WO2016143329A1 - Toroidal continuously variable transmission, and drive-mechanism-integrated power generating device for aircraft - Google Patents

Toroidal continuously variable transmission, and drive-mechanism-integrated power generating device for aircraft Download PDF

Info

Publication number
WO2016143329A1
WO2016143329A1 PCT/JP2016/001255 JP2016001255W WO2016143329A1 WO 2016143329 A1 WO2016143329 A1 WO 2016143329A1 JP 2016001255 W JP2016001255 W JP 2016001255W WO 2016143329 A1 WO2016143329 A1 WO 2016143329A1
Authority
WO
WIPO (PCT)
Prior art keywords
pivot
pair
oil passage
tilt axis
continuously variable
Prior art date
Application number
PCT/JP2016/001255
Other languages
French (fr)
Japanese (ja)
Inventor
謙一郎 田中
秀幸 今井
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 WO2016143329A1 publication Critical patent/WO2016143329A1/en

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
    • 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
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters

Definitions

  • the present invention relates to a toroidal continuously variable transmission and an aircraft drive mechanism integrated power generator.
  • the gear ratio of the toroidal continuously variable transmission is continuously changed by tilting the power roller interposed between the input disk and the output disk.
  • a power roller is attached to a trunnion having a pair of pivots, and is guided so as to tilt around a pivot centerline.
  • the trunnion has a support plate portion that supports the power roller, and a pair of bent wall portions formed at both ends thereof. The front ends of the bent wall portions are connected via a connecting member. By inserting the pin into the bent wall portion, the bent wall portion is connected to the connecting member.
  • the bent wall portion has a sufficiently large thickness (dimension in the direction of the center line of the pivot).
  • the pair of pivots protrude in the direction of the center line of the pivot from the outer surface of the bent wall portion. Therefore, the trunnion is large in the direction of the center line of the pivot.
  • an object of the present invention is to reduce the trunnion of the toroidal continuously variable transmission.
  • a toroidal continuously variable transmission includes an input disk and an output disk, which are arranged to face each other, and are tiltably sandwiched between the input disk and the output disk.
  • a power roller for transmitting force to the output disk at a gear ratio according to the tilt angle, a pair of pivot portions arranged coaxially with the tilt axis, and a pair of pivot portions in the tilt axis direction
  • a trunnion having a main body portion rotatably attached to the power roller, and a beam extending in the tilt axis direction on the side opposite to the main body portion when viewed from the power roller and coupled to the trunnion;
  • the pair of pivot parts projecting from the main body part in a projecting direction perpendicular to the tilt axis direction, and the beam is inserted into the pair of pivot parts. It is connected to the pivot portion of the pair.
  • the pair of pivot portions are coupled via the beam, and a connecting tool therefor is inserted into the pivot portion.
  • the pair of pivot portions also serve as attachment portions for connecting tools necessary for obtaining the connection reliability between the beam and the trunnion. For this reason, it is not necessary to provide a thick wall adjacent to the pair of pivot portions in the tilt axis direction, and the trunnion can be downsized in the tilt axis direction.
  • An aircraft drive mechanism integrated power generator includes the aforementioned toroidal continuously variable transmission, and an input mechanism that inputs rotational power extracted from the engine rotation shaft of the aircraft to the toroidal continuously variable transmission. And a generator driven by the output of the toroidal continuously variable transmission.
  • a space can be created between the other components of the drive mechanism-integrated power generation device and the toroidal continuously variable transmission as the trunnion is downsized.
  • Other components can be arranged in the room, and the other components can be brought close to the toroidal continuously variable transmission, which contributes to downsizing of the drive mechanism integrated power generation device.
  • the trunnion of the toroidal continuously variable transmission can be reduced in size.
  • FIG. 4A is a cross-sectional view of the trunnion along line AA in FIG. 3
  • FIG. 4B is a cross-sectional view of the trunnion along line BB in FIG. 4A
  • FIG. 4C is a trunnion along line CC in FIG.
  • FIG. 4D is a cross-sectional view of the trunnion along line DD of FIG. 4B.
  • a drive mechanism integrated power generator (Integrated Drive Generator: hereinafter referred to as “IDG”) 1 houses a generator 3 together with a toroidal continuously variable transmission (hereinafter referred to as “transmission”) 10.
  • a casing 2 is provided. IDG1 is used for the AC power supply of the aircraft, and casing 2 is attached to the engine of the aircraft.
  • the transmission 10 includes a transmission input shaft 11 and a transmission output shaft 12 that are coaxially arranged and can rotate relative to each other (hereinafter, the rotation shafts of the two shafts 11 and 12 are referred to as “transmission axis A1”). .
  • the transmission input shaft 11 is connected to the engine rotation shaft via the input mechanism 4.
  • the input mechanism 4 includes a device input shaft 4a to which rotational power extracted from the engine rotation shaft is input, and a gear pair 4b that transmits the rotation of the device input shaft 4a to the transmission input shaft 11.
  • the gear pair 4b includes a transmission gear 5a that rotates integrally with the device input shaft 4a, and a transmission input gear 5b that meshes with the transmission gear 5a and rotates integrally with the transmission input shaft 11.
  • the device input shaft 4a is parallel to the axial direction of the transmission 10, and the gear pair 4b is a parallel shaft gear pair.
  • the transmission output shaft 12 is connected to the generator input shaft 7 via a power transmission mechanism 6 (for example, a parallel shaft gear train).
  • a part of the device input shaft 4a, the gear pair 4b, the power transmission mechanism 6, and the generator input shaft 7 are also accommodated in the casing 2.
  • One or more auxiliary machines (for example, oil pumps) of the IDG 1 may be driven based on the rotational power extracted from the input mechanism 4 or the power transmission mechanism 6.
  • Rotational power extracted from the engine rotation shaft is input to the transmission input shaft 11 via the input mechanism 4.
  • the transmission 10 changes the rotation of the transmission input shaft 11 and outputs it to the transmission output shaft 12.
  • the rotation of the transmission output shaft 12 is output to the generator input shaft 7 via the power transmission mechanism 6.
  • the generator input shaft 7 rotates, the generator 3 generates AC power at a frequency proportional to the rotational speed of the generator input shaft 7.
  • the transmission ratio of the transmission 10 is an appropriate value for the rotational speed of the generator input shaft 7 regardless of fluctuations in the rotational speed of the engine rotational shaft (a value corresponding to a frequency (for example, 400 Hz) suitable for the operation of in-flight electrical components). Is continuously changed to keep As a result, the frequency is kept at a constant appropriate value.
  • the transmission 10 is a half toroidal type and a double cavity type, and includes two sets of an input disk 13 and an output disk 14.
  • the input disk 13 is provided on the outer peripheral surface of the transmission input shaft 11 so as to rotate integrally with the transmission input shaft 11.
  • the output disk 14 is provided on the outer peripheral surface of the transmission output shaft 12 so as to rotate integrally with the transmission output shaft 12.
  • the pair of discs 13 and 14 are arranged so as to face each other in the axial direction of the transmission 10, and each of the discs 13 and 14 has an annular cavity 15 that is radially outward from the two shafts 11 and 12 and continuous in the circumferential direction of the transmission shaft center A 1. Form one. Two sets of the input disk 13 and the output disk 14 and thus the two cavities 15 are arranged in the axial direction of the transmission 10.
  • the transmission 10 is a central input type.
  • the transmission output shaft 12 is inserted into the hollow transmission input shaft 11 and protrudes from the transmission input shaft 11 to both sides.
  • the two output disks 14 are divided into two projecting portions of the transmission output shaft 12.
  • the two input disks 13 are arranged back to back on the transmission input shaft 11.
  • the transmission input gear 5 b is provided on the outer peripheral surface of the transmission input shaft 11 and is disposed between the two input disks 13.
  • Elements (for example, spur gears) constituting the upstream end of the power transmission mechanism 6 are provided on the outer peripheral surface of one projecting portion of the transmission output shaft 12, and the speed is changed with reference to the output disk 14 on the projecting portion. It is arranged on the opposite side of the input disk 13 in the axial direction of the machine 10.
  • the transmission 10 includes a plurality of power rollers 16 and a plurality of trunnions 20 corresponding to the plurality of power rollers 16 on a one-to-one basis.
  • the plurality of power rollers 16 have the same structure, and the plurality of trunnions 20 have the same structure.
  • a plurality of (for example, two) power rollers 16 are disposed in one cavity 15 at equal intervals in the circumferential direction of the transmission shaft center A1.
  • the power roller 16 is supported by the corresponding trunnion 20 via the support portion 18 so as to be rotatable around the rotation axis A2.
  • tilt axis direction X The tilt axis A3 is in a twisted position with respect to the transmission axis A1, and the rotation axis A2 is perpendicular to the tilt axis A3.
  • Casing 2 stores oil used for multiple purposes. For example, oil flows into a contact portion between the power roller 16 and the input disk 13 (hereinafter referred to as “input contact portion”) and a contact portion between the power roller 16 and the output disk 14 (hereinafter referred to as “output contact portion”). Supplied as traction oil.
  • the power roller 16 is pressed against the disks 13 and 14 at a high pressure by a strong axial clamping force of the transmission 10 generated by a clamping mechanism (not shown). Thereby, a highly viscous oil film is formed in the input contact portion and the output contact portion.
  • the clamp mechanism is hydraulic, oil is supplied to the clamp mechanism as hydraulic oil.
  • tilt angle the rotation angle around the tilt axis A3 of the power roller 16 is changed, and the transmission The gear ratio of 10 is continuously changed according to the tilt angle.
  • the rotational power is transmitted from the transmission input shaft 11 to the transmission output shaft 12 by the traction drive.
  • the power roller 16 is sandwiched between the input disk 13 and the output disk 14 so as to be tiltable around the tilt axis A3, and the rotational driving force of the input disk 13 is changed at a gear ratio corresponding to the tilt angle. It is transmitted to the output disk 14.
  • the trunnion 20 has a pair of pivot portions 21 and 22 arranged coaxially, and a main body portion 23 to which the power roller 16 is rotatably attached around the rotation axis A2.
  • the center lines of the pivot portions 21 and 22 are located on the tilt axis A3 or constitute the tilt axis A3.
  • the main body portion 23 is located between the pair of pivot portions 21 and 22 in the tilt axis direction X.
  • one of the pivot portions 21 and 22 is referred to as a “first pivot portion 21”, and the other is referred to as a “second pivot portion 22”.
  • the first pivot portion 21 is fitted into the through hole 29 of the first yoke 27 through the bearing 25, and the second pivot portion 22 is fitted into the through hole 30 of the second yoke 28 through the bearing 26.
  • the pair of yokes 27 and 28 are attached to the casing 2 (see FIG. 1).
  • the trunnion 20 is supported by the casing 2 via the yokes 27 and 28 so as to be rotatable (oscillating, tilting or angular displacement) around the tilt axis A3 and displaceable in the tilt axis direction X.
  • the pair of pivot portions 21 and 22 are shaft necks inserted into the bearings 25 and 26, and are portions fitted together with the pair of yokes 27 and 28 (along with the bearings 25 and 26).
  • the yokes 27 and 28 have the same number of through holes 29 and 30 as the total number of trunnions 20. All the trunnions 20 are supported by the first yoke 27 on one side in the tilt axis direction X and supported by the second yoke 28 on the other side so that the tilt axes A3 are parallel to each other.
  • the trunnion 20 and the power roller 16 attached to the trunnion 20 are driven to be displaced in the tilt axis direction X by the hydraulic drive mechanism 31 of the IDG1.
  • the hydraulic drive mechanism 31 includes, for example, a plurality of hydraulic cylinders 32 that correspond one-to-one with the plurality of trunnions 20.
  • the hydraulic cylinder 32 has a cylinder body 33, a piston 34, and a rod 35.
  • the cylinder body 33 is fixed on a coupling surface 36 orthogonal to the tilt axis A3.
  • the coupling surface 36 is disposed on the opposite side of the transmission axis A1 in the tilt axis direction X with respect to the first yoke 27, and the cylinder body 33 has the first yoke in the tilt axis direction X with respect to the coupling surface 36. 27 on the opposite side.
  • the hydraulic cylinder 32 is, for example, a double-acting single rod type, and the piston 34 is disposed in the inner space of the cylinder body 33 so as to be able to reciprocate in the tilt axis direction X, and the inner space is divided into two oil chambers 33a, It is divided into 33b.
  • the rod 35 is fixed to the piston 34 at one end and is fixed to the first pivot portion 21 at the other end. Oil stored in the casing 2 (see FIG. 1) is supplied to the oil chambers 33a and 33b as hydraulic oil for the hydraulic drive mechanism 31.
  • the piston 34 moves in the tilt axis direction X according to the hydraulic pressure supplied to the oil chambers 33a and 33b, and the rod 35 advances and retreats in the tilt axis direction X according to the operation of the piston 34.
  • the trunnion 20 and the power roller 16 move together in the tilt axis direction X, and the tilt angle and the gear ratio of the transmission 10 are continuously changed.
  • the pair of pivot portions 21 and 22 are cylindrical, and project from both ends of the tilt axis direction X of the main body 23 in a direction perpendicular to the tilt axis A3 (hereinafter referred to as “projection direction Z”). Standing up.
  • the trunnion 20 forms a roller accommodating space 20a surrounded by the pair of pivot portions 21 and 22 and the main body 23, and the power roller 16 is disposed in the roller accommodating space 20a.
  • the surface facing the power roller housing space 20 a and facing the power roller 16 is referred to as “inner surface”.
  • the surface opposite to the inner surface in the tilt axis direction X is referred to as “outer surface”.
  • the surface opposite to the inner surface in the protruding direction Z is referred to as “outer surface”.
  • the side closer to the center of the trunnion 20 in the tilt axis direction X is referred to as “inner side”
  • the side far from this center is referred to as “outer side”.
  • the side close to the outer surface of the main body 23 in the protruding direction Z is referred to as “base end side”, and the side far from the main body 23 is referred to as “tip side”.
  • the direction perpendicular to both the tilt axis direction X and the protruding direction Z is referred to as the “width direction Y” of the trunnion 20.
  • the inner surface of the main body 23 is a plane that extends in the general XY direction, and the protruding direction Z corresponds to the height or thickness direction of the main body 23.
  • the power roller 16 has a hemispherical shape and has a curved peripheral surface 43.
  • the support shaft 45 of the support portion 18 is inserted into a circular hole 44 opened in one end face 42 of the power roller 16, and the power roller 16 is rotatably supported by the support portion 18 by bearings 48 and 49 (support shaft 45. And the center line of the circular hole 44 constitutes the rotation axis A2.)
  • the bearing 48 (for example, a radial needle roller bearing) is interposed between the support shaft 45 and the inner peripheral surface of the circular hole 44.
  • the support shaft 45 projects vertically from one end surface of the disk-shaped flange 47.
  • the bearing 49 is a thrust rolling bearing in which an inner ring is formed by the power roller 16 and an outer ring is formed by the flange 47, and a rolling element of the bearing 49 is sandwiched between one end surface 42 of the power roller 16 and one end surface of the flange 47. .
  • the support portion 18 has a mounting shaft 46 that protrudes perpendicularly from the other end surface of the flange 47, and the power roller 16 is attached to the main body portion 23 by inserting the mounting shaft 46 into a mounting hole 52 formed in the main body portion 23. It is attached and arranged in the roller accommodating space 20a.
  • the attachment hole 52 is a non-through hole extending in the protruding direction Z and opens on the inner surface of the main body 23.
  • the rotation axis A2 is directed parallel to the protruding direction Z.
  • the attachment shaft 46 is eccentric with respect to the rotation axis A2 and is inserted into the attachment hole 52 so as to be rotatable.
  • the mounting hole 52 is unevenly distributed on one side in the width direction Y as seen from the tilt axis A3 (see FIG. 4B).
  • the other end surface of the flange 47 faces the inner surface of the main body 23.
  • the support 18 is supported by the bearings 50 and 51 so as to be rotatable with respect to the main body 23.
  • a bearing 50 for example, a thrust needle roller bearing
  • a bearing 51 for example, a radial needle roller bearing
  • the main body 23 is relatively long in the tilt axis direction X and relatively short in the width direction Y.
  • the distance between the inner surfaces of the pivot portions 21 and 22 is slightly larger than the maximum diameter of the power roller 16 (for example, the diameter of the one end surface 42) (see FIG. 4B).
  • the power roller 16 is disposed between the pivot portions 21 and 22 in the tilt axis direction X, and the peripheral surface 43 faces the inner surfaces of the pivot portions 21 and 22 (see FIG. 3).
  • the width direction Y is slightly inclined with respect to the transmission axis A1 in accordance with a parallel or tilt angle with respect to the transmission axis A1 (see FIG. 1).
  • the power roller 16 partially protrudes from the main body 23 to both sides in the width direction Y for contact between the circumferential surface 43 and the disks 13 and 14 (see FIG. 1) (see FIG. 4B).
  • the pair of pivot parts 21 and 22 are connected via a beam 54 extending in the tilt axis direction X.
  • One end of the beam 54 in the tilt axis direction X is detachably connected to the first pivot 21 by the first connector 55, and the other end of the beam 54 in the tilt axis direction X is connected to the second connector 56.
  • the first connector 55 and the second connector 56 are single, and the respective pivot portions 21 and 22 are connected to the beam 54 at one point.
  • the power roller 16 In a state where the beam 54 is connected to the pair of pivot portions 21 and 22, the power roller 16 is disposed between the main body portion 23 and the beam 54 in the protruding direction Z, and the beam 54 is connected to the main body portion 23 when viewed from the power roller 16.
  • the beam 54 is connected to the trunnion 20 to reinforce the trunnion 20.
  • the trunnion 20 receives a thrust load from the power roller 16 and thereby the distal ends of the pair of pivot portions 21 and 22 try to bend inward in the tilting axis direction X, the elastic deformation can be suppressed by the beam 54. .
  • One end of the beam 54 is superimposed on the inner surface of the first pivot 21 in the tilt axis direction X.
  • the first connector 55 is inserted in the tilt axis direction X.
  • the inner surface of the first pivot portion 21 is a tip portion in the projecting direction Z and is slightly offset to the outside in the tilt axis direction X.
  • the first pivot portion 21 is a step that causes a base end portion (hereinafter referred to as “inner surface base end portion”) in the protruding direction Z of the inner surface to be continuous with a tip end portion (hereinafter referred to as “inner surface front end portion”) in the protruding direction Z of the inner surface.
  • the step surface 57 has a surface 57 and extends in the tilt axis direction X by a slight offset with respect to the inner surface proximal end portion of the inner surface distal end portion.
  • the step surface 57 extends linearly in the width direction Y, for example.
  • One end portion of the beam 54 is a base end portion (side closer to the main body portion 23) in the protruding direction Z, and is formed in a shape that matches the step surface 57 and the inner surface front end portion.
  • One end portion of the beam 54 expands in the width direction Y toward the base end side in the protruding direction Z, and the base end edge portion in the protruding direction Z extends linearly in the width direction Y, for example.
  • the first pivot portion 21 has an insertion hole 59 penetrating in the tilt axis direction X.
  • the insertion hole 59 is a stepped hole in which the inner portion in the tilt axis direction X has a smaller diameter than the outer portion, and a female screw is formed in the inner portion.
  • One end of the beam 54 has an insertion hole 61 that opens to the outer end face in the tilt axis direction X and extends in the tilt axis direction X.
  • the insertion hole 61 has a smaller diameter than the insertion hole 59.
