WO2018180282A1 - Electric power steering device and shaft coupler used for same - Google Patents

Electric power steering device and shaft coupler used for same Download PDF

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Publication number
WO2018180282A1
WO2018180282A1 PCT/JP2018/008567 JP2018008567W WO2018180282A1 WO 2018180282 A1 WO2018180282 A1 WO 2018180282A1 JP 2018008567 W JP2018008567 W JP 2018008567W WO 2018180282 A1 WO2018180282 A1 WO 2018180282A1
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WO
WIPO (PCT)
Prior art keywords
shaft
fitting
ring
inner ring
coupling
Prior art date
Application number
PCT/JP2018/008567
Other languages
French (fr)
Japanese (ja)
Inventor
勝海 下田
前原　秀雄
Original Assignee
Ｋｙｂ株式会社
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Filing date
Publication date
Application filed by Ｋｙｂ株式会社 filed Critical Ｋｙｂ株式会社
Publication of WO2018180282A1 publication Critical patent/WO2018180282A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/64—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts
    • F16D3/68—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts the elements being made of rubber or similar material
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/04—Power-assisted or power-driven steering electrical, e.g. using an electric servo-motor connected to, or forming part of, the steering gear

Definitions

  • the present invention relates to an electric power steering apparatus and a shaft coupler used therefor.
  • JP2010 shaft coupling mechanism for an electric power steering apparatus that is disposed between two rotation shafts so as to transmit the rotation of one rotation shaft to the other rotation shaft and couples the two rotation shafts.
  • JP2010-60052A a shaft coupling mechanism for an electric power steering apparatus that is disposed between two rotation shafts so as to transmit the rotation of one rotation shaft to the other rotation shaft and couples the two rotation shafts.
  • One rotation transmission member 6 includes an outer cylindrical base 33, a plurality of protrusions 36 to 41 extending radially outward from the outer peripheral surface 34 of the outer cylindrical base 33, and one of the outer cylindrical base 33. It has a pair of engaging recesses 43 formed on the end face 42 and arranged symmetrically about the axis.
  • the other rotation transmission member 7 includes an inner cylindrical base 53, a plurality of protrusions 56 to 59 extending radially outward from the outer peripheral surface 54 of the inner cylindrical base 53, and the outer peripheral surface of the inner cylindrical base 53.
  • a pair of engaging claw portions 60 that are integrally formed in one end portion of 54 in an axially symmetrical manner and project outward in the radial direction.
  • the protrusions 56 to 59 of the rotation transmitting member 7 are inserted into the recesses 46 provided in the protrusions 41, 40, 38, and 37 of the rotation transmitting member 6. Accepted. Further, the engagement claw portion 60 of the rotation transmission member 7 is received in the engagement recess 43 of the rotation transmission member 6, and the axial removal of the inner cylindrical base portion 53 from the through hole 32 is prevented.
  • the protrusion 56 of the rotation transmission member 7 is provided in a recess 46 having a bottom portion provided on one end surface in the axial direction of the protrusions 41, 40, 38, and 37 of the rotation transmission member 6. To 59. Therefore, as shown in FIG. 18 of JP2010-60052A, when the rotation transmission member 6 and the rotation transmission member 7 are assembled, the rotation transmission member 6 is attached to the rotation transmission member 7 from the left side to the right side in the figure. The mounting direction is limited. For this reason, in the shaft coupling mechanism described in JP2010-60052A, there is room for improvement in the assembling property between the rotation transmission member 6 and the rotation transmission member 7.
  • the present invention aims to prevent misalignment of the inner ring and the outer ring and improve the assembling property of the inner ring and the outer ring.
  • a shaft coupler there is a shaft coupler, the first joint connected to the first shaft, the second joint connected to the second shaft, and between the first joint and the second joint.
  • the first joint and the second joint have a plurality of protrusions extending in the axial direction, the protrusions are arranged alternately in the circumferential direction, and the coupling is And a torque transmitting portion that is sandwiched between adjacent projecting portions of the first joint and the second joint and transmits the rotational torque of the first shaft to the second shaft, and the coupling includes an inner ring and an axial direction of the inner ring.
  • An outer ring that exposes both end surfaces and covers the radially outer peripheral surface of the inner ring, and the inner ring extends radially outward from the outer periphery of the inner cylindrical portion and the inner cylindrical portion.
  • a plurality of inner arms, The side ring includes a cylindrical outer cylindrical portion covering the inner cylindrical portion, and a plurality of outer arm portions extending radially outward from the outer periphery of the outer cylindrical portion and covering the inner arm portion,
  • the inner ring and the outer ring are different in rigidity
  • the torque transmission part has an inner arm part and an outer arm part, and each of the inner ring and the outer ring is engaged with each other to regulate displacement.
  • a fitting uneven part is provided.
  • FIG. 1 is a cross-sectional view of an electric power steering apparatus.
  • FIG. 2 is a perspective view of the worm side joint and the motor side joint.
  • 3A is a plan view of the coupling according to the first embodiment of the present invention, and FIG. 3B is a cross-sectional view taken along the line IIIb-IIIb in FIG. 3A.
  • FIG. 4 is a sectional view taken along the axial center plane of the shaft coupler.
  • FIG. 5A is a plan view of a coupling according to the second embodiment of the present invention, and FIG. 5B is a cross-sectional view taken along the line Vb-Vb in FIG.
  • FIG. 5C is a cross-sectional view taken along the line Vc-Vc in FIG.
  • FIG. 6A is a plan view of the coupling according to the third embodiment of the present invention
  • FIG. 6B is a cross-sectional view taken along the line VIb-VIb in FIG.
  • FIG. 6C is a cross-sectional view taken along the line VIc-VIc in FIG.
  • FIG. 7A is a plan view of the coupling according to the fourth embodiment of the present invention
  • FIG. 7B is a cross-sectional view taken along the line VIIb-VIIb in FIG. 7A.
