WO2021220904A1 - Transmission toroïdale à variation continue - Google Patents

Transmission toroïdale à variation continue Download PDF

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Publication number
WO2021220904A1
WO2021220904A1 PCT/JP2021/016139 JP2021016139W WO2021220904A1 WO 2021220904 A1 WO2021220904 A1 WO 2021220904A1 JP 2021016139 W JP2021016139 W JP 2021016139W WO 2021220904 A1 WO2021220904 A1 WO 2021220904A1
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WO
WIPO (PCT)
Prior art keywords
stopper
disc
transmission
disk
ball
Prior art date
Application number
PCT/JP2021/016139
Other languages
English (en)
Japanese (ja)
Inventor
賢司 小松
秀幸 今井
吉平 松田
Original Assignee
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 川崎重工業株式会社 filed Critical 川崎重工業株式会社
Publication of WO2021220904A1 publication Critical patent/WO2021220904A1/fr

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    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/06—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement
    • 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

  • This disclosure relates to a toroidal continuously variable transmission.
  • the toroidal continuously variable transmission includes an input disc and an output disc, and a power roller sandwiched between these discs. Power is transmitted from the input disc to the output disc by rotating the power roller. At that time, the output can be decelerated or accelerated steplessly by changing the inclination of the power roller (that is, changing the contact radius with the input disk and the output disk).
  • At least one of the discs is assembled to the rotating shaft via a ball spline.
  • the ball spline is an outer spline groove formed on the inner peripheral surface of the disc, an inner spline groove formed on the outer peripheral surface of the rotating shaft, and a plurality of balls rotatably provided between these spline grooves. It consists of.
  • Some toroidal continuously variable transmissions have a structure for preventing the balls of the ball spline from falling off.
  • Patent Document 1 discloses this type of toroidal continuously variable transmission.
  • Patent Document 1 In the toroidal continuously variable transmission of Patent Document 1, a ball spline provided between a rotating shaft and a disc by a tubular stopper tightly fitted on the rotating shaft (spindle) between the axial directions of a pair of opposing discs. The ball is prevented from coming off. A part of the tubular stopper described in Patent Document 1 is inserted into the spline groove. The cylindrical stopper is movable relative to the axis of rotation in the axial direction and may collide with the disc and the portion of the axis of rotation forming the spline groove.
  • tubular stopper described in Patent Document 1 has a tubular portion in which a part thereof is inserted into a spline groove and a flange portion that protrudes radially outward from the tubular portion.
  • This cylindrical stopper is movable relative to the rotation axis in the axial direction, and the flange portion may collide with the main body portion of the disc.
  • the cylindrical stopper collides with the disk and / or the rotating shaft in the axial direction and receives an axial load from them. Since the tubular stopper has a wall thickness that can withstand this load, it is difficult to reduce the weight. Similarly, the disc and / or the portion of the rotating shaft that the cylindrical stopper collides with must also have rigidity.
  • the conventional toroidal continuously variable transmission has room for improvement from the viewpoint of reducing the weight of the ball spline and the mechanism associated therewith. Therefore, the present disclosure proposes a technique for preventing the balls of a ball spline provided between a disc and a rotating shaft from falling off in a toroidal continuously variable transmission, which can realize weight reduction.
  • the toroidal continuously variable transmission is A rotating shaft extending in the axial direction, a first disk and a second disk inserted through the rotating shaft so that the main surfaces face each other in the axial direction, and an inclination between the first disk and the second disk.
  • a power roller sandwiched in a rollable manner and a ball spline for supporting the first disc on the rotating shaft are provided.
  • the rotating shaft includes a disc arranging portion having a plurality of inner spline grooves formed on the outer peripheral surface, a stopper arranging portion provided on one shaft end side of the disc arranging portion, and the shaft end of the stopper arranging portion. It has an engaging surface provided on the side and facing the shaft end side.
  • the first disc has an inner peripheral surface on which a plurality of outer spline grooves are formed.