  • the first connector 55 has a head portion 55a, a male screw portion 55b, and a non-screw portion 55c.
  • the non-screw part 55c has a circular cross section and is smaller in diameter than the male screw part 55b.
  • the first connector 55 may be a screw having a screw tip formed on a rod tip or a pointed tip.
  • the male screw portion 55 b is screwed into the inner portion of the insertion hole 59, and the head portion 55 a is abutted against the step of the insertion hole 59.
  • the head portion 55 a is immersed in the insertion hole 59 and does not protrude from the outer surface of the first pivot portion 21.
  • the non-screw part 55 c protrudes from the insertion hole 59 and is inserted into the insertion hole 61. Since the male screw portion 55 b is screwed with the first pivot portion 21, the first connector 55 can be prevented from falling off from the outer surface of the first pivot portion 21.
  • the beam 54 Since the non-threaded portion 55c is inserted into the beam 54, the beam 54 is guided with respect to the insertion hole 61 and the non-threaded portion 55c, and is inclined with respect to the first connector 55 and the first pivot portion 21 screwed with the first connector 55. Relative movement in the rotation axis direction X is possible.
  • at least a part of the first connector 55 is located inside the first pivot portion 21. In other words, in a state where the first yoke 27 is fitted into the through hole 29, at least a part of the first connector 55 is located inside the through hole 29.
  • Reference numeral 56a denotes a head
  • 56b denotes a male screw part
  • 56c denotes a non-screw part
  • 58 denotes a stepped surface
  • 60 denotes an insertion hole
  • 62 denotes an insertion hole.
  • the couplers 55 and 56 are arranged coaxially, and the insertion holes 59 and 60 and the insertion holes 61 and 62 are also arranged coaxially. These center lines extend in parallel to the tilt axis A3 at a position away from the tilt axis A3 toward the distal end side in the projecting direction Z, and pass through the center in the width direction Y of the pivot portions 21 and 22 ( (See FIGS. 4A and C).
  • the trunnion 20 has a contact surface 63 that protrudes from the outer peripheral surface of the first pivot 21 and is orthogonal to the tilt axis A3.
  • the abutting surface 63 has an annular shape, and has an inner diameter that is the same as the diameter of the first pivot portion 21 and an outer diameter that is slightly larger than the inner diameter.
  • the abutting surface 63 is configured by a step between the outer surface of the main body portion 23 and the outer peripheral surface of the first pivot portion 21 at the proximal end portion in the projecting direction Z of the first pivot portion 21.
  • the trunnion 20 has a thin wall 65 continuous with the first pivot portion 21 inside the first pivot portion 21 on the tip side.
  • the thin wall 65 is semicircular when viewed in the tilting axis direction X, and the abutting surface 63 is formed inside the distal end side of the first pivot portion 21 by the thin wall 65 and becomes an endless annular shape. .
  • the bearing 25 is fitted on the first pivot portion 21 from the outside in the tilt axis direction X. At the time of attachment, the bearing 25 is superimposed on the abutting surface 63 via the spacer 67 in the tilt axis direction X, and is positioned in the tilt axis direction X. Further, a disk-shaped bearing retainer 69 is attached to the outer surface of the first pivot portion 21. As a result, the bearing 25 can be prevented from falling off, and the insertion hole 59 is closed.
  • the second pivot portion 22 is also configured in the same manner as described above.
  • Reference numeral 64 is an abutting surface
  • 66 is a thin wall
  • 68 is a spacer
  • 70 is a bearing retainer.
  • the transmission 10 includes an oil passage 80 that supplies oil to the trunnion 20 and the power roller 16.
  • the oil passage 80 includes a first inflow oil passage 81 (see FIGS. 3 and 4A), a second inflow oil passage 82 (see FIGS. 3 and 4A), a first pivot oil passage 83 (see FIGS. 4A and B), and a first nozzle. 84 (see FIGS. 4A and B), second nozzle 85 (see FIGS. 4B and C), distribution oil passage 86 (see FIGS. 4A to C), main body oil passage 87 (see FIGS. 4A to C), second pivot oil passage 88 (see FIGS. 4B and C), and a roller oil passage 89 (see FIGS. 4B and D).
  • the first inflow oil passage 81 is formed in the rod 35 and extends in the tilt axis direction X.
  • the second inflow oil passage 82 extends in the width direction Y within the first pivot portion 21 and communicates with the first inflow oil passage 81 in the vicinity of the tilt axis A3.
  • the first pivot oil passage 83 extends in the protruding direction Z inside the first pivot portion 21.
  • the first pivot oil passage 83 communicates with the second inflow oil passage 82 at an intermediate portion in the protruding direction Z.
  • the first nozzle 84 communicates with the tip portion of the first pivot oil passage 83 in the projecting direction Z, opens to the inner surface of the first pivot portion 21, and faces the peripheral surface 43 of the power roller 16.
  • the second inflow oil passage 82 and the pivot oil passage 83 are located inside the first pivot portion 21. That is, in a state where the first yoke 27 is fitted in the through hole 29, the second inflow oil passage 82 extending in the width direction Y and the pivot oil passage 83 extending in the protruding direction Z are located inside the through hole 29. It will be.
  • the second nozzle 85 opens on the inner surface of the second pivot portion 22 and faces the peripheral surface 43 of the power roller 16.
  • the distribution oil passage 86 is connected to the second nozzle 85 from the base end portion on the base end side in the protruding direction Z of the first pivot oil passage 83 through the inside of the main body portion 23 and the second pivot portion 22.
  • the distribution oil passage 86 includes a main body oil passage 87 formed inside the main body portion 23 and a second pivot oil passage 88 formed inside the second pivot portion 22, and the first pivot oil passage 83 is a main body oil.
  • the main body oil passage 87 is communicated with the second pivot oil passage 88.
  • the main body oil passage 87 includes a first main body oil passage 87a, a second main body oil passage 87b, and a branch main body oil passage 87c.
  • the first main body oil passage 87 a extends in the tilting axis direction X inside the main body portion 23, and the base end portion in the projecting direction Z of the first pivot oil passage 83 is communicated with the mounting hole 52.
  • the mounting hole 52 is unevenly distributed on one side in the width direction Y from the tilt axis A3.
  • the first pivot portion 21 has an insertion hole 59 through which the first connector 55 is inserted at the distal end portion in the protruding direction Z. Therefore, like the mounting hole 52, the first pivot oil passage 83 is unevenly distributed on one side in the width direction Y from the tilt axis A3 and is in a position twisted with the tilt axis A3.
  • the second main body oil passage 87 b allows the mounting hole 52 to communicate with the second pivot oil passage 88.
  • the branch main body oil passage 87 c branches from the middle of the first main body oil passage 87 a, extends in the protruding direction Z, and opens on the inner surface of the main body portion 23.
  • the roller oil passage 89 includes a first roller oil passage 89a and a second roller oil passage 89b.
  • the first roller oil passage 89a opens to the other end surface of the flange 47 and the end surface of the support shaft 45, and extends in the direction of the rotation axis A2 inside the support portion 18.
  • the second roller oil passage 89b branches from the middle of the first roller oil passage 89a and extends in a direction substantially orthogonal to the rotation axis A2.
  • the oil passage 80 is configured by drilling the trunnion 20 and the support portion 18 with a tool such as a drill, and providing plugs 91-95 (see FIGS. 4A to 4C) at important points in the long holes formed thereby.
  • the plug 91 closes the open end of the non-through long hole formed in the first pivot portion 21 in order to constitute the second inflow oil passage 82.
  • the plug 92 closes the opening end of the non-through long hole formed in the first pivot portion 21 in order to constitute the first pivot oil passage 83.
  • These open ends are disposed on the outer peripheral surface of the first pivot portion 21, and the plugs 91 and 92 are externally fitted to the bearing 25, and the first yoke 27 (FIG. 3)) from the outer peripheral side in the radial direction.
  • the plug 93 closes the open end of the long hole formed in the main body portion 23 in order to constitute the first main body oil passage 87a.
  • the open end is disposed on the outer surface of the first pivot portion 21, and the plug 93 is covered with the bearing retainer 69 from the outside in the tilt axis direction X.
  • the plug 94 closes the open end of the long hole formed in the main body portion 23 in order to constitute the second main body oil passage 87b. This open end is disposed on the outer surface of the second pivot portion 22, and the plug 94 is covered with the bearing retainer 70 from the outside in the tilt axis direction X.
  • the plug 95 closes the open end of the non-through long hole formed in the second pivot portion 22 in order to constitute the second pivot oil passage 88.
  • the open end is disposed on the outer peripheral surface of the second pivot portion 22, and the plug 95 includes a bearing 26 that is fitted on the second pivot portion 22, and a second yoke 28 in which the bearing 26 is fitted (see FIG. 3). ) In the radial direction.
  • the oil stored in the casing 2 flows into the first pivot oil passage 83 via the first inflow oil passage 81 and the second inflow oil passage 82.
  • the oil flows to the tip end side in the protruding direction Z in the first pivot oil passage 83, and is sprayed from the first nozzle 84 to the peripheral surface 43 near one of the input contact portion and the output contact portion.
  • the oil flows to the proximal end side in the protruding direction Z in the first pivot oil passage 83, flows through the distribution oil passage 86, and is the peripheral surface 43 from the second nozzle 85 to the other of the input contact portion and the output contact portion. Is sprayed in the vicinity.
  • the nozzles 84 and 85 eject oil in the tangential direction of the peripheral surface 43 of the power roller 16. In this way, oil is supplied to the power roller 16 as traction oil.
  • oil is supplied as lubricating oil from the first main body oil passage 87 a to the bearing 51 in the mounting hole 52.
  • Oil flowing out from the mounting hole 52 is supplied to the second nozzle 85 via the second main body oil passage 87 b and the second pivot oil passage 88.
  • the oil is supplied as a lubricating oil to the bearing 50 through the branch main body oil passage 87c.
  • the oil supplied to the bearing 50 is supplied as the lubricating oil to the bearing 48 through the first roller oil passage 89a, and is supplied as the lubricating oil to the bearing 49 through the second roller oil passage 89b.
  • the transmission 10 is positioned between the pair of pivot portions 21 and 22 disposed coaxially with the tilt axis A3 and the pair of pivot portions 21 and 22 in the tilt axis direction X.
  • the trunnion 20 which has the main-body part 23 to which 16 is attached is provided.
  • a pair of pivot portions 21 and 22 project from the main body portion 23 in a projecting direction Z perpendicular to the tilt axis direction X.
  • the beam 54 is connected to the pair of pivot portions 21 and 22 by connecting tools 55 and 56 inserted into the pair of pivot portions 21 and 22.
  • the pair of pivot portions 21 and 22 also serve as attachment portions for the connecting tools 55 and 56 that are necessary for obtaining the connection reliability between the beam 54 and the trunnion 20. For this reason, it is not necessary to provide a thick wall adjacent to the pair of pivot portions 21 and 22 and the tilt axis direction X. As a result, the trunnion 20 can be downsized in the tilt axis direction X.
  • the thin walls 65 and 66 are expected to fulfill the function of positioning the bearings 25 and 26 mainly.
  • the dimensions of the thin walls 65 and 66 in the tilt axis direction X are determined as small as possible according to the expected function. For example, the dimensions of the thin walls 65 and 66 in the tilt axis direction X are less than 20% of the dimensions of the pivot portions 21 and 22 in the tilt axis direction X.
  • the beam 54 is overlapped with the inner surfaces of the pair of pivot portions 21 and 22 in the tilting axis direction X, and the couplers 55 and 56 are inserted in the tilting axis direction X.
  • the bearings 25 and 26 are fitted on the pivot portions 21 and 22, and the coupling tools 55 and 56 can be inserted in a direction orthogonal to the tilt axis direction X (that is, the radial direction of the pivot portions 21 and 22). Even if it is difficult, the beam 54 can be connected to the pivot portions 21 and 22.
  • an excessive shear load does not act on the couplers 55 and 56, and the coupling reliability is high.
  • the pair of pivot portions 21 and 22 have a pair of stepped surfaces 57 and 58 formed by offsetting the front end portion in the protruding direction Z of the inner surface to the outside of the tilt axis direction X, and the beam 54 extends in the protruding direction Z.
  • the beam 54 can be easily positioned in a state where it is overlapped with the inner surfaces of the pivot portions 21 and 22, and the state can be easily maintained, and the setting work of the connectors 55 and 56 can be performed easily.
  • the connecting tools 55 and 56 have non-threaded portions 55 c and 56 c inserted into the beam 54, and each of the pair of pivot portions 21 and 22 is connected to the beam 54 by a single connecting tool 55 and 56.
  • the beam 54 can move relative to the couplers 55, 56 and the pivot portions 21, 22 in the tilt axis direction X, so that the force from the trunnion 20 can be smoothly transmitted to the beam 54.
  • the first connector 55 and the second connector 56 are single and the non-threaded portions 55c and 56c are inserted into the beam 54, the beam 54 may rotate around the center line of the connectors 55 and 56. . In the present embodiment, the rotation of the beam 54 can be restricted by overlapping the stepped surfaces 57 and 58.
  • the pivot parts 21 and 22 protrude from the main body part 23 and are connected in a state of being overlapped with the beam 54 and the tilt axis direction X at the tip part.
  • the pivot portions 21 and 22 have a sufficiently large diameter so that the power roller 16 is disposed between the main body portion 23 and the beam 54 in the projecting direction Z.
  • the main body portion 23 includes a high-back portion 23a in which a mounting hole 52 is formed, and a pair of low-back portions 23b and 23c located on both sides in the width direction Y with respect to the high-back portion 23a.
  • the pair of low-profile portions 23b and 23c is thinner than the high-profile portion 23a (the dimension in the protruding direction Z is shorter), and the outer surface of the main body 23 has a step between the high-profile portion 23a and the low-profile portions 23b and 23c.
  • the high-back portion 23a has inclined portions 23d and 23e that become thinner as they move away from the attachment hole 52 in the tilt axis direction X. Since the surplus of the main body 23 is removed as much as possible, the trunnion 20 can be reduced in weight.
  • the oil passage 80 includes a first pivot oil passage 83 extending in the protruding direction Z inside the first pivot portion 21.
  • first pivot oil passage 83 oil can be supplied to a part away from the tilt axis A ⁇ b> 3 in the protruding direction Z. Since the first pivot oil passage 83 can be formed linearly, drilling can be performed easily. Since the first inflow oil passage and the second inflow oil passage are also formed linearly, the oil passage until the oil is guided to the first pivot oil passage 83 can be easily manufactured.
  • the trunnion 20 has an attachment hole 52 that opens to the inner surface of the main body 23, and the power roller 16 is attached to the main body 23 via an attachment shaft 46 that is rotatably inserted into the attachment hole 52.
  • the mounting hole 52 and the first pivot oil passage 83 are unevenly distributed on one side in the width direction Y from the tilt axis A3.
  • the oil passage 80 extends in the tilt axis direction X inside the main body portion 23, and a main body oil passage 87 (particularly, the first main body oil passage) that communicates the base end portion in the projecting direction Z of the first pivot oil passage 83 with the mounting hole 52. Including oil passage 87a).
  • the first pivot oil passage 83 and the main body oil passage 87 can be formed linearly, and drilling can be performed. It can be done easily.
  • the length of the first pivot oil passage 83 in the protruding direction Z is shorter than the diameter of the pivot portions 21 and 22, so that drilling can be performed easily.
  • Each of the pair of pivot portions 21 and 22 is connected to the beam 54 by a single connector 55 and 56, and the pair of connectors 55 and 56 are coaxial at the central portion of the pivot portions 21 and 22 in the width direction Y. Be placed.
  • the couplers 55 and 56 By arranging the couplers 55 and 56 in this way, the beam 54 can be stably coupled to the pivot portions 21 and 22 even if the beam 54 is stopped at one point. As described above, the rotation of the beam 54 can be restricted even in this arrangement. Since the first pivot oil passage 83 is unevenly distributed in the width direction Y, the insertion hole 59 does not interfere with the first pivot oil passage 83.
  • the oil passage 80 passes from the base end portion in the projecting direction Z of the first nozzle 84, the second nozzle 85, and the first pivot oil passage 83 to the second nozzle 85 through the inside of the main body portion 23 and the second pivot portion 22.
  • a distribution oil passage 86 to be connected is included.
  • the oil is distributed to the second nozzle 85 using the inside of the main body 23 without using the beam 54. For this reason, the rigidity required for the beam 54 can be ensured while reducing the width and height of the beam 54 by an amount corresponding to the absence of the oil passage to reduce the size and weight.
  • the nozzles 84 and 85 are open on the inner surfaces of the pivot portions 21 and 22. Since the pivot portions 21 and 22 have a large diameter, a relatively wide inner surface is secured. For this reason, it becomes easy to freely select the opening positions of the nozzles 84 and 85 on the inner surfaces of the pivot portions 21 and 22, and the oil supply to the peripheral surface 43 of the power roller 16 is optimized.
  • the trunnion 20 is downsized in the tilt axis direction X. Accordingly, the pair of yokes 27 and 28 can be brought close to each other in the tilt axis direction X.
  • the coupling surface 36 can be brought close to the transmission shaft center A ⁇ b> 1 together with the first yoke 27. Thereby, the transmission 10 becomes compact in the tilt axis direction X as a whole.
  • the device input shaft 4a is parallel to the transmission shaft center A1, and the extending direction of the straight line L connecting the device input shaft 4a and the transmission shaft center A1 is the tilt axis A3.
  • the gear input 4b can be reduced in diameter by bringing the device input shaft 4a closer to the transmission shaft center A1 so as to fill this space. This makes IDG1 compact and lightweight.
  • the non-threaded portion 55c may have a non-circular cross section.
  • the step surfaces 57 and 58 are linearly extending in the width direction Y.
  • the step surfaces 57 and 58 have a function of preventing rotation unless the step surfaces 57 and 58 have an arc shape centered on the center line of the couplers 55 and 56 when viewed in the tilt axis direction X. I can do it.
  • the first connector 55 may be screwed with the beam 54.
  • One end portion of the beam 54 may be connected to the first pivot portion 21 by a plurality of first connecting tools 55.
  • the beam 54 may be superimposed on the pair of pivot portions 21 and 22 in a direction perpendicular to the tilt axis A3 (the radial direction of the pivot portions 21 and 22), and the connectors 55 and 56 may be inserted in that direction.
  • one end of the beam 54 may be formed in a shape matching the bearing 25 or the through hole 29 of the first yoke 27. The same applies to the other end of the beam 54, the second connector 56, and the second pivot portion 22.
  • the supply of oil to the trunnion 20 may be performed from the second pivot portion 22.
  • an oil passage corresponding to the second inflow oil passage 82 extending in the width direction Y is formed in the second pivot portion 22.
  • the transmission may be a central output type instead of the central input type.
  • the transmission input shaft is inserted through the hollow transmission output shaft and protrudes on both sides, and the arrangement relationship between the input side element and the output side element is opposite to that of the central input type.
  • the transmission may be a single cavity type including a pair of an input disk and an output disk instead of the double cavity type.
  • the arrangement of trunnions (tilt axis) with respect to the input disk and output disk can be changed as long as the power can be transmitted effectively.
  • the tilt axis can be appropriately changed as long as it touches a virtual circle having a predetermined size centered on the transmission axis in a plane perpendicular to the transmission axis.
  • the transmission may be a full toroidal type instead of a half toroidal type, and the power roller may be formed in a disk shape.
  • the device input shaft may be orthogonal to the transmission shaft center or in a twisted position, and the gear pair may be a cross shaft gear or a staggered shaft gear.
  • the toroidal continuously variable transmission shown in the above-described embodiment is not limited to an application to an aircraft power generation apparatus, and may be used for another application power generation apparatus, an automobile, or various industrial machines. .