  • FIG. 7C is a cross-sectional view taken along the line VIIc-VIIc in FIG.
  • the shaft coupler which concerns on embodiment of this invention connects the worm shaft in an electric power steering device, and the output shaft of an electric motor.
  • the electric power steering apparatus 101 will be described with reference to FIG.
  • the electric power steering device 101 is a device that is mounted on the vehicle and assists the steering force applied by the driver to the steering wheel.
  • the electric power steering device 101 includes a worm wheel 1 provided on a steering shaft linked to a steering handle, a worm shaft 2 meshing with the worm wheel 1, and an electric motor 7 connected to the worm shaft 2 via a shaft coupler 100. .
  • the worm shaft 2 rotates as the electric motor 7 is driven, and the rotation of the worm shaft 2 is decelerated and transmitted to the worm wheel 1.
  • the worm wheel 1 and the worm shaft 2 constitute a worm speed reducer.
  • the shaft coupler 100 connects the worm shaft 2 and the output shaft 7 a of the electric motor 7.
  • the shaft coupler 100 will be described in detail later.
  • the torque output from the electric motor 7 is transmitted from the worm shaft 2 to the worm wheel 1 and applied to the steering shaft as assist torque.
  • the torque output by the electric motor 7 corresponds to the steering torque calculated based on the torsion amount of the torsion bar that is twisted by the relative rotation between the input shaft and the output shaft constituting the steering shaft.
  • the worm shaft 2 is accommodated in a metal gear case 3.
  • a part of the worm shaft 2 is formed with a tooth part 2 a that meshes with the tooth part 1 a of the worm wheel 1.
  • An opening 3c is formed on the inner peripheral surface of the gear case 3 at a position corresponding to the tooth 2a, and the tooth 2a of the worm shaft 2 and the tooth 1a of the worm wheel 1 mesh with each other through the opening 3c.
  • the gear case 3 may be made of resin.
  • the base end side which is the electric motor 7 side of the worm shaft 2 is rotatably supported by the first bearing 4.
  • the first bearing 4 has a ball interposed between an annular inner ring and an outer ring.
  • the outer ring of the first bearing 4 is sandwiched between a step 3 a formed in the gear case 3 and the lock nut 5.
  • the inner ring of the first bearing 4 is sandwiched between the step 2 b of the worm shaft 2 and the worm side joint 6 connected to the worm shaft 2. Thereby, the movement to the axial direction of the worm shaft 2 is controlled.
  • the second bearing 11 is housed on the bottom of the gear case 3 via an L-shaped ring 10 as an annular elastic member having an L-shaped cross section.
  • the tip end side of the worm shaft 2 is rotatably supported by the second bearing 11.
  • the second bearing 11 has a ball interposed between an annular inner ring and an outer ring. A step 2c formed near the tip of the worm shaft 2 is locked to the inner ring of the second bearing 11.
  • the backlash in the axial direction of the second bearing 11 is reduced. That is, the L-shaped ring 10 is compressed between the bottom portion of the gear case 3 and the bottom portion of the second bearing 11 to pressurize the second bearing 11 in the axial direction.
  • a flange portion 17 having a flat end surface 17a is formed on the outer peripheral surface of the gear case 3 on the end side.
  • the flange portion 17 is formed with a through-hole 13 that opens toward the outer peripheral surface of the second bearing 11. The opening of the through hole 13 that opens to the end surface 17 a of the flange portion 17 is closed by the plug 14.
  • a coil spring 12 as an urging member compressed between the tip end surface of the plug 14 and the outer peripheral surface of the second bearing 11 is accommodated in the through hole 13.
  • the coil spring 12 biases the second bearing 11 in a direction in which the gap between the tooth portion 2a of the worm shaft 2 and the tooth portion 1a of the worm wheel 1 is reduced. That is, the coil spring 12 biases the worm shaft 2 toward the worm wheel 1 via the second bearing 11.
  • the inner peripheral surface 3 b surrounding the outer peripheral surface of the second bearing 11 in the gear case 3 has a pair of plane portions parallel to each other so that the second bearing 11 can move toward the worm wheel 1 by the biasing force of the coil spring 12. It is formed in a long hole shape.
  • the inner peripheral surface 3b may have any shape as long as the second bearing 11 can move inside the inner peripheral surface 3b.
  • the inner peripheral surface 3b may have a round hole shape whose inner diameter is larger than the outer diameter of the second bearing 11, and it is not necessary to form a pair of plane portions parallel to each other.
  • the second bearing 11 is urged toward the worm wheel 1 by the urging force of the coil spring 12, and there is no backlash.
  • the worm shaft 2 is inclined with the first bearing 4 as a fulcrum by the urging force of the coil spring 12, and the worm shaft 2 and the output shaft 7 a of the electric motor 7 are out of alignment.
  • Axial displacement between the worm shaft 2 and the output shaft 7 a of the electric motor 7 is allowed by the shaft coupler 100.
  • the shaft coupler 100 allows the shaft misalignment between the worm shaft 2 and the output shaft 7a of the electric motor 7 so that the worm shaft 2 is used as the output shaft 7a of the electric motor 7. It is necessary to tilt smoothly.
  • FIG. 2 is a perspective view of the worm side joint 6 and the motor side joint 8.
  • 3A is a plan view of the coupling 20
  • FIG. 3B is a cross-sectional view taken along the line IIIb-IIIb in FIG. 3A.
  • FIG. 4 is a cross-sectional view along the axial center plane of the shaft coupler 100.
  • the shaft coupler 100 includes a motor side joint 8 connected to the output shaft 7 a of the electric motor 7, a worm side joint 6 connected to the worm shaft 2, a motor side joint 8 and the worm side. And a coupling 20 provided between the joint 6 and for transmitting the rotational torque of the output shaft 7a of the electric motor 7 to the worm shaft 2.