  • the ball spline includes a plurality of balls arranged in a ball accommodating portion formed by a combination of the inner spline groove and the outer spline groove arranged in the radial direction, and the shaft end from the ball accommodating portion of the plurality of balls. It has a stopper that regulates movement to the side,
  • the stopper includes a tubular body that is externally fitted to the stopper arranging portion, and a plurality of pins that protrude from the tubular body in the axial direction and are inserted into the ball accommodating portion without contacting at least the tip portion with the groove wall. It is characterized by having an inner flange that protrudes inward in the radial direction from the tubular body and engages with the engaging surface.
  • the ball of the ball spline is restricted from moving to the shaft end side by the pin inserted in the ball accommodating portion, and is prevented from falling off from the ball accommodating portion. Since the pin is inserted into the ball accommodating portion without contacting the groove wall, the stopper does not contact the disc and does not contact the formed portion of the inner spline groove of the rotating shaft. Further, the engagement between the engaging surface and the inner flange restricts the stopper from moving toward the ball accommodating portion with respect to the rotation axis. Therefore, the stopper does not receive the axial load directly from the disk and the rotating shaft.
  • the strength against the axial load required for the stopper can be suppressed, the thickness of the stopper can be reduced, and the weight of the stopper can be reduced. Further, since the stopper does not collide with the rotating shaft and the groove-forming portion of the disc, the strength against the axial load required for these can be suppressed. As a result, the diameter of the rotating shaft can be reduced, which in turn can contribute to the weight reduction of the rotating shaft.
  • a technique for preventing a ball of a ball spline provided between a disc and a rotating shaft from falling off, which can realize weight reduction, is provided. Can be done.
  • FIG. 1 is a cross-sectional view of a drive mechanism integrated power generation device including a toroidal continuously variable transmission according to an embodiment of the present invention.
  • FIG. 2 is an enlarged view of the output disk and pressing device of the toroidal continuously variable transmission shown in FIG. 1 and their vicinity.
  • FIG. 3 is an enlarged cross-sectional view of a ball spline provided between the transmission output shaft and the output disc.
  • FIG. 4 is a perspective view of the stopper.
  • FIG. 1 is a cross-sectional view of a drive mechanism integrated power generation device 1 including a toroidal continuously variable transmission 10 according to the present embodiment.
  • the integrated drive generator 1 IDG
  • the casing 2 houses an input mechanism 3, a toroidal continuously variable transmission (hereinafter, simply referred to as “transmission 10”), a power transmission mechanism 7, and a generator 5.
  • the transmission 10 does not have to be a part of the drive mechanism integrated power generation device 1, and its use is not limited to aircraft.
  • the transmission 10 includes a transmission input shaft 11 and a transmission output shaft 9 that are coaxially arranged and can rotate relative to each other.
  • rotary axis A1 the axis lines of the transmission input shaft 11 and the transmission output shaft 9 will be referred to as “rotary axis A1”.
  • axis direction X the extending direction of the rotation axis A1 is referred to as "axis direction X”.
  • the axial direction X of the rotating axis A1 is, that is, the axial direction X of the main shaft of the transmission 10.
  • the transmission input shaft 11 is connected to an engine rotation shaft (not shown) via an input mechanism 3.
  • the input mechanism 3 includes a device input shaft 3a to which rotational power from the engine rotation shaft is input, and a gear 3b that rotates integrally with the device input shaft 3a.
  • the transmission input shaft 11 is provided with a gear 6 that rotates integrally with the transmission input shaft 11.
  • the transmission output shaft 9 is connected to the generator input shaft 5a of the generator 5 via
  • the rotational power taken out from the engine rotary shaft is input to the transmission input shaft 11 via the input mechanism 3, and the rotational power of the transmission input shaft 11 is transmitted to the input disk 13.
  • the transmission 10 shifts the rotation of the transmission input shaft 11 and outputs the rotation to the transmission output shaft 9.
  • the rotational power of the transmission output shaft 9 is transmitted to the generator input shaft 5a via the power transmission mechanism 7.
  • the generator input shaft 5a When the generator input shaft 5a is rotationally driven, the generator 5 generates AC power.
  • the gear ratio of the transmission 10 is set so that the rotation speed of the generator input shaft 5a is kept at an appropriate value (a value corresponding to a frequency suitable for the operation of the electrical components of the aircraft) regardless of the fluctuation of the rotation speed of the engine rotation shaft. It changes continuously.