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

A toroidal continuously variable transmission is provided with: an input disk (13) and an output disk (14) that are disposed so as to face each other; a power roller (16) that is interposed between the input disk (13) and the output disk (14) and transmits the rotational driving force of the input disk (13) to the output disk (14) at a gear ratio depending on the tilt angle; a trunnion (20) that has a pair of pivot parts (21, 22) disposed coaxially with the tilt axis, and a main body (23) to which the power roller (16) is rotatably mounted; and a beam (54) that extends in the direction of the tilt axis on the side opposite the main body (23), as seen from the power roller (16), and is coupled to the trunnion (20). The pair of pivot parts (21, 22) project from the main body (23) in a projecting direction that is perpendicular to the direction of the tilt axis. The beam is coupled to the pair of pivot parts (21, 22) via couplings (55, 56) inserted in the pair of pivot parts (21, 22).

Description

トロイダル無段変速機及び航空機用駆動機構一体型発電装置Toroidal continuously variable transmission and aircraft drive mechanism integrated power generator
　本発明は、トロイダル無段変速機及び航空機用駆動機構一体型発電装置に関する。 The present invention relates to a toroidal continuously variable transmission and an aircraft drive mechanism integrated power generator.
　トロイダル無段変速機の変速比は、入力ディスクと出力ディスクの間に介在するパワーローラを傾転させることで、連続的に変更される。特許文献１では、パワーローラが、一対の枢軸を有するトラニオンに取り付けられ、枢軸の中心線周りに傾転するように案内される。トラニオンは、パワーローラを支持する支持板部、及びその両端部に形成された一対の折れ曲がり壁部を有する。折れ曲がり壁部の先端部同士は、連結部材を介して連結される。ピンが折れ曲がり壁部に挿入されることで、折れ曲がり壁部が連結部材と連結される。 The gear ratio of the toroidal continuously variable transmission is continuously changed by tilting the power roller interposed between the input disk and the output disk. In Patent Document 1, a power roller is attached to a trunnion having a pair of pivots, and is guided so as to tilt around a pivot centerline. The trunnion has a support plate portion that supports the power roller, and a pair of bent wall portions formed at both ends thereof. The front ends of the bent wall portions are connected via a connecting member. By inserting the pin into the bent wall portion, the bent wall portion is connected to the connecting member.
特開２００３－２０２０６２号公報JP 2003-202062 A
　ピンによる連結部材と折れ曲がり壁部との連結信頼性を得るには、折れ曲がり壁部が十分に大きい厚さ（枢軸の中心線方向における寸法）を有することを求められる。一対の枢軸は、このような折れ曲がり壁部の外側面から枢軸の中心線方向に突出する。したがって、トラニオンが枢軸の中心線方向に大きい。 In order to obtain the connection reliability between the connecting member by the pin and the bent wall portion, it is required that the bent wall portion has a sufficiently large thickness (dimension in the direction of the center line of the pivot). The pair of pivots protrude in the direction of the center line of the pivot from the outer surface of the bent wall portion. Therefore, the trunnion is large in the direction of the center line of the pivot.
　そこで本発明は、トロイダル無段変速機のトラニオンの小型化を目的とする。 Therefore, an object of the present invention is to reduce the trunnion of the toroidal continuously variable transmission.
　本発明の一態様に係るトロイダル無段変速機は、互いに対向配置される入力ディスク及び出力ディスクと、前記入力ディスクと前記出力ディスクとの間に傾転可能に挟まれ、前記入力ディスクの回転駆動力を傾転角に応じた変速比で前記出力ディスクに伝達するパワーローラと、傾転軸線と同軸状に配置された一対の枢軸部、及び、傾転軸線方向において前記一対の枢軸部の間に位置して前記パワーローラが回転自在に取り付けられる本体部を有するトラニオンと、前記パワーローラから見て前記本体部と反対側において前記傾転軸線方向に延びて前記トラニオンに連結されるビームと、を備え、前記一対の枢軸部が、前記本体部から前記傾転軸線方向と垂直な突出方向に突出し、前記ビームが前記一対の枢軸部に挿入される連結具で前記一対の枢軸部と連結される。 A toroidal continuously variable transmission according to an aspect of the present invention includes an input disk and an output disk, which are arranged to face each other, and are tiltably sandwiched between the input disk and the output disk. A power roller for transmitting force to the output disk at a gear ratio according to the tilt angle, a pair of pivot portions arranged coaxially with the tilt axis, and a pair of pivot portions in the tilt axis direction A trunnion having a main body portion rotatably attached to the power roller, and a beam extending in the tilt axis direction on the side opposite to the main body portion when viewed from the power roller and coupled to the trunnion; The pair of pivot parts projecting from the main body part in a projecting direction perpendicular to the tilt axis direction, and the beam is inserted into the pair of pivot parts. It is connected to the pivot portion of the pair.
　前記構成によれば、一対の枢軸部がビームを介して連結され、そのための連結具が枢軸部に挿入される。即ち、一対の枢軸部がビームとトラニオンとの連結信頼性を得るために必要となる連結具の取り付け部を兼ねる。このため、一対の枢軸部と傾転軸線方向に隣接して分厚い壁を設けずにすみ、トラニオンを傾転軸線方向に小型化できる。 According to the above-described configuration, the pair of pivot portions are coupled via the beam, and a connecting tool therefor is inserted into the pivot portion. In other words, the pair of pivot portions also serve as attachment portions for connecting tools necessary for obtaining the connection reliability between the beam and the trunnion. For this reason, it is not necessary to provide a thick wall adjacent to the pair of pivot portions in the tilt axis direction, and the trunnion can be downsized in the tilt axis direction.
　本発明の一態様に係る航空機用駆動機構一体型発電装置は、前述のトロイダル無段変速機と、航空機のエンジン回転軸から取り出される回転動力を前記トロイダル無段変速機に入力する入力機構と、前記トロイダル無段変速機の出力で駆動される発電機と、を備える。 An aircraft drive mechanism integrated power generator according to an aspect of the present invention includes the aforementioned toroidal continuously variable transmission, and an input mechanism that inputs rotational power extracted from the engine rotation shaft of the aircraft to the toroidal continuously variable transmission. And a generator driven by the output of the toroidal continuously variable transmission.
　前記構成によれば、トラニオンの小型化に伴い、駆動機構一体型発電装置の他の構成要素とトロイダル無段変速機の間に余地を創生できる。他の構成要素を余地に配置することができ、他の構成要素をトロイダル無段変速機に近づけることができるため、駆動機構一体型発電装置の小型化に資する。 According to the above-described configuration, a space can be created between the other components of the drive mechanism-integrated power generation device and the toroidal continuously variable transmission as the trunnion is downsized. Other components can be arranged in the room, and the other components can be brought close to the toroidal continuously variable transmission, which contributes to downsizing of the drive mechanism integrated power generation device.
　本発明によれば、トロイダル無段変速機のトラニオンを小型化できる。 According to the present invention, the trunnion of the toroidal continuously variable transmission can be reduced in size.
実施形態に係る駆動機構一体型発電装置の動力伝達経路を模式的に表す概要図である。It is a schematic diagram showing typically the power transmission course of the drive mechanism integrated power generator concerning an embodiment. トロイダル無段変速機の構成を示す図である。It is a figure which shows the structure of a toroidal continuously variable transmission. パワーローラ及びトラニオンの断面図である。It is sectional drawing of a power roller and a trunnion. 図４Ａは図３のＡ－Ａ線に沿ったトラニオンの断面図、図４Ｂは図４ＡのＢ－Ｂ線に沿ったトラニオンの断面図、図４Ｃは図４ＢのＣ－Ｃ線に沿ったトラニオンの断面図、図４Ｄは図４ＢのＤ－Ｄ線に沿ったトラニオンの断面図である。4A is a cross-sectional view of the trunnion along line AA in FIG. 3, FIG. 4B is a cross-sectional view of the trunnion along line BB in FIG. 4A, and FIG. 4C is a trunnion along line CC in FIG. FIG. 4D is a cross-sectional view of the trunnion along line DD of FIG. 4B.
　以下、図面を参照して実施形態について説明する。 Hereinafter, embodiments will be described with reference to the drawings.
　なお、本書における「垂直」は略垂直を含む概念である。単に「平行」、「直交」及び「ねじれの位置」という場合も同様である。 In addition, “vertical” in this document is a concept including substantially vertical. The same applies to the cases of simply “parallel”, “orthogonal”, and “twisted position”.
　図１に示すように、駆動機構一体型発電装置（Integrated Drive Generator：以下、「ＩＤＧ」という）１は、発電機３をトロイダル無段変速機（以下、「変速機」という）１０と共に収容するケーシング２を備えている。ＩＤＧ１は航空機の交流電源に用いられ、ケーシング２は航空機のエンジンに取り付けられる。 As shown in FIG. 1, a drive mechanism integrated power generator (Integrated Drive Generator: hereinafter referred to as “IDG”) 1 houses a generator 3 together with a toroidal continuously variable transmission (hereinafter referred to as “transmission”) 10. A casing 2 is provided. IDG1 is used for the AC power supply of the aircraft, and casing 2 is attached to the engine of the aircraft.
　変速機１０は、互いに同軸に配置されて相対回転可能な変速機入力軸１１及び変速機出力軸１２を備えている（以下、２軸１１，１２の回転軸を「変速機軸心Ａ１」という）。 The transmission 10 includes a transmission input shaft 11 and a transmission output shaft 12 that are coaxially arranged and can rotate relative to each other (hereinafter, the rotation shafts of the two shafts 11 and 12 are referred to as “transmission axis A1”). .
　変速機入力軸１１は入力機構４を介してエンジン回転軸に接続される。入力機構４は、エンジン回転軸から取り出された回転動力が入力される装置入力軸４ａ、及び装置入力軸４ａの回転を変速機入力軸１１に伝達するギヤ対４ｂを含む。ギヤ対４ｂは、装置入力軸４ａと一体回転する伝達ギヤ５ａ、及び伝達ギヤ５ａと噛合され変速機入力軸１１と一体回転する変速機入力ギヤ５ｂから構成される。装置入力軸４ａは変速機１０の軸方向と平行であり、ギヤ対４ｂは平行軸ギヤ対である。変速機出力軸１２は動力伝達機構６（例えば、平行軸ギヤ列）を介して発電機入力軸７に接続される。 The transmission input shaft 11 is connected to the engine rotation shaft via the input mechanism 4. The input mechanism 4 includes a device input shaft 4a to which rotational power extracted from the engine rotation shaft is input, and a gear pair 4b that transmits the rotation of the device input shaft 4a to the transmission input shaft 11. The gear pair 4b includes a transmission gear 5a that rotates integrally with the device input shaft 4a, and a transmission input gear 5b that meshes with the transmission gear 5a and rotates integrally with the transmission input shaft 11. The device input shaft 4a is parallel to the axial direction of the transmission 10, and the gear pair 4b is a parallel shaft gear pair. The transmission output shaft 12 is connected to the generator input shaft 7 via a power transmission mechanism 6 (for example, a parallel shaft gear train).
　装置入力軸４ａの一部、ギヤ対４ｂ、動力伝達機構６、及び発電機入力軸７もケーシング２に収容される。ＩＤＧ１の１以上の補機（例えば、オイルポンプ）が、入力機構４又は動力伝達機構６から取り出された回転動力に基づき駆動されてもよい。 A part of the device input shaft 4a, the gear pair 4b, the power transmission mechanism 6, and the generator input shaft 7 are also accommodated in the casing 2. One or more auxiliary machines (for example, oil pumps) of the IDG 1 may be driven based on the rotational power extracted from the input mechanism 4 or the power transmission mechanism 6.
　エンジン回転軸から取り出された回転動力は入力機構４を介して変速機入力軸１１に入力される。変速機１０は、変速機入力軸１１の回転を変速して変速機出力軸１２に出力する。変速機出力軸１２の回転は動力伝達機構６を介して発電機入力軸７に出力される。発電機入力軸７が回転すると、発電機３は、発電機入力軸７の回転速度に比例した周波数で交流電力を発生する。変速機１０の変速比は、エンジン回転軸の回転速度の変動に関わらず発電機入力軸７の回転速度を適値（機内電装品の作動に適した周波数（例えば、400Hz）と対応する値）に保つように連続的に変更される。これにより、周波数が一定の適値に保たれる。 Rotational power extracted from the engine rotation shaft is input to the transmission input shaft 11 via the input mechanism 4. The transmission 10 changes the rotation of the transmission input shaft 11 and outputs it to the transmission output shaft 12. The rotation of the transmission output shaft 12 is output to the generator input shaft 7 via the power transmission mechanism 6. When the generator input shaft 7 rotates, the generator 3 generates AC power at a frequency proportional to the rotational speed of the generator input shaft 7. The transmission ratio of the transmission 10 is an appropriate value for the rotational speed of the generator input shaft 7 regardless of fluctuations in the rotational speed of the engine rotational shaft (a value corresponding to a frequency (for example, 400 Hz) suitable for the operation of in-flight electrical components). Is continuously changed to keep As a result, the frequency is kept at a constant appropriate value.
　変速機１０は、ハーフトロイダル型且つダブルキャビティ型であり、入力ディスク１３及び出力ディスク１４を２組備えている。入力ディスク１３は、変速機入力軸１１の外周面上に、変速機入力軸１１と一体回転するよう設けられる。出力ディスク１４は、変速機出力軸１２の外周面上に、変速機出力軸１２と一体回転するよう設けられる。一組のディスク１３，１４は、変速機１０の軸方向に互いに対向配置され、２軸１１，１２よりも径方向外方で変速機軸心Ａ１の周方向に連続する円環状のキャビティ１５を１つ形成する。２組の入力ディスク１３及び出力ディスク１４ひいては２つのキャビティ１５が、変速機１０の軸方向に並べられる。 The transmission 10 is a half toroidal type and a double cavity type, and includes two sets of an input disk 13 and an output disk 14. The input disk 13 is provided on the outer peripheral surface of the transmission input shaft 11 so as to rotate integrally with the transmission input shaft 11. The output disk 14 is provided on the outer peripheral surface of the transmission output shaft 12 so as to rotate integrally with the transmission output shaft 12. The pair of discs 13 and 14 are arranged so as to face each other in the axial direction of the transmission 10, and each of the discs 13 and 14 has an annular cavity 15 that is radially outward from the two shafts 11 and 12 and continuous in the circumferential direction of the transmission shaft center A 1. Form one. Two sets of the input disk 13 and the output disk 14 and thus the two cavities 15 are arranged in the axial direction of the transmission 10.
　変速機１０は中央入力型である。変速機出力軸１２が、中空の変速機入力軸１１内に挿通され、変速機入力軸１１から両側に突出する。２つの出力ディスク１４は変速機出力軸１２の２つの突出部に分かれて配置される。２つの入力ディスク１３は変速機入力軸１１上で背中合わせに配置される。変速機入力ギヤ５ｂは、変速機入力軸１１の外周面上に設けられ、２つの入力ディスク１３間に配置される。動力伝達機構６の上流端を構成する要素（例えば、平歯車）は、変速機出力軸１２の一方の突出部の外周面上に設けられ、この突出部上の出力ディスク１４を基準にして変速機１０の軸方向において入力ディスク１３と反対側に配置される。 The transmission 10 is a central input type. The transmission output shaft 12 is inserted into the hollow transmission input shaft 11 and protrudes from the transmission input shaft 11 to both sides. The two output disks 14 are divided into two projecting portions of the transmission output shaft 12. The two input disks 13 are arranged back to back on the transmission input shaft 11. The transmission input gear 5 b is provided on the outer peripheral surface of the transmission input shaft 11 and is disposed between the two input disks 13. Elements (for example, spur gears) constituting the upstream end of the power transmission mechanism 6 are provided on the outer peripheral surface of one projecting portion of the transmission output shaft 12, and the speed is changed with reference to the output disk 14 on the projecting portion. It is arranged on the opposite side of the input disk 13 in the axial direction of the machine 10.
　変速機１０は、複数のパワーローラ１６及び複数のパワーローラ１６と一対一で対応する複数のトラニオン２０を備える。複数のパワーローラ１６は同じ構造を有し、複数のトラニオン２０は同じ構造を有する。複数（例えば２つ）のパワーローラ１６が、１つのキャビティ１５内に変速機軸心Ａ１の周方向に等間隔をあけて配置される。パワーローラ１６は支持部１８を介して対応するトラニオン２０に対して回転軸線Ａ２周りに回転可能に支持される。トラニオン２０は、ケーシング２に対し、傾転軸線Ａ３周りに傾転可能且つ傾転軸線Ａ３の方向（以下、「傾転軸線方向Ｘ」という）に変位可能に支持される。傾転軸線Ａ３は変速機軸心Ａ１とねじれの位置にあり、回転軸線Ａ２は傾転軸線Ａ３と垂直である。 The transmission 10 includes a plurality of power rollers 16 and a plurality of trunnions 20 corresponding to the plurality of power rollers 16 on a one-to-one basis. The plurality of power rollers 16 have the same structure, and the plurality of trunnions 20 have the same structure. A plurality of (for example, two) power rollers 16 are disposed in one cavity 15 at equal intervals in the circumferential direction of the transmission shaft center A1. The power roller 16 is supported by the corresponding trunnion 20 via the support portion 18 so as to be rotatable around the rotation axis A2. The trunnion 20 is supported with respect to the casing 2 so as to be tiltable about the tilt axis A3 and displaceable in the direction of the tilt axis A3 (hereinafter referred to as “tilt axis direction X”). The tilt axis A3 is in a twisted position with respect to the transmission axis A1, and the rotation axis A2 is perpendicular to the tilt axis A3.
　ケーシング２は多目的で用いられる油を貯留している。例えば、油は、パワーローラ１６と入力ディスク１３との接触部（以下、「入力接触部」という）、及びパワーローラ１６と出力ディスク１４との接触部（以下、「出力接触部」という）にトラクションオイルとして供給される。パワーローラ１６は、クランプ機構（図示せず）で発生される変速機１０の軸方向の強いクランプ力によってディスク１３，１４に高圧で押し付けられる。それにより高粘度の油膜が、入力接触部及び出力接触部に形成される。クランプ機構が油圧式である場合、油はクランプ機構に作動油として供給される。 Casing 2 stores oil used for multiple purposes. For example, oil flows into a contact portion between the power roller 16 and the input disk 13 (hereinafter referred to as “input contact portion”) and a contact portion between the power roller 16 and the output disk 14 (hereinafter referred to as “output contact portion”). Supplied as traction oil. The power roller 16 is pressed against the disks 13 and 14 at a high pressure by a strong axial clamping force of the transmission 10 generated by a clamping mechanism (not shown). Thereby, a highly viscous oil film is formed in the input contact portion and the output contact portion. When the clamp mechanism is hydraulic, oil is supplied to the clamp mechanism as hydraulic oil.