  • the motor-side joint 8 protrudes from an annular base 31 in which a fitting hole 31 a to be press-fitted into the outer peripheral surface of the output shaft 7 a of the electric motor 7 is formed, and from the outer peripheral edge of the base 31. And a plurality of protrusions 32 extending in the axial direction.
  • the motor side joint 8 is made of a steel material.
  • the motor side joint 8 is connected to the output shaft 7a by press-fitting the fitting hole 31a into the outer peripheral surface of the output shaft 7a, thereby preventing the output shaft 7a from coming off and rotating.
  • the method for connecting the motor side joint 8 to the output shaft 7a is not limited to press-fitting, and other methods may be used as long as the motor side joint 8 is prevented from being detached and prevented from rotating with respect to the output shaft 7a.
  • the four protrusions 32 are formed at equal intervals in the circumferential direction.
  • the four protruding portions 32 are formed in a substantially arc shape with the central axis of the base portion 31 as the center.
  • the outer peripheral surface of the protrusion part 32 has a pair of plane part 32a extended in a substantially radial direction.
  • the worm side joint 6 has an annular base 41 formed with a fitting hole 41a to be press-fitted into the outer peripheral surface of the proximal end of the worm shaft 2, and a plurality of protrusions that protrude from the outer peripheral edge of the base 41 and extend in the axial direction. Part 42.
  • the worm side joint 6 is made of a steel material.
  • the worm side joint 6 is connected to the worm shaft 2 by press-fitting a fitting hole 41 a into the outer peripheral surface of the proximal end of the worm shaft 2, so that the worm side joint 6 is prevented from being detached and prevented from rotating.
  • the worm side joint 6 is press-fitted into the proximal end side outer peripheral surface of the worm shaft 2 until the end surface 41b of the base portion 41 comes into contact with the stepped portion 2d of the worm shaft 2 and the inner ring of the first bearing 4 (see FIG. 1).
  • the method for connecting the worm side joint 6 to the worm shaft 2 is not limited to press-fitting as with the motor side joint 8.
  • the four protrusions 42 are formed at equal intervals in the circumferential direction.
  • the four protruding portions 42 are formed in a substantially arc shape with the central axis of the base portion 41 as the center.
  • the outer peripheral surface of the protrusion part 42 has a pair of plane part 42a extended in a substantially radial direction.
  • the motor side joint 8 and the worm side joint 6 have the same shape, and as shown in FIG. 4, the protrusions 32 and 42 are arranged to face each other so that they are alternately arranged at equal intervals in the circumferential direction.
  • the coupling 20 will be described with reference to FIG.
  • the center axis CA of the coupling 20 coincides with the center axes of the inner ring 21 and the outer ring 25 described later.
  • the axial direction is a direction parallel to the central axis CA.
  • the coupling 20 includes an inner ring 21 and an outer ring 25 that covers the radially outer peripheral surface of the inner ring 21.
  • the inner ring 21 has a cylindrical inner cylindrical portion 22 and a plurality of rectangular arm-shaped inner arm portions 23.
  • the plurality of inner arm portions 23 extend radially outward from the outer periphery of the inner cylindrical portion 22 about the central axis CA.
  • the eight inner arm portions 23 are arranged at equal intervals in the circumferential direction (that is, at intervals of 45 degrees).
  • the shape of the outer peripheral surface of the inner ring 21 is a rotationally symmetric shape with the central axis CA as the center.
  • a rotationally symmetric shape is a shape that does not change when it is rotated about a central axis CA, which is a symmetry axis, by a certain angle.
  • the outer ring 25 includes a cylindrical outer cylindrical portion 26 and a plurality of outer arm portions 27 having a hollow rectangular parallelepiped shape.
  • the plurality of outer arm portions 27 extend radially outward from the outer periphery of the outer cylindrical portion 26 about the central axis CA.
  • the outer cylindrical portion 26 covers the entire outer surface of the inner cylindrical portion 22, and the outer arm portion 27 covers the entire outer surface of the inner arm portion 23.
  • the outer arm portion 27 is provided corresponding to the inner arm portion 23.
  • the eight outer arm portions 27 are arranged at equal intervals in the circumferential direction (that is, at intervals of 45 degrees).
  • the shapes of the inner peripheral surface and the outer peripheral surface of the outer ring 25 are rotationally symmetric with respect to the central axis CA.
  • the outer cylindrical portion 26 has a circular through hole 26h penetrating in the axial direction
  • the outer arm portion 27 has a rectangular through hole 27h penetrating in the axial direction.
  • the through hole 26h and the through hole 27h are in communication with each other and form an opening 25h into which the inner ring 21 is inserted.
  • the axial dimensions of the inner cylindrical portion 22, the inner arm portion 23, the outer cylindrical portion 26, and the outer arm portion 27 are the same.
  • the axial end surface of the inner ring 21 and the axial end surface of the outer ring 25 are flush with each other, and both axial end surfaces of the inner ring 21 are exposed from the opening 25h of the outer ring 25, respectively.
  • the inner ring 21 when the inner ring 21 is assembled to the outer ring 25, the inner arm portion 23 and the outer arm portion 27 are overlapped to form a torque transmission portion 51 having a laminated structure in the circumferential direction.
  • the torque transmission unit 51 is sandwiched between the planar portions 32 a and the planar portions 42 a of the adjacent projecting portions 32 and 42 of the motor side joint 8 and the worm side joint 6, and transmits the rotational torque of the electric motor 7 to the worm shaft 2.
  • the torque transmission part 51 is extended in the substantially radial direction so that it may fit in the clearance gap between the adjacent protrusion parts 32 and 42. As shown in FIG.
  • the plurality of torque transmission parts 51 are arranged radially around the output shaft 7 a of the electric motor 7. Thereby, the rotational torque of the electric motor 7 is transmitted from the projecting portion 32 of the motor side joint 8 to the projecting portion 42 of the worm side joint 6 through the torque transmitting portion 51 and is transmitted to the worm shaft 2.