  • the transmission 10 is a half toroidal type and a double cavity type, and includes two sets of input discs 13 and 13 and output discs 14 and 15.
  • the transmission 10 is not limited to the double cavity type, and may be, for example, a single cavity type.
  • the input disks 13 and 13 are fitted to the transmission input shaft 11, and rotate around the rotation axis A1 integrally with the transmission input shaft 11.
  • the output disc 14 is fitted to the transmission output shaft 9 and rotates integrally with the transmission output shaft 9 about the rotation axis A1.
  • the output disk 15 is supported by the transmission output shaft 9 via the ball spline 16, rotates around the rotation axis A1 integrally with the transmission output shaft 9, and has an axis with respect to the transmission output shaft 9. Movement in direction X is allowed.
  • the input disc 13 has a concave surface 13a.
  • the output disks 14 and 15 have concave surfaces 14a and 15a.
  • the surface on which the concave surfaces 13a, 14a and 15a are formed is referred to as a "main surface", and the surface on the opposite side thereof is referred to as a "back surface”.
  • the input disc 13 and the output disc 14 are arranged so as to face each other in the axial direction X so that the concave surfaces 13a and 14a face each other.
  • the input disc 13 and the output disc 15 are arranged to face each other in the axial direction X so that the concave surfaces 13a and 15a face each other.
  • An annular cavity is formed around the rotation axis A1 by the opposing concave surfaces 13a, 14a, 13a, 15a.
  • the transmission 10 is a central input type as an example.
  • the transmission output shaft 9 is inserted into the transmission input shaft 11 and projects from the transmission input shaft 11 on both sides in the axial direction X.
  • the pair of input discs 13 and 13 are central discs and are arranged back to back on the transmission input shaft 11.
  • the pair of output disks 14 and 15 are external disks, and are arranged outside the pair of input disks 13 and 13 in the axial direction X. Between the pair of input disks 13 and 13, a gear 6 provided on the outer peripheral surface of the transmission input shaft 11 and rotating integrally with the transmission input shaft 11 is arranged.
  • the output disc 14 on one side is regulated to be displaced outward from the rotation axis A1 by a convex portion 9a provided at the end of the transmission output shaft 9.
  • the output disc 15 on the other side is urged toward the input disc 13 by the preload spring 64, and is urged toward the input disc 13 by the pressing device 17 during rotational drive.
  • the output disk 15 is connected to the power transmission mechanism 7 via a pressing device 17 so as to be able to transmit power.
  • the transmission 10 includes a plurality of power rollers 18 arranged in the cavity and a plurality of trunnions 19 that support the plurality of power rollers 18 so as to be tiltable.
  • the trunnion 19 is supported by the casing 2 in a state where it can be tilted around the tilt axis A2 and can be displaced in the tilt axis A2 direction.
  • the tilt axis A2 is in a twisted position with the rotation axis A1.
  • the power roller 18 is rotatably supported by the trunnion 19 around a rotation axis (not shown) perpendicular to the tilt axis A2.
  • the trunnion 19 is connected to a hydraulic drive mechanism (not shown), and the hydraulic drive mechanism reciprocates the trunnion 19 together with the power roller 18 in the tilting axis A2 direction.
  • FIG. 2 is an enlarged view of the output disk 15 and the pressing device 17 of the toroidal continuously variable transmission 10 shown in FIG. 1 and their vicinity.
  • the pressing device 17 has a cam plate 61 and a roller unit 60.
  • the cam plate 61 is loosely fitted to the transmission output shaft 9 so as to face the back surface of the output disk 15.
  • the cam plate 61 integrally has a hollow disk-shaped cam portion 611 and a cylindrical tubular shaft portion 612 projecting from the outer peripheral edge portion of the cam portion 611 in the axial direction X.
  • the main surface of the cam portion 611 faces the back surface of the output disk 15.
  • the main surface of the cam portion 611 is the first cam surface 613, and irregularities are repeatedly formed over the circumferential direction.
  • a second cam surface 151 is provided on the back surface of the output disk 15 facing the first cam surface 613. Concavities and convexities are repeatedly formed on the second cam surface 151 in the circumferential direction so as to correspond to the first cam surface 613.