　変速機入力軸１１が回転すると、入力ディスク１３が回転駆動され、パワーローラ１６が入力接触部で生じる油膜の剪断抵抗で回転軸線Ａ２周りに回転駆動される。パワーローラ１６が回転すると、出力ディスク１４が出力接触部で生じる油膜の剪断抵抗で回転駆動され、変速機出力軸１２が回転駆動される。トラニオン２０及びこれに取り付けられているパワーローラ１６が傾転軸線方向Ｘに移動すると、パワーローラ１６の傾転軸線Ａ３周りの回転角（以下、「傾転角」という）が変更され、変速機１０の変速比が傾転角に応じて連続的に変更される。このように、変速機１０では、回転動力がトラクションドライブにより変速機入力軸１１から変速機出力軸１２へと伝達される。パワーローラ１６は、入力ディスク１３と出力ディスク１４との間に傾転軸線Ａ３の周りに傾転可能に挟まれ、入力ディスク１３の回転駆動力を傾転角に応じた変速比で変速して出力ディスク１４に伝達する。 When the transmission input shaft 11 is rotated, the input disk 13 is rotationally driven, and the power roller 16 is rotationally driven around the rotational axis A2 by the shear resistance of the oil film generated at the input contact portion. When the power roller 16 rotates, the output disk 14 is rotationally driven by the oil film shear resistance generated at the output contact portion, and the transmission output shaft 12 is rotationally driven. When the trunnion 20 and the power roller 16 attached thereto move in the tilt axis direction X, the rotation angle (hereinafter referred to as “tilt angle”) around the tilt axis A3 of the power roller 16 is changed, and the transmission The gear ratio of 10 is continuously changed according to the tilt angle. As described above, in the transmission 10, the rotational power is transmitted from the transmission input shaft 11 to the transmission output shaft 12 by the traction drive. The power roller 16 is sandwiched between the input disk 13 and the output disk 14 so as to be tiltable around the tilt axis A3, and the rotational driving force of the input disk 13 is changed at a gear ratio corresponding to the tilt angle. It is transmitted to the output disk 14.
　図２に示すように、トラニオン２０は、同軸状に配置された一対の枢軸部２１，２２、及び回転軸線Ａ２周りに回転自在にパワーローラ１６が取り付けられる本体部２３を有する。枢軸部２１，２２の中心線は傾転軸線Ａ３上に位置し又は傾転軸線Ａ３を構成する。本体部２３は、傾転軸線方向Ｘにおいて一対の枢軸部２１，２２の間に位置する。以下、枢軸部２１，２２の一方を「第１枢軸部２１」、他方を「第２枢軸部２２」という。 As shown in FIG. 2, the trunnion 20 has a pair of pivot portions 21 and 22 arranged coaxially, and a main body portion 23 to which the power roller 16 is rotatably attached around the rotation axis A2. The center lines of the pivot portions 21 and 22 are located on the tilt axis A3 or constitute the tilt axis A3. The main body portion 23 is located between the pair of pivot portions 21 and 22 in the tilt axis direction X. Hereinafter, one of the pivot portions 21 and 22 is referred to as a “first pivot portion 21”, and the other is referred to as a “second pivot portion 22”.
　第１枢軸部２１は軸受２５を介して第１ヨーク２７の貫通穴２９に嵌め込まれ、第２枢軸部２２は軸受２６を介して第２ヨーク２８の貫通穴３０に嵌め込まれる。一対のヨーク２７，２８は、ケーシング２（図１参照）に取り付けられる。トラニオン２０は、ヨーク２７，２８を介し、傾転軸線Ａ３周りに回転（揺動、傾転又は角変位）可能且つ傾転軸線方向Ｘに変位可能にケーシング２に支持される。このように、一対の枢軸部２１，２２は、軸受２５，２６に挿通される軸頸であり、（軸受２５，２６と共に）一対のヨーク２７，２８に嵌め込まれる部分である。 The first pivot portion 21 is fitted into the through hole 29 of the first yoke 27 through the bearing 25, and the second pivot portion 22 is fitted into the through hole 30 of the second yoke 28 through the bearing 26. The pair of yokes 27 and 28 are attached to the casing 2 (see FIG. 1). The trunnion 20 is supported by the casing 2 via the yokes 27 and 28 so as to be rotatable (oscillating, tilting or angular displacement) around the tilt axis A3 and displaceable in the tilt axis direction X. As described above, the pair of pivot portions 21 and 22 are shaft necks inserted into the bearings 25 and 26, and are portions fitted together with the pair of yokes 27 and 28 (along with the bearings 25 and 26).
　ヨーク２７，２８は、トラニオン２０の総数と同数の貫通穴２９，３０を有する。全てのトラニオン２０は、傾転軸線Ａ３が互いに平行となるように、傾転軸線方向Ｘの一方側で第１ヨーク２７に支持されて他方側で第２ヨーク２８に支持される。 The yokes 27 and 28 have the same number of through holes 29 and 30 as the total number of trunnions 20. All the trunnions 20 are supported by the first yoke 27 on one side in the tilt axis direction X and supported by the second yoke 28 on the other side so that the tilt axes A3 are parallel to each other.
　トラニオン２０及びこれに取り付けられているパワーローラ１６は、ＩＤＧ１の油圧駆動機構３１によって傾転軸線方向Ｘに変位するよう駆動される。油圧駆動機構３１は、例えば複数のトラニオン２０と一対一で対応する複数の油圧シリンダ３２によって構成される。 The trunnion 20 and the power roller 16 attached to the trunnion 20 are driven to be displaced in the tilt axis direction X by the hydraulic drive mechanism 31 of the IDG1. The hydraulic drive mechanism 31 includes, for example, a plurality of hydraulic cylinders 32 that correspond one-to-one with the plurality of trunnions 20.
　油圧シリンダ３２は、シリンダ本体３３、ピストン３４及びロッド３５を有する。シリンダ本体３３は、傾転軸線Ａ３と直交する取合面３６上に固定される。取合面３６は、第１ヨーク２７を基準として傾転軸線方向Ｘにおいて変速機軸心Ａ１と反対側に配置され、シリンダ本体３３は取合面３６を基準として傾転軸線方向Ｘにおいて第１ヨーク２７と反対側に配置される。油圧シリンダ３２は、例えば複動片ロッド型であり、ピストン３４は、シリンダ本体３３の内空間に傾転軸線方向Ｘに往復動可能に配置され、内空間がピストン３４により２つの油室３３ａ，３３ｂに区画される。ロッド３５は、一端部でピストン３４に固定され、他端部で第１枢軸部２１に固定される。ケーシング２（図１参照）に貯留されている油は、油室３３ａ，３３ｂに油圧駆動機構３１の作動油として供給される。油室３３ａ，３３ｂへの供給油圧に応じて、ピストン３４が傾転軸線方向Ｘに移動し、ロッド３５がピストン３４の動作に応じて傾転軸線方向Ｘに進退する。トラニオン２０及びパワーローラ１６が連動して傾転軸線方向Ｘに移動し、傾転角及び変速機１０の変速比が連続的に変更される。 The hydraulic cylinder 32 has a cylinder body 33, a piston 34, and a rod 35. The cylinder body 33 is fixed on a coupling surface 36 orthogonal to the tilt axis A3. The coupling surface 36 is disposed on the opposite side of the transmission axis A1 in the tilt axis direction X with respect to the first yoke 27, and the cylinder body 33 has the first yoke in the tilt axis direction X with respect to the coupling surface 36. 27 on the opposite side. The hydraulic cylinder 32 is, for example, a double-acting single rod type, and the piston 34 is disposed in the inner space of the cylinder body 33 so as to be able to reciprocate in the tilt axis direction X, and the inner space is divided into two oil chambers 33a, It is divided into 33b. The rod 35 is fixed to the piston 34 at one end and is fixed to the first pivot portion 21 at the other end. Oil stored in the casing 2 (see FIG. 1) is supplied to the oil chambers 33a and 33b as hydraulic oil for the hydraulic drive mechanism 31. The piston 34 moves in the tilt axis direction X according to the hydraulic pressure supplied to the oil chambers 33a and 33b, and the rod 35 advances and retreats in the tilt axis direction X according to the operation of the piston 34. The trunnion 20 and the power roller 16 move together in the tilt axis direction X, and the tilt angle and the gear ratio of the transmission 10 are continuously changed.
　以下、図３及び４Ａ－Ｄを参照して、トラニオン２０及びその周辺の構造について説明する。 Hereinafter, the trunnion 20 and its surrounding structure will be described with reference to FIGS. 3 and 4A-D.
　一対の枢軸部２１，２２は、円筒状であり、本体部２３の傾転軸線方向Ｘの両端部から傾転軸線Ａ３に垂直な方向（以下、「突出方向Ｚ」という）に突出するように立設している。トラニオン２０は、一対の枢軸部２１，２２及び本体部２３で囲まれるローラ収容空間２０ａを形成し、パワーローラ１６はローラ収容空間２０ａに配置される。 The pair of pivot portions 21 and 22 are cylindrical, and project from both ends of the tilt axis direction X of the main body 23 in a direction perpendicular to the tilt axis A3 (hereinafter referred to as “projection direction Z”). Standing up. The trunnion 20 forms a roller accommodating space 20a surrounded by the pair of pivot portions 21 and 22 and the main body 23, and the power roller 16 is disposed in the roller accommodating space 20a.
　以下、一対の枢軸部２１，２２及び本体部２３の表面のうち、パワーローラ収容空間２０ａに面してパワーローラ１６と対向するものを「内面」という。枢軸部２１，２２においては、傾転軸線方向Ｘにおいて内面と反対の面を「外面」という。本体部２３については、内面と突出方向Ｚにおいて反対の面を「外面」という。傾転軸線方向Ｘにおいてトラニオン２０の傾転軸線方向Ｘの中心に近い側を「内側」、この中心から遠い側を「外側」という。突出方向Ｚにおいて本体部２３の外面に近い側を「基端側」、本体部２３から遠い側を「先端側」という。傾転軸線方向Ｘにも突出方向Ｚにも垂直な方向をトラニオン２０の「幅方向Ｙ」という。本体部２３の内面は、概略ＸＹ方向に広がる平面であり、突出方向Ｚは、本体部２３の高さ又は厚さ方向に相当する。 Hereinafter, among the surfaces of the pair of pivot portions 21 and 22 and the main body portion 23, the surface facing the power roller housing space 20 a and facing the power roller 16 is referred to as “inner surface”. In the pivot portions 21 and 22, the surface opposite to the inner surface in the tilt axis direction X is referred to as “outer surface”. Regarding the main body 23, the surface opposite to the inner surface in the protruding direction Z is referred to as “outer surface”. In the tilt axis direction X, the side closer to the center of the trunnion 20 in the tilt axis direction X is referred to as “inner side”, and the side far from this center is referred to as “outer side”. The side close to the outer surface of the main body 23 in the protruding direction Z is referred to as “base end side”, and the side far from the main body 23 is referred to as “tip side”. The direction perpendicular to both the tilt axis direction X and the protruding direction Z is referred to as the “width direction Y” of the trunnion 20. The inner surface of the main body 23 is a plane that extends in the general XY direction, and the protruding direction Z corresponds to the height or thickness direction of the main body 23.
　図３に示すように、パワーローラ１６は半球形状であり、湾曲した周面４３を有する。支持部１８の支軸４５がパワーローラ１６の一端面４２に開口する円孔４４に挿入され、パワーローラ１６は軸受４８，４９により支持部１８に対して回転可能に支持される（支軸４５及び円孔４４の中心線が回転軸線Ａ２を構成する）。軸受４８（例えば、ラジアル針状ころ軸受）は支軸４５と円孔４４の内周面との間に介在している。支軸４５は円盤状のフランジ４７の一端面から垂直に突出する。軸受４９は、パワーローラ１６で内輪を構成しフランジ４７で外輪を構成したスラスト転がり軸受であり、軸受４９の転動体がパワーローラ１６の一端面４２とフランジ４７の一端面の間に挟持される。 As shown in FIG. 3, the power roller 16 has a hemispherical shape and has a curved peripheral surface 43. The support shaft 45 of the support portion 18 is inserted into a circular hole 44 opened in one end face 42 of the power roller 16, and the power roller 16 is rotatably supported by the support portion 18 by bearings 48 and 49 (support shaft 45. And the center line of the circular hole 44 constitutes the rotation axis A2.) The bearing 48 (for example, a radial needle roller bearing) is interposed between the support shaft 45 and the inner peripheral surface of the circular hole 44. The support shaft 45 projects vertically from one end surface of the disk-shaped flange 47. The bearing 49 is a thrust rolling bearing in which an inner ring is formed by the power roller 16 and an outer ring is formed by the flange 47, and a rolling element of the bearing 49 is sandwiched between one end surface 42 of the power roller 16 and one end surface of the flange 47. .
　支持部１８はフランジ４７の他端面から垂直に突出する取付軸４６を有し、取付軸４６が本体部２３に形成された取付孔５２に挿入されることで、パワーローラ１６が本体部２３に取り付けられてローラ収容空間２０ａに配置される。取付孔５２は、突出方向Ｚに延びる非貫通穴で、本体部２３の内面に開口する。回転軸線Ａ２は、突出方向Ｚと平行に向けられる。取付軸４６は回転軸線Ａ２に対して偏心し、取付孔５２に回転可能に挿入される。取付孔５２は、傾転軸線Ａ３から見て幅方向Ｙの一方側に偏在している（図４Ｂ参照）。 The support portion 18 has a mounting shaft 46 that protrudes perpendicularly from the other end surface of the flange 47, and the power roller 16 is attached to the main body portion 23 by inserting the mounting shaft 46 into a mounting hole 52 formed in the main body portion 23. It is attached and arranged in the roller accommodating space 20a. The attachment hole 52 is a non-through hole extending in the protruding direction Z and opens on the inner surface of the main body 23. The rotation axis A2 is directed parallel to the protruding direction Z. The attachment shaft 46 is eccentric with respect to the rotation axis A2 and is inserted into the attachment hole 52 so as to be rotatable. The mounting hole 52 is unevenly distributed on one side in the width direction Y as seen from the tilt axis A3 (see FIG. 4B).
　パワーローラ１６がトラニオン２０に取り付けられた状態において、フランジ４７の他端面が本体部２３の内面と対向する。支持部１８は軸受５０，５１によって本体部２３に対して回転可能に支持される。軸受５０（例えば、スラスト針状ころ軸受）がフランジ４７の他端面と本体部２３の内面の間に介在し、軸受５１（例えば、ラジアル針状ころ軸受）が取付軸４６と取付孔５２の内周面との間に介在する。 In the state where the power roller 16 is attached to the trunnion 20, the other end surface of the flange 47 faces the inner surface of the main body 23. The support 18 is supported by the bearings 50 and 51 so as to be rotatable with respect to the main body 23. A bearing 50 (for example, a thrust needle roller bearing) is interposed between the other end surface of the flange 47 and the inner surface of the main body 23, and a bearing 51 (for example, a radial needle roller bearing) is disposed in the mounting shaft 46 and the mounting hole 52. It is interposed between the peripheral surface.
　本体部２３は傾転軸線方向Ｘに比較的長寸で幅方向Ｙに比較的短寸である。枢軸部２１，２２の内面同士の間隔はパワーローラ１６の最大直径（例えば、一端面４２の直径）よりも僅かに大きい（図４Ｂ参照）。パワーローラ１６は傾転軸線方向Ｘにおいて枢軸部２１，２２の間に配置され、周面４３が枢軸部２１，２２の内面と対向する（図３参照）。幅方向Ｙは、変速機軸心Ａ１（図１参照）と平行又は傾転角に応じて変速機軸心Ａ１に対して若干傾斜している。パワーローラ１６は、周面４３とディスク１３，１４（図１参照）との接触のため、本体部２３から幅方向Ｙにおいて両側へ部分的に突出している（図４Ｂ参照）。 The main body 23 is relatively long in the tilt axis direction X and relatively short in the width direction Y. The distance between the inner surfaces of the pivot portions 21 and 22 is slightly larger than the maximum diameter of the power roller 16 (for example, the diameter of the one end surface 42) (see FIG. 4B). The power roller 16 is disposed between the pivot portions 21 and 22 in the tilt axis direction X, and the peripheral surface 43 faces the inner surfaces of the pivot portions 21 and 22 (see FIG. 3). The width direction Y is slightly inclined with respect to the transmission axis A1 in accordance with a parallel or tilt angle with respect to the transmission axis A1 (see FIG. 1). The power roller 16 partially protrudes from the main body 23 to both sides in the width direction Y for contact between the circumferential surface 43 and the disks 13 and 14 (see FIG. 1) (see FIG. 4B).
　一対の枢軸部２１，２２は、傾転軸線方向Ｘに延びるビーム５４を介して連結される。ビーム５４の傾転軸線方向Ｘにおける一端部は、第１連結具５５で第１枢軸部２１に取外し可能に連結され、ビーム５４の傾転軸線方向Ｘにおける他端部は、第２連結具５６で第２枢軸部２２に取外し可能に連結される。第１連結具５５及び第２連結具５６は単一であり、各枢軸部２１，２２は、一点止めでビーム５４に連結される。 The pair of pivot parts 21 and 22 are connected via a beam 54 extending in the tilt axis direction X. One end of the beam 54 in the tilt axis direction X is detachably connected to the first pivot 21 by the first connector 55, and the other end of the beam 54 in the tilt axis direction X is connected to the second connector 56. Is detachably connected to the second pivot portion 22. The first connector 55 and the second connector 56 are single, and the respective pivot portions 21 and 22 are connected to the beam 54 at one point.
　ビーム５４が一対の枢軸部２１，２２に連結された状態において、パワーローラ１６が突出方向Ｚにおいて本体部２３とビーム５４の間に配置され、ビーム５４はパワーローラ１６から見て本体部２３とは反対側に配置される。ビーム５４はトラニオン２０に連結されてトラニオン２０を補強する。例えば、トラニオン２０がパワーローラ１６からのスラスト荷重を受け、それにより一対の枢軸部２１，２２の先端部が傾転軸線方向Ｘの内側に撓もうとするとき、ビーム５４で弾性変形を抑制できる。 In a state where the beam 54 is connected to the pair of pivot portions 21 and 22, the power roller 16 is disposed between the main body portion 23 and the beam 54 in the protruding direction Z, and the beam 54 is connected to the main body portion 23 when viewed from the power roller 16. Are arranged on the opposite side. The beam 54 is connected to the trunnion 20 to reinforce the trunnion 20. For example, when the trunnion 20 receives a thrust load from the power roller 16 and thereby the distal ends of the pair of pivot portions 21 and 22 try to bend inward in the tilting axis direction X, the elastic deformation can be suppressed by the beam 54. .
　ビーム５４の一端部は、第１枢軸部２１の内面に傾転軸線方向Ｘに重ねられる。第１連結具５５は傾転軸線方向Ｘに挿入される。 One end of the beam 54 is superimposed on the inner surface of the first pivot 21 in the tilt axis direction X. The first connector 55 is inserted in the tilt axis direction X.
　第１枢軸部２１の内面は、突出方向Ｚにおける先端部で、傾転軸線方向Ｘの外側に僅かにオフセットされている。第１枢軸部２１は、内面の突出方向Ｚにおける基端部（以下、「内面基端部」という）を内面の突出方向Ｚにおける先端部（以下、「内面先端部」という）に連続させる段差面５７を有し、段差面５７は、内面先端部の内面基端部に対する僅かなオフセット分だけ傾転軸線方向Ｘに延びている。段差面５７は、例えば幅方向Ｙに直線的に延びている。ビーム５４の一端部は、第１枢軸部２１の内面に重ねられる際、突出方向Ｚにおいて段差面５７にも重ねられる。ビーム５４の一端部は、突出方向Ｚにおける基端部（本体部２３に近い側）で、段差面５７及び内面先端部と整合する形状に形成されている。ビーム５４の一端部は、突出方向Ｚにおいて基端側に向かうほど幅方向Ｙに拡がり、突出方向Ｚにおける基端縁部が、例えば幅方向Ｙに直線的に延びている。 The inner surface of the first pivot portion 21 is a tip portion in the projecting direction Z and is slightly offset to the outside in the tilt axis direction X. The first pivot portion 21 is a step that causes a base end portion (hereinafter referred to as “inner surface base end portion”) in the protruding direction Z of the inner surface to be continuous with a tip end portion (hereinafter referred to as “inner surface front end portion”) in the protruding direction Z of the inner surface. The step surface 57 has a surface 57 and extends in the tilt axis direction X by a slight offset with respect to the inner surface proximal end portion of the inner surface distal end portion. The step surface 57 extends linearly in the width direction Y, for example. When the one end portion of the beam 54 is overlapped with the inner surface of the first pivot portion 21, it is also overlapped with the step surface 57 in the protruding direction Z. One end portion of the beam 54 is a base end portion (side closer to the main body portion 23) in the protruding direction Z, and is formed in a shape that matches the step surface 57 and the inner surface front end portion. One end portion of the beam 54 expands in the width direction Y toward the base end side in the protruding direction Z, and the base end edge portion in the protruding direction Z extends linearly in the width direction Y, for example.
