dimension depending on the position in the axial direction. Specifically, the outer fitting surface portion 47 includes a small-diameter outer fitting surface portion 53 at the other end portion in the axial direction, and has a larger inner diameter than the small-diameter outer fitting surface portion 53 at the one axial end portion. A large-diameter outer fitting surface portion 52 is provided.
  • a portion 54 is provided.
  • the inner peripheral surfaces of the large-diameter outer fitting surface portion 52 and the small-diameter outer fitting surface portion 53 are configured by cylindrical surfaces whose outer diameter dimensions do not change in the axial direction.
  • the inner diameter dimension of the large-diameter outer fitting surface portion 52 is larger than the outer diameter dimension of the small-diameter inner fitting surface portion 50 provided in the other axial end portion of the inner fitting surface portion 37, and is one axial end side.
  • the inner diameter size of the small-diameter outer fitting surface portion 53 is slightly smaller than the outer diameter size of the small-diameter inner fitting surface portion 50 provided in the other axial end portion of the inner fitting surface portion 37. ing.
  • the inner disk 6a is supported around the intermediate portion in the axial direction of the rotating shaft 1b so as to be able to rotate relative to the rotating shaft 1b.
  • the axial side surfaces (outer side surfaces) on both sides in the axial direction of the inner disk 6a are opposed to the axial side surfaces of the outer disks 2d and 2e, respectively.
  • a plurality of power rollers 7 are sandwiched between the outer disks 2d and 2e and the inner disk 6a. These power rollers 7 transmit power from the outer disks 2d and 2e to the inner disk 6a while rotating as the outer disks 2d and 2e rotate.
  • the outer disk 2d, the inner disk 6a, and the outer disk 2e are arranged in the order of the axial direction of the rotating shaft 1b around the rotating shaft 1b.
  • a plurality of power rollers 7 are arranged in a portion between the outer disk 2d and the inner disk 6a and a portion between the outer disk 2e and the inner disk 6a.
  • the pressing device 10a is assembled around the rotation shaft 1b from the other axial end side (base end side) of the rotation shaft 1b, and the locking ring 29 and the holding ring 30 are disposed near the other axial end of the rotation shaft 1b.
  • the toroidal continuously variable transmission 20 of this example is completed by fixing.
  • the assembly work of the outer disk 2d with respect to the rotating shaft 1b is performed as follows.
  • the outer disk 2d is moved to one end side (tip side) in the axial direction of the rotating shaft 1b, and is provided at one end part in the axial direction of the center hole 40 of the outer disk 2d.
  • the periphery of the small-diameter inner fitting surface portion 50 is passed to one end in the axial direction without fitting the large-diameter outer fitting surface portion 52 to the small-diameter inner fitting surface portion 50 of the rotating shaft 1b.
  • the axial clearance A between the axial one end portion of the female spline portion 46 and the other axial end portion of the male spline portion 38 is provided at one end part in the axial direction of the center hole 40 of the outer disk 2d.
  • the dimensions of the constituent parts of the rotating shaft 1b and the outer disk 2d are regulated so that the axial gaps A, B, C having such a dimensional relationship are formed.
  • the axial dimension X1 from the axial end of the female spline portion 46 to the axial end of the large-diameter outer fitting surface portion 52 is set so that the axial clearance A is smaller than the axial clearance B.
  • the axial dimension Y1 from the other axial end of the male spline portion 38 to the other axial end of the large-diameter inner fitting surface portion 49 is made larger (X1> Y1).
  • an axial dimension X2 from one axial end of the female spline portion 46 to one axial end of the small-diameter outer fitting surface portion 53 is set so that the axial clearance A is smaller than the axial clearance C. It is larger than the axial dimension Y2 from the other axial end of 38 to the other axial end of the small-diameter inner fitting surface 50 (X2> Y2).
  • the outer disc 2d With the large-diameter outer fitting surface portion 52 positioned around the inner escape portion 51, the outer disc 2d is rotated relative to the rotating shaft 1b, thereby aligning the phases of the male spline portion 38 and the female spline portion 46. I do.
  • the input side disk 2e is further moved toward the one end side in the axial direction. Thereby, first, the male spline part 38 and the female spline part 46 are spline-engaged. Subsequently, the large-diameter inner fitting surface portion 49 and the large-diameter outer fitting surface portion 52 are fitted by an interference fit, and the small-diameter inner fitting surface portion 50 and the small-diameter outer fitting surface portion 53 are fitted by an interference fit.
  • the timing for fitting the large-diameter inner fitting surface portion 49 and the large-diameter outer fitting surface portion 52 and the timing for fitting the small-diameter inner fitting surface portion 50 and the small-diameter outer fitting surface portion 53 are axial clearances. By adjusting the sizes of B and C, it is possible to make them simultaneously, or to make one of the timings earlier than the other timing.
  • the male spline portion 38 and the female spline portion 46 are spline-engaged, the inner fitting surface portion 37 and the outer fitting surface portion 47 are loosely fitted, Since centering can be performed by this portion, the work of spline engagement can be easily performed.
  • the outer fitting surface portion 47 provided in the center hole 40 of the outer disk 2d includes a large-diameter outer fitting surface portion 52 at one end portion in the axial direction and a small-diameter outer portion at the other end portion in the axial direction. And a fitting surface portion 53. Then, among the inner fitting surface portion 37 provided on the outer peripheral surface of the rotating shaft 1b, the large-diameter outer fitting surface portion 52 is fitted into the large-diameter inner fitting surface portion 49 at one end portion in the axial direction, and the shaft The small-diameter outer fitting surface portion 53 is fitted into the small-diameter inner fitting surface portion 50 at the other end portion in the direction by an interference fit.