  • the roller unit 60 is provided between the first cam surface 613, the second cam surface 151, and the axial direction X.
  • the roller unit 60 includes a cage 62 and a plurality of rollers 63 held by the cage 62.
  • the cage 62 holds a plurality of roller sets arranged at substantially equal intervals in the circumferential direction about the rotation axis A1.
  • One set of rollers includes at least one roller 63 (three in this embodiment) aligned along the radial axis of rotation. Each roller 63 of the roller set can rotate about the rotation axis of the roller set.
  • Each roller 63 is sandwiched between the first cam surface 613 and the second cam surface 151, and its peripheral surface comes into contact with both the first cam surface 613 and the second cam surface 151.
  • the support bearing 4 is an angular contact ball bearing.
  • the support bearing 4 is arranged on the back surface side of the cam plate 61 and supports the cam plate 61 on the transmission output shaft 9 so as to be relatively rotatable.
  • the support bearing 4 has an inner ring 41, an outer ring 42, and a plurality of rolling elements 43 rotatably sandwiched between the inner ring 41 and the outer ring 42.
  • the inner ring 41 is fixed to the transmission output shaft 9 by being sandwiched between the transmission output shaft 9 and the nut 51 screwed into the transmission output shaft 9.
  • the outer ring 42 is rotatable with respect to the inner ring 41, and the outer ring 42 rotates integrally with the cam plate 61 about the rotation axis A1.
  • a preload spring 64 is arranged between the cam plate 61 and the outer ring 42 of the support bearing 4.
  • the preload spring 64 applies a pressing force in the axial direction X toward the output disc 15 to the cam plate 61 so that the output disc 15 is pressed (preloaded) toward the input disc 13 even when the transmission output shaft 9 is not rotating. It is to be given.
  • the preload spring 64 according to the present embodiment is sandwiched between the cam portion 611 of the cam plate 61 and the outer ring 42 of the support bearing 4, and is compressed in the axial direction X. When the preload spring 64 is compressed, the tubular shaft portion 612 of the cam plate 61 also comes into contact with the outer ring 42.
  • External teeth 614 are formed on the outer peripheral surface of the tubular shaft portion 612 of the cam plate 61.
  • the external teeth 614 mesh with the internal teeth 711 provided in the first gear 71 of the power transmission mechanism 7 to form a dog clutch.
  • the power transmission mechanism 7 transmits the output from the transmission 10 to the generator 5 and the oil pump unit (not shown).
  • the power transmission mechanism 7 is composed of a plurality of gears including the first gear 71 to the fourth gear 74.
  • the first gear 71 is a hollow gear.
  • the first gear 71 has internal teeth 711 and external teeth 712.
  • the internal teeth 711 mesh with the external teeth 614 of the cam plate 61, and the external teeth 712 mesh with the second gear 72.
  • the second gear 72 has a main tooth 721 and an auxiliary tooth 722.
  • the main tooth 721 meshes with the outer teeth 712 of the first gear 71 and the third gear 73.
  • the auxiliary teeth 722 mesh with a gear (not shown) for transmitting the output of the transmission 10 to the oil pump unit (not shown).
  • the third gear 73 meshes with the main teeth 721 and the fourth gear 74 of the second gear 72.
  • the fourth gear 74 is fixed to the generator input shaft 5a of the generator 5.
  • the power roller 18 is sandwiched between the concave surfaces 13a of the input discs 13 and 13 and the concave surfaces 14a and 15a of the output discs 14 and 15 in a state where it can be tilted around the tilting axis A2, and drives the rotation of the input discs 13.
  • the force is changed at a gear ratio according to the tilt angle and transmitted to the output discs 14 and 15.
  • the pressing device 17 presses the output disc 15 in a direction approaching the input disc 13, and the pressure between the input discs 13 and 13 and the output discs 14 and 15 increases to sandwich the power roller 18. do.
  • FIG. 3 is an enlarged cross-sectional view of a ball spline 16 provided between the transmission output shaft 9 and the output disc 15. In FIG. 3, some components are omitted.
  • the transmission output shaft 9 (an example of a rotating shaft) is a hollow shaft, and the inside of the shaft functions as an oil passage 90.