  • the inner ring 21 and the outer ring 25 have different rigidity.
  • the inner ring 21 is formed of a flexible rubber having a relatively low rigidity (that is, a small Young's modulus), and the outer ring 25 is relatively rigid (that is, a Young's modulus is small). Large) resin.
  • the torque transmitting portion 51 Since the outer ring 25 covers the outer peripheral surface of the inner ring 21, the torque transmitting portion 51 has a three-layer structure in which rubber is sandwiched between resins in the circumferential direction. In this way, by configuring the torque transmitting portion 51 with two types of materials having different rigidity, it is possible to obtain characteristics having both rigidity and flexibility. Therefore, the coupling 20 functions to efficiently transmit the rotational torque of the electric motor 7 to the worm shaft 2 and to allow an axial deviation between the worm shaft 2 and the output shaft 7 a of the electric motor 7.
  • fitting uneven portions for restricting the positional deviation of the inner ring 21 and the outer ring 25 are provided in the inner ring 21 and the outer ring 25.
  • the fitting uneven portion will be described in detail.
  • the outer peripheral surface of the inner cylindrical portion 22 between the adjacent inner arm portions 23 is provided with a fitting convex portion 22f protruding radially outward.
  • the fitting convex portion 22f has a rectangular parallelepiped shape. In the present embodiment, eight fitting convex portions 22f are provided.
  • the fitting protrusion 22 f is formed symmetrically with respect to the axial center plane CP of the coupling 20 at the axial center of the inner ring 21.
  • the axial center plane CP of the coupling 20 is a plane located at the axial center of the coupling 20 and is a plane orthogonal to the central axis CA.
  • the axial center plane CP of the coupling 20 coincides with the axial center planes of the inner ring 21 and the outer ring 25.
  • a fitting recess 26f that is recessed radially outward is provided on the inner peripheral surface of the outer cylindrical portion 26 between the adjacent outer arm portions 27, a fitting recess 26f that is recessed radially outward is provided.
  • eight fitting recesses 26f are provided on the inner peripheral surface of the outer cylindrical portion 26 between the adjacent outer arm portions 27 .
  • the fitting recess 26 f is formed symmetrically with respect to the axial center plane CP of the coupling 20 at the axial center of the outer ring 25.
  • both axial end surfaces of the fitting convex portion 22f are in contact with both axial end surfaces of the fitting concave portion 26f. Touch. For this reason, when the fitting convex part 22f and the fitting concave part 26f fit each other, the positional deviation of the inner ring 21 and the outer ring 25 in the axial direction is restricted.
  • the output shaft 7a of the electric motor 7 is press-fitted over the entire length of the fitting hole 31a in order to be firmly fixed to the fitting hole 31a of the motor side joint 8, and the tip of the output shaft 7a. Protrudes from the fitting hole 31a.
  • the worm shaft 2 is press-fitted over the entire length of the fitting hole 41a in order to be firmly fixed to the fitting hole 41a of the worm side joint 6, and the tip of the worm shaft 2 protrudes from the fitting hole 41a. Yes.
  • the inner cylindrical portion 22 has a circular through hole 22h penetrating in the axial direction.
  • the through hole 22h has an inner diameter larger than the outer diameter of the output shaft 7a and the worm shaft 2 so as not to interfere with the output shaft 7a and the worm shaft 2.
  • a gap 90a having a predetermined length is formed between the inner peripheral surface of the through hole 22h of the inner cylindrical portion 22 and the output shaft 7a.
  • a gap 90 b having a predetermined length is formed between the inner peripheral surface of the through hole 22 h of the inner cylindrical portion 22 and the worm shaft 2.
  • the radial lengths of the gaps 90a and 90b are larger than the protruding height dimension (radially protruding length) of the fitting convex portion 22f shown in FIG.
  • the diameter of the through hole 22h of the inner cylindrical portion 22 is set so that the radial lengths of the gaps 90a and 90b are smaller than the protruding height dimension of the fitting convex portion 22f. .
  • the diameters of the inner ring 21 and the outer ring 25 are set by setting the radial lengths of the gaps 90a and 90b to be smaller than the protruding height dimension of the fitting convex portion 22f and restricting the amount of movement of the inner ring 21 in the radial direction.
  • Directional misregistration is regulated.
  • the assembly procedure of the shaft coupler 100 will be described.
  • the outer ring 25 and the inner ring 21 are individually manufactured in advance by molding.
  • the inner ring 21 is inserted into the opening 25h of the outer ring 25.
  • the inner ring 21 is inserted into the opening 25 h of the outer ring 25 until both axial end surfaces of the inner ring 21 and both end surfaces of the outer ring 25 are flush with each other.
  • the inner ring 21 may be inserted from one axial end side of the outer ring 25 or may be inserted from the other axial end side of the outer ring 25.
  • the fitting convex portion 22 f is inserted into the through hole 26 h of the outer ring 25 by elastically deforming the inner cylindrical portion 22 toward the central axis CA. Can do.
  • the inner ring 21 is inserted into the opening 25h of the outer ring 25 until the end surface of the inner ring 21 and the end surface of the outer ring 25 coincide with each other, and then the inner side of the inner cylindrical portion 22 is pressed outward in the radial direction.
  • the mating convex portion 22f is fitted into the fitting concave portion 26f. Thereby, the assembly of the inner ring 21 and the outer ring 25 is completed, and the coupling 20 is completed.
  • the motor side joint 8 is connected to the output shaft 7a by press-fitting the fitting hole 31a of the motor side joint 8 into the outer peripheral surface on the tip side of the output shaft 7a of the electric motor 7.
  • the worm side joint 6 is connected to the worm shaft 2 by press-fitting the fitting hole 41 a of the worm side joint 6 into the base end side outer peripheral surface of the worm shaft 2.