　第１枢軸部２１は傾転軸線方向Ｘに貫通した挿通穴５９を有する。挿通穴５９は、傾転軸線方向Ｘにおける内側部分を外側部分よりも小径とした段付き穴であり、内側部分で雌ねじが形成されている。ビーム５４の一端部は傾転軸線方向Ｘの外側の端面に開口して傾転軸線方向Ｘに延びる挿入孔６１を有する。挿入孔６１は挿通穴５９よりも小径である。 The first pivot portion 21 has an insertion hole 59 penetrating in the tilt axis direction X. The insertion hole 59 is a stepped hole in which the inner portion in the tilt axis direction X has a smaller diameter than the outer portion, and a female screw is formed in the inner portion. One end of the beam 54 has an insertion hole 61 that opens to the outer end face in the tilt axis direction X and extends in the tilt axis direction X. The insertion hole 61 has a smaller diameter than the insertion hole 59.
　第１連結具５５は、頭部５５ａ、雄ねじ部５５ｂ及び非ねじ部５５ｃを有する。非ねじ部５５ｃは、円形断面を有して雄ねじ部５５ｂよりも小径である。例えば、ねじ先が棒先又はとがり先に形成されたねじが第１連結具５５であってもよい。 The first connector 55 has a head portion 55a, a male screw portion 55b, and a non-screw portion 55c. The non-screw part 55c has a circular cross section and is smaller in diameter than the male screw part 55b. For example, the first connector 55 may be a screw having a screw tip formed on a rod tip or a pointed tip.
　雄ねじ部５５ｂは挿通穴５９の内側部分と螺合され、頭部５５ａは挿通穴５９の段差に突き当てられる。頭部５５ａは挿通穴５９に没入され、第１枢軸部２１の外面から突出しない。非ねじ部５５ｃは、挿通穴５９から突出して挿入孔６１に挿入される。雄ねじ部５５ｂが第１枢軸部２１と螺合されるので、第１連結具５５が第１枢軸部２１の外面から脱落するのを防止できる。非ねじ部５５ｃがビーム５４に挿入されるので、ビーム５４は、挿入孔６１及び非ねじ部５５ｃの案内を受け、第１連結具５５及びこれと螺合された第１枢軸部２１に対し傾転軸線方向Ｘに相対移動できる。このように、本実施形態においては、第１連結具５５の少なくとも一部が、第１枢軸部２１の内部に位置している。すなわち、第１ヨーク２７の貫通穴２９に嵌め込まれた状態では、第１連結具５５の少なくとも一部が、貫通穴２９の内部に位置することとなる。 The male screw portion 55 b is screwed into the inner portion of the insertion hole 59, and the head portion 55 a is abutted against the step of the insertion hole 59. The head portion 55 a is immersed in the insertion hole 59 and does not protrude from the outer surface of the first pivot portion 21. The non-screw part 55 c protrudes from the insertion hole 59 and is inserted into the insertion hole 61. Since the male screw portion 55 b is screwed with the first pivot portion 21, the first connector 55 can be prevented from falling off from the outer surface of the first pivot portion 21. Since the non-threaded portion 55c is inserted into the beam 54, the beam 54 is guided with respect to the insertion hole 61 and the non-threaded portion 55c, and is inclined with respect to the first connector 55 and the first pivot portion 21 screwed with the first connector 55. Relative movement in the rotation axis direction X is possible. Thus, in the present embodiment, at least a part of the first connector 55 is located inside the first pivot portion 21. In other words, in a state where the first yoke 27 is fitted into the through hole 29, at least a part of the first connector 55 is located inside the through hole 29.
　ビーム５４の他端部、第２枢軸部２２及び第２連結具５６も、上記同様に構成されている。符号５６ａは頭部、５６ｂは雄ねじ部、５６ｃは非ねじ部、５８は段差面、６０は挿通穴、６２は挿入孔である。 The other end portion of the beam 54, the second pivot portion 22 and the second connector 56 are also configured in the same manner as described above. Reference numeral 56a denotes a head, 56b denotes a male screw part, 56c denotes a non-screw part, 58 denotes a stepped surface, 60 denotes an insertion hole, and 62 denotes an insertion hole.
　連結具５５，５６は同軸状に配置され、挿通穴５９，６０及び挿入孔６１，６２も同軸状に配置される。これらの中心線は、傾転軸線Ａ３から突出方向Ｚにおける先端側に離れた位置で傾転軸線Ａ３と平行に延び、各枢軸部２１，２２の幅方向Ｙにおける中央部を通過している（図４Ａ及びＣ参照）。 The couplers 55 and 56 are arranged coaxially, and the insertion holes 59 and 60 and the insertion holes 61 and 62 are also arranged coaxially. These center lines extend in parallel to the tilt axis A3 at a position away from the tilt axis A3 toward the distal end side in the projecting direction Z, and pass through the center in the width direction Y of the pivot portions 21 and 22 ( (See FIGS. 4A and C).
　トラニオン２０は、第１枢軸部２１の外周面より突出し、傾転軸線Ａ３と直交する突当て面６３を有する。突当て面６３は、円環状であり、第１枢軸部２１の直径と同寸の内径、及びこれよりも僅かに大きい外径を有する。突当て面６３は、第１枢軸部２１の突出方向Ｚの基端部では、本体部２３の外面と第１枢軸部２１の外周面との間の段差によって構成される。トラニオン２０は、第１枢軸部２１のうち先端側の内側に、第１枢軸部２１と連続した薄壁６５を有する。薄壁６５は、傾転軸線方向Ｘに見て半円形状であり、この薄壁６５によって、突当て面６３が、第１枢軸部２１の先端側の内側に形成され、無端円環状になる。 The trunnion 20 has a contact surface 63 that protrudes from the outer peripheral surface of the first pivot 21 and is orthogonal to the tilt axis A3. The abutting surface 63 has an annular shape, and has an inner diameter that is the same as the diameter of the first pivot portion 21 and an outer diameter that is slightly larger than the inner diameter. The abutting surface 63 is configured by a step between the outer surface of the main body portion 23 and the outer peripheral surface of the first pivot portion 21 at the proximal end portion in the projecting direction Z of the first pivot portion 21. The trunnion 20 has a thin wall 65 continuous with the first pivot portion 21 inside the first pivot portion 21 on the tip side. The thin wall 65 is semicircular when viewed in the tilting axis direction X, and the abutting surface 63 is formed inside the distal end side of the first pivot portion 21 by the thin wall 65 and becomes an endless annular shape. .
　軸受２５は、傾転軸線方向Ｘの外側から第１枢軸部２１に外嵌される。取付けの際、軸受２５は、スペーサ６７を介して突当て面６３に傾転軸線方向Ｘに重ねられ、傾転軸線方向Ｘに位置決めされる。更に、円盤状の軸受押え６９が第１枢軸部２１の外面に取り付けられる。これにより、軸受２５の脱落を防止でき、また、挿通穴５９が閉塞される。 The bearing 25 is fitted on the first pivot portion 21 from the outside in the tilt axis direction X. At the time of attachment, the bearing 25 is superimposed on the abutting surface 63 via the spacer 67 in the tilt axis direction X, and is positioned in the tilt axis direction X. Further, a disk-shaped bearing retainer 69 is attached to the outer surface of the first pivot portion 21. As a result, the bearing 25 can be prevented from falling off, and the insertion hole 59 is closed.
　第２枢軸部２２も、上記同様に構成されている。符号６４は突当て面、６６は薄壁、６８はスペーサ、７０は軸受押えである。 The second pivot portion 22 is also configured in the same manner as described above. Reference numeral 64 is an abutting surface, 66 is a thin wall, 68 is a spacer, and 70 is a bearing retainer.
　変速機１０は、トラニオン２０及びパワーローラ１６に油を供給する油路８０を備えている。油路８０は、第１流入油路８１（図３及び４Ａ参照）、第２流入油路８２（図３及び４Ａ参照）、第１枢軸油路８３（図４Ａ及びＢ参照）、第１ノズル８４（図４Ａ及びＢ参照）、第２ノズル８５（図４Ｂ及びＣ参照）、分配油路８６（図４Ａ－Ｃ参照）、本体油路８７（図４Ａ－Ｃ参照）、第２枢軸油路８８（図４Ｂ及びＣ参照）、及びローラ油路８９（図４Ｂ及びＤ参照）を含む。 The transmission 10 includes an oil passage 80 that supplies oil to the trunnion 20 and the power roller 16. The oil passage 80 includes a first inflow oil passage 81 (see FIGS. 3 and 4A), a second inflow oil passage 82 (see FIGS. 3 and 4A), a first pivot oil passage 83 (see FIGS. 4A and B), and a first nozzle. 84 (see FIGS. 4A and B), second nozzle 85 (see FIGS. 4B and C), distribution oil passage 86 (see FIGS. 4A to C), main body oil passage 87 (see FIGS. 4A to C), second pivot oil passage 88 (see FIGS. 4B and C), and a roller oil passage 89 (see FIGS. 4B and D).
　第１流入油路８１は、ロッド３５内に形成され、傾転軸線方向Ｘに延びている。第２流入油路８２は、第１枢軸部２１内で幅方向Ｙに延び、傾転軸線Ａ３付近で第１流入油路８１と連通される。第１枢軸油路８３は、第１枢軸部２１の内部で突出方向Ｚに延びる。第１枢軸油路８３は、突出方向Ｚにおける中間部で第２流入油路８２と連通される。第１ノズル８４は、第１枢軸油路８３の突出方向Ｚにおける先端部と連通され、第１枢軸部２１の内面に開口してパワーローラ１６の周面４３と対向する。このように、本実施形態においては、第２流入油路８２と枢軸油路８３とが、第１枢軸部２１の内部に位置している。すなわち、第１ヨーク２７の貫通穴２９に嵌め込まれた状態では、幅方向Ｙに延びる第２流入油路８２と、突出方向Ｚに延びる枢軸油路８３とが、貫通穴２９の内部に位置することとなる。 The first inflow oil passage 81 is formed in the rod 35 and extends in the tilt axis direction X. The second inflow oil passage 82 extends in the width direction Y within the first pivot portion 21 and communicates with the first inflow oil passage 81 in the vicinity of the tilt axis A3. The first pivot oil passage 83 extends in the protruding direction Z inside the first pivot portion 21. The first pivot oil passage 83 communicates with the second inflow oil passage 82 at an intermediate portion in the protruding direction Z. The first nozzle 84 communicates with the tip portion of the first pivot oil passage 83 in the projecting direction Z, opens to the inner surface of the first pivot portion 21, and faces the peripheral surface 43 of the power roller 16. Thus, in the present embodiment, the second inflow oil passage 82 and the pivot oil passage 83 are located inside the first pivot portion 21. That is, in a state where the first yoke 27 is fitted in the through hole 29, the second inflow oil passage 82 extending in the width direction Y and the pivot oil passage 83 extending in the protruding direction Z are located inside the through hole 29. It will be.
　第２ノズル８５は、第２枢軸部２２の内面に開口してパワーローラ１６の周面４３と対向する。分配油路８６は、第１枢軸油路８３の突出方向Ｚにおける基端側にある基端部から本体部２３及び第２枢軸部２２の内部を通って第２ノズル８５に接続される。 The second nozzle 85 opens on the inner surface of the second pivot portion 22 and faces the peripheral surface 43 of the power roller 16. The distribution oil passage 86 is connected to the second nozzle 85 from the base end portion on the base end side in the protruding direction Z of the first pivot oil passage 83 through the inside of the main body portion 23 and the second pivot portion 22.
　分配油路８６は、本体部２３の内部に形成された本体油路８７、及び第２枢軸部２２の内部に形成される第２枢軸油路８８を含み、第１枢軸油路８３は本体油路８７と連通され、本体油路８７は第２枢軸油路８８と連通される。 The distribution oil passage 86 includes a main body oil passage 87 formed inside the main body portion 23 and a second pivot oil passage 88 formed inside the second pivot portion 22, and the first pivot oil passage 83 is a main body oil. The main body oil passage 87 is communicated with the second pivot oil passage 88.
　本体油路８７は、第１本体油路８７ａ、第２本体油路８７ｂ及び分岐本体油路８７ｃを含む。第１本体油路８７ａは、本体部２３の内部で傾転軸線方向Ｘに延び、第１枢軸油路８３の突出方向Ｚにおける基端部を取付孔５２に連通させる。 The main body oil passage 87 includes a first main body oil passage 87a, a second main body oil passage 87b, and a branch main body oil passage 87c. The first main body oil passage 87 a extends in the tilting axis direction X inside the main body portion 23, and the base end portion in the projecting direction Z of the first pivot oil passage 83 is communicated with the mounting hole 52.
　取付孔５２は傾転軸線Ａ３から幅方向Ｙの一方側に偏在している。また、第１枢軸部２１は、突出方向Ｚにおける先端部に、第１連結具５５が挿通される挿通穴５９を有する。そこで、第１枢軸油路８３は、取付孔５２と同様に、傾転軸線Ａ３から幅方向Ｙの一方側に偏在しており、傾転軸線Ａ３とねじれの位置にある。 The mounting hole 52 is unevenly distributed on one side in the width direction Y from the tilt axis A3. Further, the first pivot portion 21 has an insertion hole 59 through which the first connector 55 is inserted at the distal end portion in the protruding direction Z. Therefore, like the mounting hole 52, the first pivot oil passage 83 is unevenly distributed on one side in the width direction Y from the tilt axis A3 and is in a position twisted with the tilt axis A3.
　第２本体油路８７ｂは、取付孔５２を第２枢軸油路８８と連通させる。分岐本体油路８７ｃは、第１本体油路８７ａの途中から分岐して突出方向Ｚに延び、本体部２３の内面に開口する。 The second main body oil passage 87 b allows the mounting hole 52 to communicate with the second pivot oil passage 88. The branch main body oil passage 87 c branches from the middle of the first main body oil passage 87 a, extends in the protruding direction Z, and opens on the inner surface of the main body portion 23.
　ローラ油路８９は、第１ローラ油路８９ａ及び第２ローラ油路８９ｂを含む。第１ローラ油路８９ａは、フランジ４７の他端面及び支軸４５の端面に開口し、支持部１８の内部で回転軸線Ａ２の方向に延びる。第２ローラ油路８９ｂは、第１ローラ油路８９ａの途中から分岐して回転軸線Ａ２と略直交する方向に延びる。 The roller oil passage 89 includes a first roller oil passage 89a and a second roller oil passage 89b. The first roller oil passage 89a opens to the other end surface of the flange 47 and the end surface of the support shaft 45, and extends in the direction of the rotation axis A2 inside the support portion 18. The second roller oil passage 89b branches from the middle of the first roller oil passage 89a and extends in a direction substantially orthogonal to the rotation axis A2.
　油路８０は、ドリルなどの工具でトラニオン２０及び支持部１８に穿孔加工を施し、それにより形成された長穴内の要所にプラグ９１－９５（図４Ａ－Ｃ参照）を設けることによって構成される。 The oil passage 80 is configured by drilling the trunnion 20 and the support portion 18 with a tool such as a drill, and providing plugs 91-95 (see FIGS. 4A to 4C) at important points in the long holes formed thereby. The
　図４Ａに示すように、プラグ９１は、第２流入油路８２を構成するため第１枢軸部２１に形成された非貫通長穴の開口端を閉塞する。プラグ９２は、第１枢軸油路８３を構成するため第１枢軸部２１に形成された非貫通長穴の開口端を閉塞する。これら開口端は、第１枢軸部２１の外周面に配置され、プラグ９１，９２は、第１枢軸部２１に外嵌される軸受２５、及び軸受２５が内嵌される第１ヨーク２７（図３参照）で半径方向外周側から覆われる。 As shown in FIG. 4A, the plug 91 closes the open end of the non-through long hole formed in the first pivot portion 21 in order to constitute the second inflow oil passage 82. The plug 92 closes the opening end of the non-through long hole formed in the first pivot portion 21 in order to constitute the first pivot oil passage 83. These open ends are disposed on the outer peripheral surface of the first pivot portion 21, and the plugs 91 and 92 are externally fitted to the bearing 25, and the first yoke 27 (FIG. 3)) from the outer peripheral side in the radial direction.
　図４Ｂに示すように、プラグ９３は、第１本体油路８７ａを構成するため本体部２３に形成された長穴の開口端を閉塞する。この開口端は、第１枢軸部２１の外面に配置され、プラグ９３は軸受押え６９で傾転軸線方向Ｘの外側から覆われる。プラグ９４は、第２本体油路８７ｂを構成するため本体部２３に形成された長穴の開口端を閉塞する。この開口端は、第２枢軸部２２の外面に配置され、プラグ９４は軸受押え７０で傾転軸線方向Ｘの外側から覆われる。 As shown in FIG. 4B, the plug 93 closes the open end of the long hole formed in the main body portion 23 in order to constitute the first main body oil passage 87a. The open end is disposed on the outer surface of the first pivot portion 21, and the plug 93 is covered with the bearing retainer 69 from the outside in the tilt axis direction X. The plug 94 closes the open end of the long hole formed in the main body portion 23 in order to constitute the second main body oil passage 87b. This open end is disposed on the outer surface of the second pivot portion 22, and the plug 94 is covered with the bearing retainer 70 from the outside in the tilt axis direction X.
　図４Ｃに示すように、プラグ９５は、第２枢軸油路８８を構成するため第２枢軸部２２に形成された非貫通長穴の開口端を閉塞する。この開口端は、第２枢軸部２２の外周面に配置され、プラグ９５は、第２枢軸部２２に外嵌される軸受２６、及び軸受２６が内嵌される第２ヨーク２８（図３参照）で半径方向外周側から覆われる。 As shown in FIG. 4C, the plug 95 closes the open end of the non-through long hole formed in the second pivot portion 22 in order to constitute the second pivot oil passage 88. The open end is disposed on the outer peripheral surface of the second pivot portion 22, and the plug 95 includes a bearing 26 that is fitted on the second pivot portion 22, and a second yoke 28 in which the bearing 26 is fitted (see FIG. 3). ) In the radial direction.
　ケーシング２（図１参照）に貯留されている油は、第１流入油路８１及び第２流入油路８２を介し、第１枢軸油路８３に流入する。油は、第１枢軸油路８３内で突出方向Ｚの先端側に流れ、第１ノズル８４から周面４３であって入力接触部及び出力接触部のうち一方の近傍に吹き付けられる。油は、第１枢軸油路８３内で突出方向Ｚの基端側へ流れ、分配油路８６を通流し、第２ノズル８５から周面４３であって入力接触部及び出力接触部のうち他方の近傍に吹き付けられる。ノズル８４，８５は、パワーローラ１６の周面４３の接線方向に油を噴出する。このようにして、油がパワーローラ１６にトラクションオイルとして供給される。 The oil stored in the casing 2 (see FIG. 1) flows into the first pivot oil passage 83 via the first inflow oil passage 81 and the second inflow oil passage 82. The oil flows to the tip end side in the protruding direction Z in the first pivot oil passage 83, and is sprayed from the first nozzle 84 to the peripheral surface 43 near one of the input contact portion and the output contact portion. The oil flows to the proximal end side in the protruding direction Z in the first pivot oil passage 83, flows through the distribution oil passage 86, and is the peripheral surface 43 from the second nozzle 85 to the other of the input contact portion and the output contact portion. Is sprayed in the vicinity. The nozzles 84 and 85 eject oil in the tangential direction of the peripheral surface 43 of the power roller 16. In this way, oil is supplied to the power roller 16 as traction oil.
　分配油路８６では、油は、第１本体油路８７ａから取付孔５２内の軸受５１に潤滑油として供給される。取付孔５２からの流出油が、第２本体油路８７ｂ及び第２枢軸油路８８を介して第２ノズル８５に供給される。油は、分岐本体油路８７ｃを介し、軸受５０に潤滑油として供給される。軸受５０に供給された油は、第１ローラ油路８９ａを介して軸受４８に潤滑油として供給され、第２ローラ油路８９ｂを介して軸受４９に潤滑油として供給される。 In the distribution oil passage 86, oil is supplied as lubricating oil from the first main body oil passage 87 a to the bearing 51 in the mounting hole 52. Oil flowing out from the mounting hole 52 is supplied to the second nozzle 85 via the second main body oil passage 87 b and the second pivot oil passage 88. The oil is supplied as a lubricating oil to the bearing 50 through the branch main body oil passage 87c. The oil supplied to the bearing 50 is supplied as the lubricating oil to the bearing 48 through the first roller oil passage 89a, and is supplied as the lubricating oil to the bearing 49 through the second roller oil passage 89b.