  • the outer disk 2d is not only spline-engaged with the rotary shaft 1b, but is also fitted (externally fitted) at two positions separated in the axial direction.
  • the support rigidity of the outer disk 2d with respect to the rotating shaft 1b can be improved. For this reason, it can suppress that fretting wear arises in the spline engaging part 55.
  • the large-diameter outer fitting surface portion 52 of the outer fitting surface portion 47 is assembled. Is not required to be fitted into the small-diameter inner fitting surface portion 50 provided at the other axial end portion of the inner fitting surface portion 37, and the large-diameter outer fitting surface portion 52 is provided at the one axial end portion.
  • the outer disk 2d is pivoted until it is fitted to the large-diameter inner fitting surface portion 49 or until the small-diameter outer fitting surface portion 53 is fitted to the small-diameter inner fitting surface portion 50 provided at the other axial end portion. It is possible to move to one end side in the direction.
  • the axial position of the outer disk 2d with respect to the rotating shaft 1a when the fitting occurs between the outer fitting surface portion 47 and the inner fitting surface portion 37 Compared to the case where the outer fitting surface portion and the inner fitting surface portion are cylindrical surfaces whose diameter dimension does not change in the axial direction, the outer fitting surface portion and the inner fitting surface portion can be shifted toward one end in the axial direction. As described above, even when the axial dimension of the female spline portion 46 is lengthened to the extent that the axial position where the fitting occurs is shifted, the outer fitting is performed.
  • the female spline portion 46 can be spline-engaged with the male spline portion 38 before the surface portion 47 and the inner fitting surface portion 37 are fitted by interference fit. That is, before the outer fitting surface portion 47 and the inner fitting surface portion 37 are fitted with an interference fit, the work of aligning the phases of the female spline portion 47 and the male spline portion 38 can be performed. As a result, in the case of this example, the assembly work efficiency of the toroidal continuously variable transmission 20 can be improved without enlarging the outer disk 2d more than necessary.
  • the female spline portion 46 is formed in a portion closer to one end (the medium diameter hole portion 42) from the axial direction intermediate portion of the outer disc 2d, but the radial direction of the outer disc 2d is related.
  • the thickness dimension (thickness) tends to become thicker toward the one end side in the axial direction because the side surface in the axial direction (the other end surface in the axial direction) is a toroidal curved surface having a circular arc cross section.
  • the female spline portion 46 is formed in a portion of the outer disk 2d where the radial thickness dimension is sufficiently large, the operation of the toroidal continuously variable transmission 20 is possible. Regardless of the stress concentration involved, it is possible to effectively prevent the occurrence of damage such as deformation.
  • an outer fitting surface part and an inner fitting surface part it is not limited to the structure of one example of embodiment mentioned above. That is, with respect to the outer fitting surface portion, a small-diameter outer fitting having a smaller inner diameter than the large-diameter outer fitting surface portion is provided on the other axial end portion while a large-diameter outer fitting surface portion is provided on one axial-side portion. It is sufficient if the surface portion is provided, and it is not always necessary to provide the outer clearance portion between the large-diameter outer fitting surface portion and the small-diameter outer fitting surface portion.
  • a small-diameter inner fitting having an outer diameter dimension smaller than that of the large-diameter inner fitting surface portion is provided on the one axial end portion and a large-diameter inner fitting surface portion on the other axial end portion. It is sufficient if the mating surface portion is provided, and it is not always necessary to provide the inner relief portion between the large-diameter inner fitting surface portion and the small-diameter inner fitting surface portion.
  • a medium-diameter outer fitting surface portion whose inner diameter dimension is intermediate between the large-diameter outer fitting surface portion and the small-diameter outer fitting surface portion is provided.
  • a medium-diameter outer fitting surface portion is provided between the large-diameter inner fitting surface portion and the small-diameter inner fitting surface portion, and the outer diameter dimension is intermediate between the large-diameter inner fitting surface portion and the small-diameter inner fitting surface portion. It is also possible to employ a configuration in which the inner side fitting surface portion is fitted with an interference fit.
  • the pair of outer disks are input disks that input power and the inner disks are output disks that output power has been described.
  • the inner disk may be an input disk for inputting power
  • the pair of outer disks may be an output disk for outputting power.
  • the present invention is not limited to the half-toroidal toroidal continuously variable transmission shown in the figure, but can be implemented with a full toroidal toroidal continuously variable transmission.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
PCT/JP2017/040956 2016-11-24 2017-11-14 トロイダル無段変速機 WO2018096983A1 (ja)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016227563A JP6705735B2 (ja) 2016-11-24 2016-11-24 トロイダル型無段変速機
JP2016-227563 2016-11-24