  • the coupling 20 After attaching the coupling 20 to one of the motor side joint 8 and the worm side joint 6, the worm shaft 2 and the output shaft 7a of the electric motor 7 are connected.
  • the coupling 20 is fitted to each protrusion 32 of the motor side joint 8.
  • Each torque transmitting portion 51 of the coupling 20 is brought into contact with one of the pair of flat surface portions 32a of each protruding portion 32.
  • the gear case 3 and the electric motor 7 are connected so that each protrusion 42 of the worm side joint 6 is inserted into a gap between the adjacent torque transmission parts 51.
  • the torque transmission part 51 of the coupling 20 will be in the state pinched
  • the worm shaft 2 and the output shaft 7 a of the electric motor 7 are connected via the shaft coupler 100.
  • the coupling 20 is assembled first to the motor side joint 8 or the worm side joint 6 does not depend on the order in which the worm shaft 2 and the electric motor 7 are assembled. That is, when the electric motor 7 is assembled first, the coupling 20 may be assembled to the motor side joint 8 first, or the coupling 20 is assembled to the worm side joint 6 of the worm shaft 2 assembled later. After that, the worm shaft 2 and the output shaft 7a of the electric motor 7 may be connected. Further, when the worm shaft 2 is assembled first, the coupling 20 may be assembled to the worm side joint 6 first, or the coupling 20 is assembled to the motor side joint 8 of the electric motor 7 assembled later. After that, the worm shaft 2 and the output shaft 7a of the electric motor 7 may be connected.
  • the coupling 20 includes an inner ring 21 and an outer ring 25 that exposes both axial end surfaces of the inner ring 21 and covers the radially outer peripheral surface of the inner ring 21. Since both end surfaces in the axial direction of the inner ring 21 assembled to the outer ring 25 are exposed, the inner ring 21 can be attached from either side of the outer ring 25 in the axial direction. That is, the degree of freedom in the mounting direction is high, and the assemblability of the inner ring 21 and the outer ring 25 can be improved.
  • the inner ring 21 and the outer ring 25 have different rigidity. For this reason, it is possible to optimize the rigidity characteristics of the torque transmission unit 51 constituted by the inner arm part 23 and the outer arm part 27, and efficiently transmit the rotational torque of the electric motor 7 to the worm shaft 2, An axial deviation between the worm shaft 2 and the output shaft 7a of the electric motor 7 can be allowed.
  • Each of the inner ring 21 and the outer ring 25 is provided with a fitting uneven portion that regulates the displacement by fitting with each other.
  • the fitting protrusion 22f is provided on the inner ring 21 and the fitting recess 26f is provided on the outer ring 25 as the fitting irregularities.
  • the shape of the outer peripheral surface of the inner ring 21 (the outer peripheral surface including the fitting convex portion 22f) and the shape of the inner peripheral surface of the outer ring 25 (the outer peripheral surface including the fitting concave portion 26f) are the central axis of the coupling 20 It is a rotationally symmetric shape centered on CA.
  • the fitting convex part 22f and the fitting concave part 26f are provided in all eight places between the adjacent torque transmission parts 51 in total. In this way, the inner arm portion 23 and the outer arm portion 27, and the fitting convex portion 22f and the fitting concave portion 26f are arranged so that the phases are evenly allocated to the central axis CA.
  • the inner ring 21 and the outer ring 25 can be assembled even if the phase is not a specific phase in the circumferential direction. For example, assembly is possible even when the phases of the inner arm portion 23 and the outer arm portion 27 are shifted by one pitch. According to this embodiment, since the freedom degree of the alignment of the rotation direction of the inner side ring 21 and the outer side ring 25 can be improved, the assembly property of the inner side ring 21 and the outer side ring 25 can be improved.
  • the fitting convex portion 22f and the fitting concave portion 26f are formed symmetrically with respect to the axial center plane CP of the coupling 20. Accordingly, when the inner ring 21 is inserted into the opening 25 h of the outer ring 25, the inner ring 21 can be assembled to the outer ring 25 regardless of whether the inner ring 21 is inserted from both axial ends. That is, the inner ring 21 and the outer ring 25 can be assembled regardless of the combination of the front and back sides. Since the degree of freedom of the orientation of the inner ring 21 when inserting the inner ring 21 into the opening 25h of the outer ring 25 is high, the assembling property of the inner ring 21 and the outer ring 25 can be improved.
  • FIG. 5A is a plan view of the coupling 220
  • FIG. 5B is a cross-sectional view taken along the line Vb-Vb of FIG. 5A.
  • FIG. 5C is a cross-sectional view taken along the line Vc-Vc in FIG.
  • corrugated part (fitting convex part 22f, the fitting recessed part 26f) was provided in the multiple places at equal intervals in the circumferential direction.
  • fitting concave and convex portions are provided over the entire circumference of the outer peripheral surface of the inner ring 221 and the inner peripheral surface of the outer ring 225. It has been.
  • the coupling 220 will be described in detail.
  • structures other than the coupling 220 in the electric power steering apparatus of the second embodiment are the same as those of the first embodiment, description thereof is omitted.
  • the inner cylindrical portion 222 is provided with a fitting convex portion 222f that protrudes outward from the outer peripheral surface by a predetermined length.
  • the inner arm portion 223 is provided with a fitting convex portion 223f that protrudes outward from the outer peripheral surface by a predetermined length.
  • the fitting convex portion 222f and the fitting convex portion 223f are continuous, and constitute an annular fitting convex portion 221f along the outer periphery of the inner ring 221.
  • the outer cylindrical portion 226 is provided with a fitting concave portion 226f that is recessed by a predetermined length outward from the inner peripheral surface.
  • the outer arm portion 227 is provided with a fitting recess 227f that is recessed by a predetermined length outward from the inner peripheral surface.
  • the fitting recess 226f and the fitting recess 227f are continuous, and form an annular fitting recess 225f along the inner periphery of the outer ring 225.