　上記構成では、変速機１０が、傾転軸線Ａ３と同軸状に配置された一対の枢軸部２１，２２、及び傾転軸線方向Ｘにおいて一対の枢軸部２１，２２の間に位置してパワーローラ１６が取り付けられる本体部２３を有するトラニオン２０を備える。一対の枢軸部２１，２２が、本体部２３から傾転軸線方向Ｘと垂直な突出方向Ｚに突出する。ビーム５４が一対の枢軸部２１，２２に挿入される連結具５５，５６で一対の枢軸部２１，２２と連結される。即ち、一対の枢軸部２１，２２がビーム５４とトラニオン２０との連結信頼性を得るために必要となる連結具５５，５６の取り付け部を兼ねる。このため、一対の枢軸部２１，２２と傾転軸線方向Ｘに隣接する分厚い壁を設けなくてもよくなる。その結果、トラニオン２０を傾転軸線方向Ｘに小型化できる。 In the above configuration, the transmission 10 is positioned between the pair of pivot portions 21 and 22 disposed coaxially with the tilt axis A3 and the pair of pivot portions 21 and 22 in the tilt axis direction X. The trunnion 20 which has the main-body part 23 to which 16 is attached is provided. A pair of pivot portions 21 and 22 project from the main body portion 23 in a projecting direction Z perpendicular to the tilt axis direction X. The beam 54 is connected to the pair of pivot portions 21 and 22 by connecting tools 55 and 56 inserted into the pair of pivot portions 21 and 22. In other words, the pair of pivot portions 21 and 22 also serve as attachment portions for the connecting tools 55 and 56 that are necessary for obtaining the connection reliability between the beam 54 and the trunnion 20. For this reason, it is not necessary to provide a thick wall adjacent to the pair of pivot portions 21 and 22 and the tilt axis direction X. As a result, the trunnion 20 can be downsized in the tilt axis direction X.
　薄壁６５，６６は、主として軸受２５，２６を位置決めするという機能を果たすことを期待される。薄壁６５，６６の傾転軸線方向Ｘの寸法は、期待された機能に応じて極力小さく定められる。例えば、薄壁６５，６６の傾転軸線方向Ｘの寸法は、枢軸部２１，２２の傾転軸線方向Ｘの寸法の２０％未満である。 The thin walls 65 and 66 are expected to fulfill the function of positioning the bearings 25 and 26 mainly. The dimensions of the thin walls 65 and 66 in the tilt axis direction X are determined as small as possible according to the expected function. For example, the dimensions of the thin walls 65 and 66 in the tilt axis direction X are less than 20% of the dimensions of the pivot portions 21 and 22 in the tilt axis direction X.
　ビーム５４が、一対の枢軸部２１，２２の内面と傾転軸線方向Ｘに重ねられ、連結具５５，５６が傾転軸線方向Ｘに挿入される。これにより、軸受２５，２６が枢軸部２１，２２に外嵌され、傾転軸線方向Ｘと直交する方向（すなわち、枢軸部２１，２２の径方向）に連結具５５，５６を挿入することが困難であっても、ビーム５４を枢軸部２１，２２に連結することを実現できる。一対の枢軸部２１，２２が互いに向き合うように撓もうとする際に、連結具５５，５６に過大な剪断荷重が作用せず、連結信頼性が高い。 The beam 54 is overlapped with the inner surfaces of the pair of pivot portions 21 and 22 in the tilting axis direction X, and the couplers 55 and 56 are inserted in the tilting axis direction X. Thereby, the bearings 25 and 26 are fitted on the pivot portions 21 and 22, and the coupling tools 55 and 56 can be inserted in a direction orthogonal to the tilt axis direction X (that is, the radial direction of the pivot portions 21 and 22). Even if it is difficult, the beam 54 can be connected to the pivot portions 21 and 22. When the pair of pivot portions 21 and 22 are to be bent so as to face each other, an excessive shear load does not act on the couplers 55 and 56, and the coupling reliability is high.
　一対の枢軸部２１，２２は、内面の突出方向Ｚにおける先端部を傾転軸線方向Ｘの外側にオフセットすることで形成される一対の段差面５７，５８を有し、ビーム５４が突出方向Ｚにおいて段差面５７，５８に重ねられる。ビーム５４を枢軸部２１，２２の内面に重ねた状態に簡単に位置決めでき且つ簡単にその状態を維持でき、連結具５５，５６のセット作業を簡便に行うことができる。 The pair of pivot portions 21 and 22 have a pair of stepped surfaces 57 and 58 formed by offsetting the front end portion in the protruding direction Z of the inner surface to the outside of the tilt axis direction X, and the beam 54 extends in the protruding direction Z. Are overlaid on the step surfaces 57 and 58. The beam 54 can be easily positioned in a state where it is overlapped with the inner surfaces of the pivot portions 21 and 22, and the state can be easily maintained, and the setting work of the connectors 55 and 56 can be performed easily.
　連結具５５，５６は、ビーム５４に挿入される非ねじ部５５ｃ，５６ｃを有し、一対の枢軸部２１，２２の各々が、単一の連結具５５，５６でビーム５４に連結される。これにより、ビーム５４が連結具５５，５６及び枢軸部２１，２２に対して傾転軸線方向Ｘに相対移動できるので、トラニオン２０からの力をビーム５４にスムーズに伝達できる。第１連結具５５及び第２連結具５６が単一であって非ねじ部５５ｃ，５６ｃがビーム５４に挿入される場合、ビーム５４が連結具５５，５６の中心線周りに回転するおそれがある。本実施形態では、ビーム５４が段差面５７，５８に重ねられることで、このような回転を規制できる。 The connecting tools 55 and 56 have non-threaded portions 55 c and 56 c inserted into the beam 54, and each of the pair of pivot portions 21 and 22 is connected to the beam 54 by a single connecting tool 55 and 56. As a result, the beam 54 can move relative to the couplers 55, 56 and the pivot portions 21, 22 in the tilt axis direction X, so that the force from the trunnion 20 can be smoothly transmitted to the beam 54. When the first connector 55 and the second connector 56 are single and the non-threaded portions 55c and 56c are inserted into the beam 54, the beam 54 may rotate around the center line of the connectors 55 and 56. . In the present embodiment, the rotation of the beam 54 can be restricted by overlapping the stepped surfaces 57 and 58.
　枢軸部２１，２２は、本体部２３から突出し、その先端部でビーム５４と傾転軸線方向Ｘに重ねられた状態で連結される。枢軸部２１，２２は、パワーローラ１６が突出方向Ｚにおいて本体部２３とビーム５４の間に配置されるために十分大きな径を有する。 The pivot parts 21 and 22 protrude from the main body part 23 and are connected in a state of being overlapped with the beam 54 and the tilt axis direction X at the tip part. The pivot portions 21 and 22 have a sufficiently large diameter so that the power roller 16 is disposed between the main body portion 23 and the beam 54 in the projecting direction Z.
　図３及び４Ｄに示すように、本体部２３は、取付孔５２が形成されている高背部２３ａと、高背部２３ａを基準として幅方向Ｙの両側に位置する一対の低背部２３ｂ，２３ｃとを有する。一対の低背部２３ｂ，２３ｃは、高背部２３ａよりも薄肉であり（突出方向Ｚにおける寸法が短い）、本体部２３の外面は、高背部２３ａと低背部２３ｂ，２３ｃの間で段差がついている。高背部２３ａは、傾転軸線方向Ｘにおいて取付孔５２から離れるほど薄肉となる傾斜部２３ｄ，２３ｅを有している。本体部２３の余肉が極力除去されるので、トラニオン２０を軽量化できる。 As shown in FIGS. 3 and 4D, the main body portion 23 includes a high-back portion 23a in which a mounting hole 52 is formed, and a pair of low- back portions 23b and 23c located on both sides in the width direction Y with respect to the high-back portion 23a. Have. The pair of low- profile portions 23b and 23c is thinner than the high-profile portion 23a (the dimension in the protruding direction Z is shorter), and the outer surface of the main body 23 has a step between the high-profile portion 23a and the low- profile portions 23b and 23c. . The high-back portion 23a has inclined portions 23d and 23e that become thinner as they move away from the attachment hole 52 in the tilt axis direction X. Since the surplus of the main body 23 is removed as much as possible, the trunnion 20 can be reduced in weight.
　油路８０は、第１枢軸部２１の内部で突出方向Ｚに延びる第１枢軸油路８３を含む。第１枢軸油路８３により、傾転軸線Ａ３から突出方向Ｚに離れた部位に油を供給できる。第１枢軸油路８３を直線的に形成できるので、穿孔加工を簡便に行える。なお、第１流入油路及び第２流入油路も直線的に形成されるので、油を第１枢軸油路８３に導くまでの油路も簡便に製作できる。 The oil passage 80 includes a first pivot oil passage 83 extending in the protruding direction Z inside the first pivot portion 21. With the first pivot oil passage 83, oil can be supplied to a part away from the tilt axis A <b> 3 in the protruding direction Z. Since the first pivot oil passage 83 can be formed linearly, drilling can be performed easily. Since the first inflow oil passage and the second inflow oil passage are also formed linearly, the oil passage until the oil is guided to the first pivot oil passage 83 can be easily manufactured.
　トラニオン２０は、本体部２３の内面に開口する取付孔５２を有し、パワーローラ１６は、取付孔５２に回転可能に挿入される取付軸４６を介して本体部２３に取り付けられる。取付孔５２及び第１枢軸油路８３は、傾転軸線Ａ３から幅方向Ｙの一方側に偏在している。油路８０は、本体部２３の内部で傾転軸線方向Ｘに延び、第１枢軸油路８３の突出方向Ｚにおける基端部を取付孔５２に連通させる本体油路８７（特に、第１本体油路８７ａ）を含む。第１枢軸油路８３を取付孔５２と同方向に偏在させることで、第１枢軸油路８３及び本体油路８７（特に、第１本体油路８７ａ）を直線的に形成でき、穿孔加工を簡便に行える。また、第１枢軸油路８３の突出方向Ｚの長さが枢軸部２１，２２の直径よりも短くなり、穿孔加工を簡便に行える。 The trunnion 20 has an attachment hole 52 that opens to the inner surface of the main body 23, and the power roller 16 is attached to the main body 23 via an attachment shaft 46 that is rotatably inserted into the attachment hole 52. The mounting hole 52 and the first pivot oil passage 83 are unevenly distributed on one side in the width direction Y from the tilt axis A3. The oil passage 80 extends in the tilt axis direction X inside the main body portion 23, and a main body oil passage 87 (particularly, the first main body oil passage) that communicates the base end portion in the projecting direction Z of the first pivot oil passage 83 with the mounting hole 52. Including oil passage 87a). By causing the first pivot oil passage 83 to be unevenly distributed in the same direction as the mounting hole 52, the first pivot oil passage 83 and the main body oil passage 87 (particularly, the first main body oil passage 87a) can be formed linearly, and drilling can be performed. It can be done easily. In addition, the length of the first pivot oil passage 83 in the protruding direction Z is shorter than the diameter of the pivot portions 21 and 22, so that drilling can be performed easily.
　一対の枢軸部２１，２２の各々が、単一の連結具５５，５６でビーム５４に連結され、一対の連結具５５，５６が幅方向Ｙにおける枢軸部２１，２２の中央部で同軸状に配置される。連結具５５，５６がこのように配置されることで、ビーム５４を１点止めであっても安定的に枢軸部２１，２２に連結できる。前述のとおり、このように配置してもビーム５４の回転を規制できる。第１枢軸油路８３は幅方向Ｙに偏在しているので、挿通穴５９は第１枢軸油路８３と干渉しない。 Each of the pair of pivot portions 21 and 22 is connected to the beam 54 by a single connector 55 and 56, and the pair of connectors 55 and 56 are coaxial at the central portion of the pivot portions 21 and 22 in the width direction Y. Be placed. By arranging the couplers 55 and 56 in this way, the beam 54 can be stably coupled to the pivot portions 21 and 22 even if the beam 54 is stopped at one point. As described above, the rotation of the beam 54 can be restricted even in this arrangement. Since the first pivot oil passage 83 is unevenly distributed in the width direction Y, the insertion hole 59 does not interfere with the first pivot oil passage 83.
　油路８０は、第１ノズル８４、第２ノズル８５、及び第１枢軸油路８３の突出方向Ｚにおける基端部から本体部２３及び第２枢軸部２２の内部を通って第２ノズル８５に接続される分配油路８６を含む。ビーム５４を用いず本体部２３の内部を用いて油を第２ノズル８５まで分配する。このため、ビーム５４の幅及び高さを油路がない分小さくして小型化及び軽量化を図りながら、ビーム５４に必要な剛性を確保できる。ノズル８４，８５は、枢軸部２１，２２の内面に開口している。枢軸部２１，２２が大きな径を有することで内面は比較的広く確保されている。このため、ノズル８４，８５の開口位置を枢軸部２１，２２の内面上で自由に選択しやすくなり、パワーローラ１６の周面４３への給油最適化が図られる。 The oil passage 80 passes from the base end portion in the projecting direction Z of the first nozzle 84, the second nozzle 85, and the first pivot oil passage 83 to the second nozzle 85 through the inside of the main body portion 23 and the second pivot portion 22. A distribution oil passage 86 to be connected is included. The oil is distributed to the second nozzle 85 using the inside of the main body 23 without using the beam 54. For this reason, the rigidity required for the beam 54 can be ensured while reducing the width and height of the beam 54 by an amount corresponding to the absence of the oil passage to reduce the size and weight. The nozzles 84 and 85 are open on the inner surfaces of the pivot portions 21 and 22. Since the pivot portions 21 and 22 have a large diameter, a relatively wide inner surface is secured. For this reason, it becomes easy to freely select the opening positions of the nozzles 84 and 85 on the inner surfaces of the pivot portions 21 and 22, and the oil supply to the peripheral surface 43 of the power roller 16 is optimized.
　以上のように、本実施形態に係る変速機１０では、トラニオン２０が傾転軸線方向Ｘに小型化される。それに伴い、一対のヨーク２７，２８を傾転軸線方向Ｘにおいて互いに近付けることができる。 As described above, in the transmission 10 according to this embodiment, the trunnion 20 is downsized in the tilt axis direction X. Accordingly, the pair of yokes 27 and 28 can be brought close to each other in the tilt axis direction X.
　図２を参照して、これに伴い、取合面３６を第１ヨーク２７と共に変速機軸心Ａ１に近づけることができる。これにより、変速機１０が全体として傾転軸線方向Ｘにコンパクトになる。 Referring to FIG. 2, along with this, the coupling surface 36 can be brought close to the transmission shaft center A <b> 1 together with the first yoke 27. Thereby, the transmission 10 becomes compact in the tilt axis direction X as a whole.
　この変速機１０を組み込んだＩＤＧ１において、例えば、装置入力軸４ａは変速機軸心Ａ１と平行であり、装置入力軸４ａと変速機軸心Ａ１とを結ぶ直線Ｌの延在方向は、傾転軸線Ａ３と非垂直、更に言えば略平行である場合、第２ヨーク２８が変速機軸心Ａ１に近付くことで、第２ヨーク２８と装置入力軸４ａの間のスペースが拡大する。そこで、このスペースを埋めるように装置入力軸４ａを変速機軸心Ａ１に近づけてギヤ対４ｂを小径化できる。これにより、ＩＤＧ１がコンパクトになり且つ軽量になる。 In the IDG1 incorporating the transmission 10, for example, the device input shaft 4a is parallel to the transmission shaft center A1, and the extending direction of the straight line L connecting the device input shaft 4a and the transmission shaft center A1 is the tilt axis A3. When the second yoke 28 approaches the transmission shaft center A1, the space between the second yoke 28 and the device input shaft 4a is expanded. Therefore, the gear input 4b can be reduced in diameter by bringing the device input shaft 4a closer to the transmission shaft center A1 so as to fill this space. This makes IDG1 compact and lightweight.
　上記実施形態は一例であり、本発明の趣旨を逸脱しない範囲で適宜変更可能である。 The above embodiment is an example, and can be appropriately changed without departing from the gist of the present invention.
　例えば、非ねじ部５５ｃは非円形断面を有してもよい。段差面５７，５８が、幅方向Ｙに直線的に延びるのは一例で、傾転軸線方向Ｘに見て連結具５５，５６の中心線を中心とする円弧状でなければ回り止めの機能を果たせる。第１連結具５５はビーム５４と螺合してもよい。ビーム５４の一端部が複数の第１連結具５５で第１枢軸部２１と連結されてもよい。ビーム５４が一対の枢軸部２１，２２に傾転軸線Ａ３と直交する方向（枢軸部２１，２２の径方向）に重ねられ、連結具５５，５６が当該方向に挿入されてもよい。この場合、ビーム５４の一端部は、軸受２５や第１ヨーク２７の貫通穴２９に整合する形状に形成されていてもよい。ビーム５４の他端部、第２連結具５６及び第２枢軸部２２についても同様である。 For example, the non-threaded portion 55c may have a non-circular cross section. The step surfaces 57 and 58 are linearly extending in the width direction Y. The step surfaces 57 and 58 have a function of preventing rotation unless the step surfaces 57 and 58 have an arc shape centered on the center line of the couplers 55 and 56 when viewed in the tilt axis direction X. I can do it. The first connector 55 may be screwed with the beam 54. One end portion of the beam 54 may be connected to the first pivot portion 21 by a plurality of first connecting tools 55. The beam 54 may be superimposed on the pair of pivot portions 21 and 22 in a direction perpendicular to the tilt axis A3 (the radial direction of the pivot portions 21 and 22), and the connectors 55 and 56 may be inserted in that direction. In this case, one end of the beam 54 may be formed in a shape matching the bearing 25 or the through hole 29 of the first yoke 27. The same applies to the other end of the beam 54, the second connector 56, and the second pivot portion 22.
　また、トラニオン２０に対する油の供給は第２枢軸部２２から行ってもよい。この場合、幅方向Ｙに延びる第２流入油路８２に相当する油路が、第２枢軸部２２内に形成される。 Further, the supply of oil to the trunnion 20 may be performed from the second pivot portion 22. In this case, an oil passage corresponding to the second inflow oil passage 82 extending in the width direction Y is formed in the second pivot portion 22.
　変速機は、中央入力型に代えて中央出力型でもよい。中央出力型では、変速機入力軸が中空の変速機出力軸に挿通されて両側に突出し、入力側要素と出力側要素との配置関係が中央入力型と逆になる。変速機は、ダブルキャビティ型に代え、１組の入力ディスク及び出力ディスクを備えるシングルキャビティ型でもよい。 The transmission may be a central output type instead of the central input type. In the center output type, the transmission input shaft is inserted through the hollow transmission output shaft and protrudes on both sides, and the arrangement relationship between the input side element and the output side element is opposite to that of the central input type. The transmission may be a single cavity type including a pair of an input disk and an output disk instead of the double cavity type.
　また、入力ディスクと出力ディスクとに対するトラニオン（傾転軸線）の配置は、有効に動力伝達ができる限り、変更可能である。例えば、傾転軸線は、変速機軸心に垂直な平面において、変速機軸心を中心とする所定の大きさの仮想円に接していれば、適宜変更可能である。 Also, the arrangement of trunnions (tilt axis) with respect to the input disk and output disk can be changed as long as the power can be transmitted effectively. For example, the tilt axis can be appropriately changed as long as it touches a virtual circle having a predetermined size centered on the transmission axis in a plane perpendicular to the transmission axis.
　変速機は、ハーフトロイダル型に代えてフルトロイダル型でもよく、その際、パワーローラが円盤状に形成されてもよい。 The transmission may be a full toroidal type instead of a half toroidal type, and the power roller may be formed in a disk shape.
　装置入力軸は変速機軸心と直交し又はねじれの位置にあってもよく、ギヤ対は交差軸ギヤ又は食い違い軸ギヤでもよい。 The device input shaft may be orthogonal to the transmission shaft center or in a twisted position, and the gear pair may be a cross shaft gear or a staggered shaft gear.
　なお、前述した実施形態に示したトロイダル無段変速機は、航空機用発電装置への用途に限定されず、その他の用途の発電装置や、自動車または各種産業機械への用途で使用してもよい。 Note that the toroidal continuously variable transmission shown in the above-described embodiment is not limited to an application to an aircraft power generation apparatus, and may be used for another application power generation apparatus, an automobile, or various industrial machines. .
１　駆動機構一体型発電装置（ＩＤＧ）
３　発電機
４　入力機構
４ａ　装置入力軸
４ｂ　ギヤ対
１０　トロイダル無段変速機
１３　入力ディスク
１４　出力ディスク
１６　パワーローラ
２０　トラニオン
２１，２２　枢軸部
２３　本体部
４６　取付軸
５２　取付孔
５４　ビーム
５５，５６　連結具
５５ｃ，５６ｃ　非ねじ部
５７，５８　段差面
８０　油路
８３　第１枢軸油路
８４　第１ノズル
８５　第２ノズル
８６　分配油路
８７　本体油路
Ａ１　変速機軸心
Ａ２　回転軸線
Ａ３　傾転軸線
Ｘ　傾転軸線方向
Ｙ　幅方向
Ｚ　突出方向 1 Drive mechanism integrated power generator (IDG)
3 generator 4 input mechanism 4a device input shaft 4b gear pair 10 toroidal continuously variable transmission 13 input disk 14 output disk 16 power roller 20 trunnion 21, 22 pivot 23 main body 46 mounting shaft 52 mounting hole 54 beam 55, 56 connection Tools 55c, 56c Non-threaded portions 57, 58 Stepped surface 80 Oil passage 83 First pivot oil passage 84 First nozzle 85 Second nozzle 86 Distribution oil passage 87 Main body oil passage A1 Transmission shaft center A2 Rotation axis A3 Tilt axis X Inclination Roll axis direction Y Width direction Z Projection direction