  • the transmission output shaft 9 is formed with a screw portion 92, a bearing support portion 93, a stopper arranging portion 94, and a disc arranging portion 95 in this order from one shaft end 91.
  • a male screw 921 that meshes with the female screw of the nut 51 is formed on the outer peripheral surface of the screw portion 92.
  • the inner ring 41 of the support bearing 4 is fitted onto the bearing support portion 93.
  • an engaging surface 96 facing the shaft end 91 side in the axial direction X is formed due to the difference in diameter between the two. That is, the engaging surface 96 is a stepped surface between the bearing support portion 93 and the stopper arranging portion 94.
  • a stopper 30, which will be described later, is fitted onto the stopper arranging portion 94.
  • the stopper arranging portion 94 is provided with a small diameter portion 941 and a large diameter portion 942 having a diameter larger than that of the small diameter portion 941 and located on the shaft end 91 side.
  • the outer peripheral surface of the disk arrangement portion 95 is a groove forming portion 951.
  • a plurality of inner spline grooves 952 arranged in the circumferential direction are formed in the groove forming portion 951.
  • Each inner spline groove 952 is a groove having a semicircular cross section extending in the axial direction X and opening outward in the radial direction.
  • the inner peripheral surface of the output disk 15 that faces the disk arrangement portion 95 of the transmission output shaft 9 in the radial direction is a groove forming portion 153.
  • a plurality of outer spline grooves 154 arranged in the circumferential direction are formed in the groove forming portion 153.
  • the number of inner spline grooves 952 corresponds to the number of outer spline grooves 154.
  • Each outer spline groove 154 is a groove having a semicircular cross section that extends in the axial direction X and opens inward in the radial direction.
  • the ball spline 16 includes a ball accommodating portion 55 formed between the outer peripheral surface of the transmission output shaft 9 and the inner peripheral surface of the output disk 15, and a plurality of balls arranged in the ball accommodating portion 55. It has 56 and a stopper 30 for preventing the plurality of balls 56 from falling from the ball accommodating portion 55 toward the shaft end 91 side.
  • the ball accommodating portion 55 is a cylindrical space extending in the axial direction X, which is formed by a combination of an inner spline groove 952 and an outer spline groove 154 arranged in the radial direction.
  • a plurality of ball accommodating portions 55 are arranged at equal intervals in the circumferential direction between the outer peripheral surface of the transmission output shaft 9 and the inner peripheral surface of the output disk 15.
  • At least one ball 56 (four in the present embodiment) is rotatably arranged in each ball accommodating portion 55.
  • FIG. 4 is a perspective view of the stopper 30.
  • the stopper 30 includes a tubular body 31, a plurality of pins 32 protruding from the tubular body 31 in the axial direction X, and an inner flange 33 protruding radially inward from the tubular body 31. Have one.
  • the tubular body 31 is a thin cylindrical member extending in the axial direction X, and is externally fitted to the stopper arranging portion 94 of the transmission output shaft 9.
  • a roller unit 60 and a cam plate 61, which are components of the pressing device 17, are arranged on the outer peripheral side of the tubular body 31.
  • the radius R31b of the inner circumference of the cylinder 31 and the radius R942 of the large diameter portion 942 of the stopper arranging portion 94 are the inner peripheral surface of a part of the cylinder 31 (the portion on the shaft end 91 side) and the outer circumference of the large diameter portion 942. Corresponds to contact with the surface (R31b ⁇ R942). As a result, the centering of the transmission output shaft 9 and the stopper 30 is performed by the operation of fitting the stopper 30 to the transmission output shaft 9. That is, the inner peripheral surface of the tubular body 31 and the outer peripheral surface of the large diameter portion 942 of the stopper arranging portion 94 form an in-row portion between the stopper 30 and the transmission output shaft 9.
  • the cylinder 31 has an oil groove continuous in the circumferential direction and an oil hole for discharging hydraulic oil from the oil groove to the outside in the radial direction at a position corresponding to the radial oil passage provided in the transmission output shaft 9. Is formed. Hydraulic oil is collected in the oil groove by centrifugal force, and this hydraulic oil is ejected from the oil holes. In this way, since the hydraulic oil path is formed between the stopper arranging portion 94 and the tubular body 31, the stopper 30 fitted to the transmission output shaft 9 allows the stopper 30 to enter from the oil passage 90 of the transmission output shaft 9. The supply of hydraulic oil to the pressing device 17 is not hindered.