  • FIG. 6 (a) is a plan view of the coupling 320
  • FIG. 6 (b) is a cross-sectional view taken along the line VIb-VIb of FIG. 6 (a).
  • FIG. 6C is a cross-sectional view taken along the line VIc-VIc in FIG.
  • corrugated part fitting convex part 22f, fitting recessed part 26f was set as the structure which controls the position shift of the axial direction of the inner side ring 21 and the outer side ring 25. As shown in FIG.
  • 3rd Embodiment it is set as the structure by which a fitting uneven
  • FIG. Hereinafter, the coupling 320 will be described in detail.
  • structures other than the coupling 320 in the electric power steering apparatus of the third embodiment are the same as those of the first embodiment, description thereof is omitted.
  • the inner cylindrical portion 322 is provided with the fitting convex portion 22f described in the first embodiment (see FIG. 3A).
  • the outer cylindrical portion 326 is not provided with the fitting recess 26f (see FIG. 3B) described in the first embodiment. Therefore, in the third embodiment, there is no portion in the coupling 320 that regulates the positional deviation in the axial direction.
  • the inner arm portion 323 is provided with a fitting recess 323f that is recessed so that the base end portion is narrow.
  • the fitting recess 323f is formed from one end to the other end of the inner arm 323 in the axial direction.
  • the inner arm portion 323 has a narrow portion 355 on the proximal end side and a wide portion 356 on the distal end side, and both end surfaces in the circumferential direction of the narrow portion 355 and the wide portion. Both end surfaces in the circumferential direction of 356 are connected by a pair of inclined surfaces 357.
  • the pair of inclined surfaces 357 constitute one side surface of the trapezoidal columnar fitting recess 323f.
  • the outer cylindrical portion 326 is provided with a fitting convex portion 326f that fits into the fitting concave portion 323f of the inner arm portion 323.
  • a fitting convex portion 326f that fits into the fitting concave portion 323f of the inner arm portion 323.
  • one side surface of the fitting concave portion 323f constituting the pair of inclined surfaces 357 and one side surface of the fitting convex portion 326f of the outer cylindrical portion 326 are in contact with each other. Touch.
  • the step portion between the narrow portion 355 and the wide portion 356 of the inner arm portion 323 is configured to be caught by the pair of fitting convex portions 326f, the diameters of the inner ring 321 and the outer ring 325 are set.
  • Directional misregistration is regulated.
  • Each of the inner ring 321 and the outer ring 325 is provided with a fitting uneven part that regulates displacement by fitting each other.
  • the fitting recesses 323f are provided on the inner ring 321 and the fitting projections 326f are provided on the outer ring 325 as the fitting unevenness portions.
  • FIG. 7A is a plan view of the coupling 420
  • FIG. 7B is a cross-sectional view taken along the line VIIb-VIIb of FIG. 7A.
  • FIG. 7C is a cross-sectional view taken along the line VIIc-VIIc in FIG.
  • grooved part was set as the structure which controls the position shift of the axial direction of the inner side rings 21 and 221 and the outer side rings 25 and 225.
  • 3rd Embodiment it was set as the structure by which a fitting uneven
  • the inner arm portion 423 connects a pair of plane portions 457 parallel to the radial direction and the axial direction, and ends of the pair of plane portions 457 in the radial direction. And a belt-like portion 458.
  • the plane part 457 and the band-like part 458 are each rectangular.
  • a fitting convex portion 423f and a fitting concave portion 425f are provided.
  • the fitting convex portion 423f is a rectangular parallelepiped convex portion that protrudes outward in the circumferential direction from the pair of flat surface portions 457 of the inner arm portion 423.
  • the fitting concave portion 425f is a rectangular parallelepiped concave portion that fits into the fitting convex portion 423f, and is continuously provided on the outer cylindrical portion 426 and the outer arm portion 427 of the outer ring 425.
  • both axial end surfaces of the fitting convex portion 423f are in contact with both axial end surfaces of the fitting concave portion 425f. Touch.
  • both radial end surfaces of the fitting convex portion 423f are both radial end surfaces of the fitting concave portion 425f. Abut. Therefore, when the fitting convex portion 423f and the fitting concave portion 425f are fitted to each other, the axial and radial positional deviations of the inner ring 421 and the outer ring 425 are restricted.
  • the fitting convex portion 22f of the inner ring 21 described in the first embodiment is fitted into the fitting concave portion 225f of the outer ring 225 described in the second embodiment. May be combined.
  • the fitting irregularities (22f, 26f) described in the first embodiment and the fitting irregularities (423f, 425f) described in the fourth embodiment may be further provided in the coupling 320 of the third embodiment. .
  • the shaft coupler 100 that connects the worm shaft 2 of the electric power steering apparatus 101 and the output shaft 7a of the electric motor 7 has been described as an example, but the present invention is not limited to this.
  • the present invention may be applied to a shaft coupler that connects the output shaft of the first electric motor and the output shaft of the second electric motor.
  • the present invention can be applied to shaft couplers of various apparatuses without being limited to the shaft couplers used in the electric power steering apparatus.
  • the shape of the outer peripheral surface of the inner rings 21, 221, 321, 421 and the shape of the inner peripheral surface of the outer rings 25, 225, 325, 425 are the central axes of the couplings 20, 220, 320, 420, respectively.
  • an example of a rotationally symmetric shape centered on CA has been described, the present invention is not limited to this.
  • the inner rings 21, 221 and 421 are provided with fitting convex portions 22f, 221f and 423f
  • the outer rings 25, 225 and 425 are provided with fitting concave portions 26f, 225f and 425f.
  • the present invention is not limited to this.
  • the fitting recess 323f is provided in the inner ring 321 and the fitting protrusion 326f is provided in the outer ring 325 has been described, but the present invention is not limited to this.
  • the relationship between the fitting convex part and the fitting concave part may be reversed.
