WO2016143329A1 - 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 - Google Patents

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 Download PDF

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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
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WO
WIPO (PCT)
Prior art keywords
pivot
pair
oil passage
tilt axis
continuously variable
Prior art date
Application number
PCT/JP2016/001255
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English (en)
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
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Filing date
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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/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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. .

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  • 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)
PCT/JP2016/001255 2015-03-09 2016-03-08 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 WO2016143329A1 (ja)

Applications Claiming Priority (2)

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JP2015-046285 2015-03-09
JP2015046285A JP6554294B2 (ja) 2015-03-09 2015-03-09 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

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Cited By (1)

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Publication number Priority date Publication date Assignee Title
WO2021132070A1 (ja) * 2019-12-25 2021-07-01 川崎重工業株式会社 トロイダル無段変速機

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Publication number Priority date Publication date Assignee Title
JP2002106667A (ja) * 2000-10-04 2002-04-10 Honda Motor Co Ltd トロイダル型無段変速機
JP2003065408A (ja) * 2001-08-27 2003-03-05 Nsk Ltd トロイダル型無段変速機
JP2003202062A (ja) * 2001-11-02 2003-07-18 Nsk Ltd トロイダル型無段変速機
JP2005054980A (ja) * 2003-07-23 2005-03-03 Nsk Ltd トロイダル型無段変速機
JP2007051658A (ja) * 2005-08-17 2007-03-01 Nsk Ltd トロイダル型無段変速機
JP2007240004A (ja) * 2007-05-07 2007-09-20 Nsk Ltd トロイダル型無段変速機用パワーローラユニット
JP2015007464A (ja) * 2013-06-26 2015-01-15 川崎重工業株式会社 トロイダル型無段変速機

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Publication number Priority date Publication date Assignee Title
JP3991703B2 (ja) * 2002-02-14 2007-10-17 日本精工株式会社 トロイダル型無段変速機

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Publication number Priority date Publication date Assignee Title
JP2002106667A (ja) * 2000-10-04 2002-04-10 Honda Motor Co Ltd トロイダル型無段変速機
JP2003065408A (ja) * 2001-08-27 2003-03-05 Nsk Ltd トロイダル型無段変速機
JP2003202062A (ja) * 2001-11-02 2003-07-18 Nsk Ltd トロイダル型無段変速機
JP2005054980A (ja) * 2003-07-23 2005-03-03 Nsk Ltd トロイダル型無段変速機
JP2007051658A (ja) * 2005-08-17 2007-03-01 Nsk Ltd トロイダル型無段変速機
JP2007240004A (ja) * 2007-05-07 2007-09-20 Nsk Ltd トロイダル型無段変速機用パワーローラユニット
JP2015007464A (ja) * 2013-06-26 2015-01-15 川崎重工業株式会社 トロイダル型無段変速機

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021132070A1 (ja) * 2019-12-25 2021-07-01 川崎重工業株式会社 トロイダル無段変速機
JP2021102985A (ja) * 2019-12-25 2021-07-15 川崎重工業株式会社 トロイダル無段変速機
JP7449088B2 (ja) 2019-12-25 2024-03-13 川崎重工業株式会社 トロイダル無段変速機

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