  • the plurality of pins 32 have a pin shape (rod shape) protruding from one end surface of the axial direction X of the tubular body 31 toward the ball accommodating portion 55.
  • the plurality of pins 32 are arranged at equal intervals in the circumferential direction.
  • the radius R32b of the inner diameter of the ring formed by the plurality of pins 32 is equal to the radius R31b of the inner circumference of the tubular body 31 (R32b ⁇ R31b).
  • the radius R31b and the radius R32b are larger than the distance R95 from the rotation axis A1 to the groove bottom of the inner spline groove 952 (R31b> R95, R32b> R95).
  • the radius R32a of the outer circumference of the ring formed by the plurality of pins 32 is smaller than the radius R31a of the outer circumference of the tubular body 31 (R32a ⁇ R31a).
  • the radius R32a is smaller than the distance R154 from the rotation axis A1 to the groove bottom of the outer spline groove 154 (R32a ⁇ R154).
  • the radius R31a of the outer circumference of the tubular body 31 is the same as or slightly larger than the distance R154 from the rotation axis A1 to the groove bottom of the outer spline groove 154 (R31a ⁇ R154).
  • a recess 321 is formed on the tip surface of each pin 32.
  • Each recess 321 is a spherical recess corresponding to the curvature of the ball 56, and a part of the ball 56 can be fitted into the recess 321.
  • the recess 321 on the tip surface of each pin 32 is not essential, and the tip surface of each pin 32 may be flat.
  • the tubular body 31, the plurality of pins 32, and the inner flange 33 are integrally molded.
  • the molding method of the stopper 30 is not limited to this, and a plurality of pins 32 may be formed by scraping the meat of the portion other than the pins 32 from the cylindrical material.
  • the radial positions of the plurality of pins 32 correspond to the positions of the radial central portion of the ball accommodating portion 55.
  • the circumferential positions of the plurality of pins 32 correspond to the circumferential positions of the plurality of ball accommodating portions 55.
  • the cross section of each pin 32 is smaller than the cross section of the ball accommodating portion 55. At least the tip of each of the plurality of pins 32 is inserted into the ball accommodating portion 55.
  • each pin 32 is not in contact with the groove wall of the outer spline groove 154 and the groove wall of the inner spline groove 952.
  • the inner flange 33 is provided at the end of the tubular body 31 on the shaft end 91 side.
  • the inner flange 33 has an engaging surface 96 of the transmission output shaft 9 and a seat surface 331 that abuts in the axial direction X.
  • the inner flange 33 is fixed to the transmission output shaft 9 by being sandwiched between the nut 51 screwed into the threaded portion 92 of the transmission output shaft 9 and the engaging surface 96. More specifically, an inner flange 33, a shim 49 for preload adjustment, and an inner ring 41 are sandwiched between the engaging surface 96 of the transmission output shaft 9 and the axial direction X of the nut 51.
  • the stopper 30 is inserted through the transmission output shaft 9.
  • the stopper 30 is positioned in the axial direction X.
  • the tubular body 31 of the stopper 30 is located radially outside the stopper arranging portion 94 of the transmission output shaft 9.
  • the pin 32 of the stopper 30 has a tip portion inserted into the ball accommodating portion 55, and is not in contact with any of the ball 56, the output disc 15, and the transmission output shaft 9.
  • the roller unit 60, the cam plate 61, and the preload spring 64 are inserted in this order through the transmission output shaft 9 on which the stopper 30 is externally mounted. Subsequently, the shim 49 and the support bearing 4 are inserted into the bearing support portion 93 of the transmission output shaft 9 in this order. Finally, the nut 51 is screwed into the threaded portion 92 of the transmission output shaft 9. As described above, the shaft assembly of the transmission 10 is assembled.
  • the toroidal continuously variable transmission 10 shifts so that the transmission output shaft 9 (an example of a rotating shaft) extending in the axial direction X and the main surfaces face each other in the axial direction X.
  • An output disk 15 (an example of a first disk) and an input disk 13 (an example of a second disk) inserted through the machine output shaft 9, a ball spline 16 for supporting the output disk 15 on the transmission output shaft 9, and an output disk.