  • the inner rings 21, 221, 321, 421 are formed of rubber, and the outer rings 25, 225, 325, 425 are formed of a resin having a rigidity higher than that of the material of the inner rings 21, 221, 321, 421.
  • the outer rings 25, 225, 325, and 425 may be formed of rubber, and the inner rings 21, 221, 321, and 421 may be formed of a resin having higher rigidity than the material of the outer rings 25, 225, 325, and 425.
  • the material is not limited to a combination of rubber and resin.
  • the inner rings 21, 221, 321, 421 and the outer rings 25, 225, 325 are made of various materials so that the inner rings 21, 221, 321, 421 and the outer rings 25, 225, 325, 425 have different rigidity. , 425 materials can be selected and the rigidity characteristics can be adjusted.
  • the motor side joint 8 and the worm side joint 6 are exemplified as having the four protrusions 32 and 42, respectively.
  • the number of the protrusions 32 and 42 is not limited to four, and a plurality of protrusions 32 and 42 are provided. If it is.
  • the number of the protrusions 32 and 42 may be three.
  • the outer rings 25, 225, 325, 425 and the inner rings 21, 221, 321, 421 are individually molded, and the inner rings 21, 221,
  • the present invention is not limited to this.
  • the couplings 20, 220, 320, 420 are integrally molded. May be.
  • the shaft coupler 100 includes a motor side joint (first joint) 8 connected to the output shaft (first axis) 7 a and a worm side joint (second joint) 6 connected to the worm shaft (second axis) 2. And couplings 20, 220, 320, 420 provided between the motor side joint (first joint) 8 and the worm side joint (second joint) 6, and the motor side joint (first joint) 8
  • the worm side joint (second joint) 6 has a plurality of protrusions 32 and 42 extending in the axial direction, and the protrusions 32 and 42 are arranged so as to be alternately arranged in the circumferential direction.
  • Reference numerals 220, 320, and 420 denote adjacent protrusions 3 of the motor side joint (first joint) 8 and the worm side joint (second joint) 6.
  • the couplings 20, 220, 320, 420 are Outer rings 25, 225 that expose both axial ends of the inner rings 21, 221, 321, 421 and the inner rings 21, 221, 321, 421 and cover the radially outer peripheral surfaces of the inner rings 21, 221, 321, 421 , 325, 425, and the inner rings 21, 221, 321, 421 are formed radially outward from the outer periphery of the inner cylindrical portions 22, 222, 322 and the inner cylindrical portions 22, 222, 322.
  • a plurality of radially extending inner arms 23, 223, 323, and 423, and the outer rings 25, 225, 325, and 425 connect the inner cylindrical portions 22, 222, and 322, respectively.
  • a plurality of outer arm portions 27, 227, and 427 covering the inner ring 21, 221, 321, 421 and the outer rings 25, 225, 325, 425 are different in rigidity and the torque transmitting portions 51, 351.
  • Has inner arm portions 23, 223, 323, 423 and outer arm portions 27, 227, 427, and inner rings 21, 221, 321, 421 and outer rings 25, 225, 325, 425 are respectively As fitting irregularities that regulate displacement by fitting each other, fitting convex portions 22f, 221f, 423f, fitting concave portion 323f, and fitting concave portions 26f, 225f, 42 are provided. 5f and fitting convex part 326f are provided.
  • both end surfaces in the axial direction of the inner rings 21, 221, 321, 421 assembled to the outer rings 25, 225, 325, 425 are exposed, so the axial direction of the outer rings 25, 225, 325, 425 is exposed.
  • the inner rings 21, 221, 321, 421 can be attached from either side, and the fitting convex portions 22f, 221f, 423f and the fitting concave portions 323f, the fitting concave portions 26f, 225f, 425f, which are fitting concave and convex portions, and The misalignment of the inner rings 21, 221, 321, 421 and the outer rings 25, 225, 325, 425 is restricted by the fitting convex portion 326 f.
  • the shaft coupler 100 includes fitting projections 22f, 221f, 423f and fitting recesses 26f, 225f, 425f, which are fitting projections and depressions, in the axial direction of the inner rings 21, 221, 421 and the outer rings 25, 225, 425. The positional deviation of is controlled.
  • the shaft coupler 100 includes fitting recesses 323f and fitting projections 423f, and fitting projections 326f and fitting recesses 425f, which are fitting projections and depressions, in the radial direction of the inner rings 321 and 421 and the outer rings 325 and 425. Regulate misalignment.
  • the shape of the outer peripheral surface of the inner rings 21, 221, 321, 421 and the shape of the inner peripheral surface of the outer rings 25, 225, 325, 425 are the central axes of the couplings 20, 220, 320, 420. It is a rotationally symmetric shape centered on CA.
  • the degree of freedom in the alignment of the inner rings 21, 221, 321, 421 and the outer rings 25, 225, 325, 425 in the rotational direction can be improved, so the inner rings 21, 221, 321, 421 and the outer ring 25 , 225, 325, 425 can be improved.
  • the shaft coupler 100 includes coupling projections 22f, 221f, 423f and fitting recesses 323f, fitting recesses 26f, 225f, 425f, and fitting projections 326f, which are fitting projections and depressions, and couplings 20, 220, 320. , 420 are symmetrical with respect to the axial center plane CP.
  • the electric power steering apparatus 101 includes the shaft coupler 100, the first axis is the output shaft 7 a of the electric motor 7, and the second axis is the worm shaft 2.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Power Steering Mechanism (AREA)

Abstract

This shaft coupler 100 is provided with: a motor-side joint 8 connected to an output shaft 7a; a worm-side joint 6 connected to a worm shaft 2; and a coupling 20 provided between the motor-side joint 8 and the worm-side joint 6 and transmitting the rotational torque of the motor-side joint 8 to the worm-side joint 6. The coupling 20 has an inner ring 21 and an outer ring 25 which exposes the opposite axial end surfaces of the inner ring 21 and which covers the radially outer peripheral surface of the inner ring 21. The inner ring 21 and the outer ring 25 have different rigidity and are provided with a fitting protrusion 22f and a fitting recess 26f, which serve as fitting protrusion/recess sections which fit to each other to prevent positional displacement.