Publications (1)

Publication Number Publication Date
WO2018096983A1 true WO2018096983A1 (ja) 2018-05-31

Family

ID=62195128

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/040956 WO2018096983A1 (ja) 2016-11-24 2017-11-14 トロイダル無段変速機

Country Status (2)

Country Link
JP (1) JP6705735B2 (enrdf_load_stackoverflow)
WO (1) WO2018096983A1 (enrdf_load_stackoverflow)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002021961A (ja) * 2000-07-04 2002-01-23 Koyo Seiko Co Ltd トロイダル型無段変速機
JP2015090160A (ja) * 2013-11-05 2015-05-11 日本精工株式会社 トロイダル型無段変速機
JP2015152148A (ja) * 2014-02-18 2015-08-24 日本精工株式会社 トロイダル型無段変速機
WO2015151932A1 (ja) * 2014-04-02 2015-10-08 日本精工株式会社 トロイダル無段変速機
JP2015218776A (ja) * 2014-05-15 2015-12-07 日本精工株式会社 トロイダル型無段変速機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002021961A (ja) * 2000-07-04 2002-01-23 Koyo Seiko Co Ltd トロイダル型無段変速機
JP2015090160A (ja) * 2013-11-05 2015-05-11 日本精工株式会社 トロイダル型無段変速機
JP2015152148A (ja) * 2014-02-18 2015-08-24 日本精工株式会社 トロイダル型無段変速機
WO2015151932A1 (ja) * 2014-04-02 2015-10-08 日本精工株式会社 トロイダル無段変速機
JP2015218776A (ja) * 2014-05-15 2015-12-07 日本精工株式会社 トロイダル型無段変速機

Also Published As

Publication number Publication date
JP6705735B2 (ja) 2020-06-03
JP2018084282A (ja) 2018-05-31

Similar Documents

Publication Publication Date Title
WO2012111562A1 (ja) トロイダル型無段変速機
US9005066B2 (en) Motor assembly with speed reducer
JP6117991B2 (ja) トロイダル無段変速機
US11359703B2 (en) Toroidal conrtinuously variable transmission
US10746267B2 (en) Toroidal continuously variable transmission
WO2018096941A1 (ja) トロイダル無段変速機
WO2018096983A1 (ja) トロイダル無段変速機
JP6252227B2 (ja) トロイダル型無段変速機
JP6110215B2 (ja) トロイダル型無段変速機
JP2018084282A5 (enrdf_load_stackoverflow)
JP5982291B2 (ja) トロイダル型無段変速機
JP6561572B2 (ja) トロイダル型無段変速機
JP4968082B2 (ja) トロイダル型無段変速機
JP6413383B2 (ja) トロイダル型無段変速機
JP5982326B2 (ja) トロイダル型無段変速機
JP5953977B2 (ja) トロイダル型無段変速機
JP6528358B2 (ja) トロイダル型無段変速機
JP6519333B2 (ja) トロイダル型無段変速機
WO2018110446A1 (ja) トロイダル無段変速機
WO2021070816A1 (ja) トロイダル無段変速機
WO2015052950A1 (ja) シングルキャビティ式トロイダル型無段変速機
JP6528361B2 (ja) トロイダル型無段変速機
JP6561554B2 (ja) トロイダル型無段変速機
JP2015197204A (ja) トロイダル型無段変速機
JP6413367B2 (ja) トロイダル型無段変速機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17873995

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 17873995

Country of ref document: EP

Kind code of ref document: A1