  • a power roller 18 sandwiched between the 15 and the input disk 13 so as to be tiltable is provided.
  • the transmission output shaft 9 has a disc arrangement portion 95 in which a plurality of inner spline grooves 952 are formed on the outer peripheral surface, and a stopper arrangement provided on one shaft end 91 side of the disc arrangement portion 95. It has a portion 94 and an engaging surface 96 provided on the shaft end 91 side of the stopper arranging portion 94 and facing the shaft end 91 side.
  • the output disk 15 has an inner peripheral surface on which a plurality of outer spline grooves 154 are formed.
  • the ball spline 16 is a shaft from a plurality of balls 56 arranged in a ball accommodating portion 55 formed by a combination of an inner spline groove 952 and an outer spline groove 154 arranged in the radial direction, and a ball accommodating portion 55 of the plurality of balls 56. It has a stopper 30 that regulates the movement toward the end 91 side. Then, the stopper 30 protrudes from the tubular body 31 outerly fitted to the stopper arranging portion 94 and the tubular body 31 in the axial direction X, and at least the tip portion thereof is inserted into the ball accommodating portion 55 without contacting the groove wall. It has a plurality of pins 32 and an inner flange 33 that protrudes inward in the radial direction from the tubular body 31 and engages with the engaging surface 96.
  • the ball 56 of the ball spline 16 is restricted from moving toward the shaft end 91 by the pin 32 inserted in the ball accommodating portion 55, and the ball 56 is prevented from falling off from the ball accommodating portion 55.
  • the stopper 30 Since the pin 32 is inserted into the ball accommodating portion 55 without contacting the groove wall, the stopper 30 is in contact with the forming portion (groove forming portion 951) of the inner spline groove 952 of the output disk 15 and the transmission output shaft 9. Do not touch. Further, the engagement between the engaging surface 96 and the inner flange 33 restricts the stopper 30 from moving toward the ball accommodating portion 55 with respect to the rotation axis A1.
  • the stopper 30 does not receive the load in the axial direction X from the output disk 15 and the transmission output shaft 9. As a result, the strength against the load required for the stopper 30 in the axial direction X is suppressed, so that the tubular body 31 of the stopper 30 can be made thinner, which in turn can contribute to the weight reduction of the stopper 30. Further, since the stopper 30 does not collide with the groove forming portion 951 of the transmission output shaft 9, the strength against the load in the axial direction X required for the groove forming portion 951 is suppressed, so that the diameter of the transmission output shaft 9 can be reduced. As a result, it is possible to contribute to the weight reduction of the transmission output shaft 9.
  • the faces have corresponding radii so that they come into contact with each other.
  • the plurality of pins 32 have recesses 321 on the tip surface into which the balls 56 fit.
  • the pin 32 and the ball 56 come into contact with each other on the surface. Therefore, as compared with the case where the pin 32 and the ball 56 come into contact with each other at a point, the load applied from the ball 56 to the pin 32 is dispersed, so that the strength against the load in the axial direction X required for the pin 32 is suppressed. This can contribute to the thinning (diameter reduction) of the pin 32.
  • the output disk 15 has a notch 155 in the inner peripheral portion on the back surface.
  • the tubular body 31 of the stopper 30 has a radius equal to or larger than the radius of the groove bottom of the outer spline groove 154. Further, the end portion of the tubular body 31 can be brought closer to the ball accommodating portion 55, and the length of the pin 32 can be shortened by that amount. As a result, the strength against the load required for the pin 32 in the axial direction X is suppressed. This can contribute to the thinning (diameter reduction) of the pin 32.
  • the transmission 10 includes a pressing device 17 that presses the output disk 15 toward the input disk 13, a bearing 4 that rotatably supports the pressing device 17 on the transmission output shaft 9, and a bearing.
  • a nut 51 for fixing the 4 to the transmission output shaft 9 is further provided.
  • the inner flange 33 is sandwiched between the engaging surface 96 and the nut 51 in the axial direction X.