Claims (10)

  1. 　互いに対向配置される入力ディスク及び出力ディスクと、
    　前記入力ディスクと前記出力ディスクとの間に傾転可能に挟まれ、前記入力ディスクの回転駆動力を傾転角に応じた変速比で前記出力ディスクに伝達するパワーローラと、
    　傾転軸線と同軸状に配置された一対の枢軸部、及び、傾転軸線方向において前記一対の枢軸部の間に位置して前記パワーローラが回転自在に取り付けられる本体部を有するトラニオンと、
    　前記パワーローラから見て前記本体部と反対側において前記傾転軸線方向に延びて前記トラニオンに連結されるビームと、を備え、
    　前記一対の枢軸部が、前記本体部から前記傾転軸線方向と垂直な突出方向に突出し、
    　前記ビームが前記一対の枢軸部に挿入される連結具で前記一対の枢軸部と連結される、トロイダル無段変速機。     An input disk and an output disk arranged opposite to each other;
    A power roller sandwiched between the input disk and the output disk so as to be tiltable, and transmitting a rotational driving force of the input disk to the output disk at a gear ratio according to a tilt angle;
    A pair of pivot portions arranged coaxially with the tilt axis, and a trunnion having a main body portion that is positioned between the pair of pivot portions in the tilt axis direction and to which the power roller is rotatably attached;
    A beam extending in the direction of the tilt axis on the side opposite to the main body as viewed from the power roller and connected to the trunnion,
    The pair of pivot portions protrude from the main body portion in a protruding direction perpendicular to the tilt axis direction,
    A toroidal continuously variable transmission in which the beam is connected to the pair of pivot parts by a connector inserted into the pair of pivot parts.
  2. 　前記ビームが、前記一対の枢軸部の内面と前記傾転軸線方向に重ねられ、前記連結具が前記傾転軸線方向に挿入される、請求項１に記載のトロイダル無段変速機。 2. The toroidal continuously variable transmission according to claim 1, wherein the beam is overlapped with an inner surface of the pair of pivot portions in the tilt axis direction, and the connector is inserted in the tilt axis direction.
  3. 　前記一対の枢軸部は、前記内面の前記突出方向における先端部を前記傾転軸線方向の外側にオフセットすることで形成される一対の段差面を有し、
    　前記ビームが前記突出方向において前記段差面に重ねられる、請求項２に記載のトロイダル無段変速機。     The pair of pivot portions have a pair of step surfaces formed by offsetting the tip portion of the inner surface in the protruding direction to the outside in the tilt axis direction,
    The toroidal continuously variable transmission according to claim 2, wherein the beam is superimposed on the step surface in the protruding direction.
  4. 　前記連結具は、前記ビームに挿入される非ねじ部を有し、
    　前記一対の枢軸部の各々が、単一の前記連結具で前記ビームに連結される、請求項３に記載のトロイダル無段変速機。     The connector has a non-threaded portion inserted into the beam,
    The toroidal continuously variable transmission according to claim 3, wherein each of the pair of pivot portions is coupled to the beam by a single coupling tool.
  5. 　前記一対の枢軸部の各々が、１つの前記連結具で、前記ビームに連結され、
    　前記一対の枢軸部に対応した一対の前記連結具が、前記傾転軸線及び前記突出方向に垂直な前記トラニオンの幅方向における前記枢軸部の中央部で、同軸状に配置される、請求項１乃至４のいずれか１項に記載のトロイダル無段変速機。     Each of the pair of pivot portions is connected to the beam by one connecting tool,
    2. The pair of coupling tools corresponding to the pair of pivot portions are arranged coaxially at a central portion of the pivot portion in the width direction of the trunnion perpendicular to the tilt axis and the protruding direction. The toroidal continuously variable transmission of any one of thru | or 4.
  6. 　前記トラニオン及び前記パワーローラに油を供給する油路、を備え、
    　前記油路は、前記一対の枢軸部のうちの一方である第１枢軸部の内部で前記突出方向に延びる第１枢軸油路を含む、請求項１乃至５のいずれか１項に記載のトロイダル無段変速機。     An oil passage for supplying oil to the trunnion and the power roller,
    6. The toroidal according to claim 1, wherein the oil passage includes a first pivot oil passage that extends in the protruding direction inside a first pivot portion that is one of the pair of pivot portions. Continuously variable transmission.
  7. 　前記トラニオンは、前記本体部の内面に開口する取付孔を有し、前記パワーローラは、前記取付孔に回転可能に挿入される取付軸を介して前記本体部に取り付けられ、
    　前記取付孔及び前記第１枢軸油路は、前記傾転軸線から前記傾転軸線方向及び前記突出方向に垂直な前記トラニオンの幅方向の一方側に偏在し、
    　前記油路は、前記本体部の内部で前記傾転軸線方向に延び、前記第１枢軸油路の前記突出方向における基端部を前記取付孔に連通させる本体油路を含む、請求項６に記載のトロイダル無段変速機。     The trunnion has an attachment hole that opens to the inner surface of the main body, and the power roller is attached to the main body via an attachment shaft that is rotatably inserted into the attachment hole.
    The mounting hole and the first pivot oil passage are unevenly distributed from the tilt axis to one side in the width direction of the trunnion perpendicular to the tilt axis direction and the protruding direction,
    The oil passage includes a main body oil passage that extends in the tilt axis direction inside the main body portion and communicates a base end portion in the protruding direction of the first pivot oil passage with the mounting hole. The toroidal continuously variable transmission described.
  8. 　前記油路は、前記第１枢軸油路の前記突出方向における先端部と連通し、前記第１枢軸部の内面に開口して前記パワーローラの周面と対向する第１ノズルと、前記一対の枢軸部のうちの他方である第２枢軸部の内面に開口して前記パワーローラの周面と対向する第２ノズルと、前記第１枢軸油路の前記突出方向における基端部から前記本体部及び前記第２枢軸部の内部を通って前記第２ノズルに接続される分配油路と、を含む、請求項６又は７に記載のトロイダル無段変速機。 The oil passage communicates with a distal end portion of the first pivot oil passage in the protruding direction, opens to an inner surface of the first pivot portion, and faces a peripheral surface of the power roller, and the pair of A second nozzle that opens on the inner surface of the second pivot portion that is the other of the pivot portions and faces the peripheral surface of the power roller; and a base end portion in the protruding direction of the first pivot oil passage from the main body portion The toroidal continuously variable transmission according to claim 6 or 7, further comprising a distribution oil passage connected to the second nozzle through the inside of the second pivot portion.
  9. 　請求項１乃至８のいずれか１項に記載のトロイダル無段変速機と、
    　航空機のエンジン回転軸から取り出される回転動力を前記トロイダル無段変速機に入力する入力機構と、
    　前記トロイダル無段変速機の出力で駆動される発電機と、を備える、航空機用駆動機構一体型発電装置。     A toroidal continuously variable transmission according to any one of claims 1 to 8,
    An input mechanism for inputting rotational power extracted from an engine rotation shaft of an aircraft to the toroidal continuously variable transmission;
    And a generator driven by an output of the toroidal continuously variable transmission.
  10. 　前記入力機構が、前記エンジン回転軸から取り出された回転動力が入力される装置入力軸と、前記装置入力軸の回転を前記トロイダル無段変速機に伝達するギヤ対とを備え、
    　前記装置入力軸が、前記トロイダル無段変速機の軸方向と平行であり、
    　前記トロイダル無段変速機の前記傾転軸線が、前記装置入力軸と前記トロイダル無段変速機における回転軸とを結ぶ直線の延在方向と非垂直である、請求項９に記載の航空機用駆動機構一体型発電装置。     The input mechanism includes a device input shaft to which rotational power extracted from the engine rotation shaft is input, and a gear pair that transmits rotation of the device input shaft to the toroidal continuously variable transmission;
    The device input shaft is parallel to the axial direction of the toroidal continuously variable transmission;
    10. The aircraft drive according to claim 9, wherein the tilt axis of the toroidal continuously variable transmission is non-perpendicular to an extending direction of a straight line connecting the device input shaft and a rotating shaft in the toroidal continuously variable transmission. Mechanism-integrated power generator.
PCT/JP2016/001255 2015-03-09 2016-03-08 Toroidal continuously variable transmission, and drive-mechanism-integrated power generating device for aircraft WO2016143329A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015046285A JP6554294B2 (en) 2015-03-09 2015-03-09 Toroidal continuously variable transmission and aircraft drive mechanism integrated power generator
JP2015-046285 2015-03-09

Publications (1)

Publication Number Publication Date
WO2016143329A1 true WO2016143329A1 (en) 2016-09-15

Family

ID=56879339

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2016/001255 WO2016143329A1 (en) 2015-03-09 2016-03-08 Toroidal continuously variable transmission, and drive-mechanism-integrated power generating device for aircraft

Country Status (2)

Country Link
JP (1) JP6554294B2 (en)
WO (1) WO2016143329A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021132070A1 (en) * 2019-12-25 2021-07-01 川崎重工業株式会社 Toroidal continuously variable transmission

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002106667A (en) * 2000-10-04 2002-04-10 Honda Motor Co Ltd Toroidal continuously variable transmission
JP2003065408A (en) * 2001-08-27 2003-03-05 Nsk Ltd Troidal type continuously variable transmission
JP2003202062A (en) * 2001-11-02 2003-07-18 Nsk Ltd Troidal type continuously variable transmission
JP2005054980A (en) * 2003-07-23 2005-03-03 Nsk Ltd Toroidal-type continuously variable transmission
JP2007051658A (en) * 2005-08-17 2007-03-01 Nsk Ltd Toroidal type continuously variable transmission
JP2007240004A (en) * 2007-05-07 2007-09-20 Nsk Ltd Power roller unit for toroidal continuously variable transmission
JP2015007464A (en) * 2013-06-26 2015-01-15 川崎重工業株式会社 Toroidal type stepless speed change device

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3991703B2 (en) * 2002-02-14 2007-10-17 日本精工株式会社 Toroidal continuously variable transmission

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002106667A (en) * 2000-10-04 2002-04-10 Honda Motor Co Ltd Toroidal continuously variable transmission
JP2003065408A (en) * 2001-08-27 2003-03-05 Nsk Ltd Troidal type continuously variable transmission
JP2003202062A (en) * 2001-11-02 2003-07-18 Nsk Ltd Troidal type continuously variable transmission
JP2005054980A (en) * 2003-07-23 2005-03-03 Nsk Ltd Toroidal-type continuously variable transmission
JP2007051658A (en) * 2005-08-17 2007-03-01 Nsk Ltd Toroidal type continuously variable transmission
JP2007240004A (en) * 2007-05-07 2007-09-20 Nsk Ltd Power roller unit for toroidal continuously variable transmission
JP2015007464A (en) * 2013-06-26 2015-01-15 川崎重工業株式会社 Toroidal type stepless speed change device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021132070A1 (en) * 2019-12-25 2021-07-01 川崎重工業株式会社 Toroidal continuously variable transmission
JP7449088B2 (en) 2019-12-25 2024-03-13 川崎重工業株式会社 toroidal continuously variable transmission

Also Published As

Publication number Publication date
JP2016166641A (en) 2016-09-15
JP6554294B2 (en) 2019-07-31

Similar Documents

Publication Publication Date Title
JP5320849B2 (en) Uniaxial eccentric screw pump
JP2008223492A (en) Rotor drive mechanism, sealing structure for eccentric shaft, and pump device
EP2327898A1 (en) Flexible coupling structure and ship thruster device with same
CN110303518B (en) Structure of joint part
WO2016143329A1 (en) Toroidal continuously variable transmission, and drive-mechanism-integrated power generating device for aircraft
US7568531B2 (en) Gear transmission device for power tool
JP2014213555A (en) Diameter expansion drill bit
JPH0861450A (en) Power transmission using planetary roller type gear changing mechanism
KR20190106742A (en) Gear unit
JP6278762B2 (en) Eccentric rocking gear device
WO2010079767A1 (en) Damper structure and rotating machine
US10744632B2 (en) Power tool
US9816503B2 (en) Uniaxial eccentric screw pump
JP2009191946A (en) Eccentric oscillation type gear device
JP2013053601A (en) Uniaxial eccentric screw pump and fluid motor
JP4678723B2 (en) Actuator
US20220252145A1 (en) Toroidal continuously variable transmission and drive mechanism-integrated electricity generation apparatus for aircraft
US12000474B2 (en) Toroidal continuously variable transmission and drive mechanism-integrated electricity generation apparatus for aircraft
WO2019146040A1 (en) Fluid cylinder
JP6611453B2 (en) Oblique shaft type axial piston machine with slide shoe on transmission flange
US20230027400A1 (en) Toroidal continuously variable transmission
JP2009058092A (en) Parallel dual-shaft type constant-velocity rotation transmission device
JP2019065986A (en) Rotary unit and cylinder device with the rotary unit
KR20160085123A (en) Gear box and turret apparatus of a turning center including the same
JP2016166641A5 (en)

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: 16761303

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: 16761303

Country of ref document: EP

Kind code of ref document: A1