  • the tubular body 31 of the stopper 30 since the tubular body 31 of the stopper 30 does not receive the load in the axial direction X directly from the output disk 15 and the transmission output shaft 9, the tubular body 31 has a length of the axial direction X corresponding to the pressing device 17. However, buckling is unlikely to occur in the tubular body 31. Therefore, the end portion of the tubular body 31 provided with the inner flange 33 can be extended to the vicinity of the bearing 4. Then, the inner flange 33 of the stopper 30 is fastened to the transmission output shaft 9 with the nut 51 together with the bearing 4, so that the stopper 30 is fixed to the transmission output shaft 9. Therefore, a dedicated member for fixing the stopper 30 to the transmission output shaft 9 is unnecessary.
  • the transmission 10 is not limited to the central input type, but may be a central output type.
  • the central output type the positional relationship between the input disk 13 and the output disk 14 described above is reversed, the output disk becomes the central disk (second disk), and the input disk becomes the outer disk (first disk).
  • the pressing device 17 is configured to press the input disc toward the output disc, and rotation is input to the cam plate 61 from a gear that meshes with the external teeth 614.
  • Support bearing 9 Transmission output shaft (example of rotating shaft) 10: Toroidal continuously variable transmission 13: Input disc (an example of the second disc) 14: Output disk 15: Output disk (example of the first disk) 32: Pin 33: Inner flange 51: Nut 55: Ball accommodating portion 56: Ball 91: Shaft end 94: Stopper arrangement portion 95: Disc arrangement portion 96: Engagement surface 153: Groove forming portion 154: Outer spline groove 155: Notch 321 : Recessed portion 951: Groove forming portion 952 : Inner spline groove X : Axial direction

Abstract

La présente invention concerne une transmission toroïdale à variation continue comprenant : un arbre de rotation ; un premier disque et un second disque ; au moins un rouleau motorisé ; et une cannelure à billes destinée à porter le premier disque sur l'arbre de rotation. La cannelure à billes comprend : une pluralité de billes disposées dans une partie logement de billes formée entre la périphérie externe de l'arbre de rotation et la périphérie interne du premier disque ; et un bouchon destiné à empêcher le glissement de la pluralité de billes hors de la partie logement de billes, et leur déplacement vers l'extrémité d'arbre. Le bouchon comprend : un corps cylindrique ajusté extérieurement à une partie de placement de bouchon ; une pluralité de broches faisant saillie dans la direction axiale à partir du corps cylindrique, au moins leurs sections de pointe étant introduites dans la partie logement de billes et ne se mettant pas en contact avec une paroi de rainure ; et une bride interne faisant saillie radialement vers l'intérieur à partir du corps cylindrique, et étant en prise avec une surface d'entrée en prise.
PCT/JP2021/016139 2020-04-27 2021-04-21 Transmission toroïdale à variation continue WO2021220904A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020077946A JP7449769B2 (ja) 2020-04-27 2020-04-27 トロイダル無段変速機
JP2020-077946 2020-04-27

Publications (1)

Publication Number Publication Date
WO2021220904A1 true WO2021220904A1 (fr) 2021-11-04

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PCT/JP2021/016139 WO2021220904A1 (fr) 2020-04-27 2021-04-21 Transmission toroïdale à variation continue

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Country Link
JP (1) JP7449769B2 (fr)
WO (1) WO2021220904A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0614604U (ja) * 1992-07-27 1994-02-25 日本精工株式会社 トロイダル型無段変速機
JP2002364663A (ja) * 2001-06-05 2002-12-18 Nsk Ltd ボールスプライン
JP2003139209A (ja) * 2001-11-01 2003-05-14 Nsk Ltd トロイダル型無段変速機
JP2004076940A (ja) * 2002-08-02 2004-03-11 Nsk Ltd トロイダル型無段変速機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0614604U (ja) * 1992-07-27 1994-02-25 日本精工株式会社 トロイダル型無段変速機
JP2002364663A (ja) * 2001-06-05 2002-12-18 Nsk Ltd ボールスプライン
JP2003139209A (ja) * 2001-11-01 2003-05-14 Nsk Ltd トロイダル型無段変速機
JP2004076940A (ja) * 2002-08-02 2004-03-11 Nsk Ltd トロイダル型無段変速機

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JP2021173342A (ja) 2021-11-01

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