Description

電動パワーステアリング装置、及びそれに用いられる軸連結器Electric power steering device and shaft coupler used therefor
　本発明は、電動パワーステアリング装置、及びそれに用いられる軸連結器に関する。 The present invention relates to an electric power steering apparatus and a shaft coupler used therefor.
　一方の回転軸の回転を他方の回転軸に伝達するように、２つの回転軸の間に配置され、２つの回転軸を連結する電動パワーステアリング装置用の軸連結機構が知られている（ＪＰ２０１０－６００５２Ａ参照）。ＪＰ２０１０－６００５２Ａに記載の軸連結機構では、剛性の異なる２種類の回転伝達部材を重ね合わせたものを２つの回転軸の間に配置している。 There is known a shaft coupling mechanism for an electric power steering apparatus that is disposed between two rotation shafts so as to transmit the rotation of one rotation shaft to the other rotation shaft and couples the two rotation shafts (JP2010). See -60052A). In the shaft coupling mechanism described in JP2010-60052A, a combination of two types of rotation transmission members having different rigidity is disposed between two rotation shafts.
　一方の回転伝達部材６は、外側円筒状基部３３と、外側円筒状基部３３の外周面３４から径方向外方向に向かって伸びる複数の突部３６～４１と、外側円筒状基部３３の一方の端面４２に形成されていると共に軸対称に配置された一対の係合凹所４３とを有している。他方の回転伝達部材７は、内側円筒状基部５３と、内側円筒状基部５３の外周面５４から径方向外方向に向かって伸びる複数の突部５６～５９と、内側円筒状基部５３の外周面５４の一方の端部に軸対称に一体的に形成されていると共に径方向外方向に突出した一対の係合爪部６０とを有している。 One rotation transmission member 6 includes an outer cylindrical base 33, a plurality of protrusions 36 to 41 extending radially outward from the outer peripheral surface 34 of the outer cylindrical base 33, and one of the outer cylindrical base 33. It has a pair of engaging recesses 43 formed on the end face 42 and arranged symmetrically about the axis. The other rotation transmission member 7 includes an inner cylindrical base 53, a plurality of protrusions 56 to 59 extending radially outward from the outer peripheral surface 54 of the inner cylindrical base 53, and the outer peripheral surface of the inner cylindrical base 53. A pair of engaging claw portions 60 that are integrally formed in one end portion of 54 in an axially symmetrical manner and project outward in the radial direction.
　回転伝達部材６と回転伝達部材７とが重ねあわされると、回転伝達部材７の突部５６～５９は、回転伝達部材６の突部４１，４０，３８，３７に設けられた凹所４６に受容される。また、回転伝達部材７の係合爪部６０が回転伝達部材６の係合凹所４３に受容されて、貫通孔３２からの内側円筒状基部５３の軸方向の抜け出しが阻止されている。 When the rotation transmitting member 6 and the rotation transmitting member 7 are overlapped, the protrusions 56 to 59 of the rotation transmitting member 7 are inserted into the recesses 46 provided in the protrusions 41, 40, 38, and 37 of the rotation transmitting member 6. Accepted. Further, the engagement claw portion 60 of the rotation transmission member 7 is received in the engagement recess 43 of the rotation transmission member 6, and the axial removal of the inner cylindrical base portion 53 from the through hole 32 is prevented.
　ＪＰ２０１０－６００５２Ａに記載の軸連結機構では、回転伝達部材６の突部４１，４０，３８，３７における軸方向一端面に設けられた底部を有する凹所４６に、回転伝達部材７の突部５６～５９を取り付ける構成である。このため、ＪＰ２０１０－６００５２Ａの図１８に示すように、回転伝達部材６と回転伝達部材７を組み付ける際には、回転伝達部材６を図示左側から右側に向かって回転伝達部材７に取り付けることになり、取付方向が限定されている。このため、ＪＰ２０１０－６００５２Ａに記載の軸連結機構では、回転伝達部材６と回転伝達部材７との組付性に改善の余地がある。 In the shaft coupling mechanism described in JP2010-60052A, the protrusion 56 of the rotation transmission member 7 is provided in a recess 46 having a bottom portion provided on one end surface in the axial direction of the protrusions 41, 40, 38, and 37 of the rotation transmission member 6. To 59. Therefore, as shown in FIG. 18 of JP2010-60052A, when the rotation transmission member 6 and the rotation transmission member 7 are assembled, the rotation transmission member 6 is attached to the rotation transmission member 7 from the left side to the right side in the figure. The mounting direction is limited. For this reason, in the shaft coupling mechanism described in JP2010-60052A, there is room for improvement in the assembling property between the rotation transmission member 6 and the rotation transmission member 7.
　本発明は、内側リングと外側リングの位置ずれを防止するとともに内側リングと外側リングの組付性を向上することを目的とする。 The present invention aims to prevent misalignment of the inner ring and the outer ring and improve the assembling property of the inner ring and the outer ring.
　本発明のある態様によれば、軸連結器であって、第１軸に接続される第１ジョイントと、第２軸に接続される第２ジョイントと、第１ジョイントと第２ジョイントとの間に設けられるカップリングと、を備え、第１ジョイント及び第２ジョイントは、軸方向に延びる複数の突出部を有し、互いの突出部が周方向に交互に並ぶように配置され、カップリングは、第１ジョイント及び第２ジョイントの隣り合う突出部に挟まれて第１軸の回転トルクを第２軸に伝達するトルク伝達部を有し、カップリングは、内側リングと、内側リングの軸方向両端面を露出させ、内側リングの径方向外周面を覆う外側リングと、を有し、内側リングは、円筒状の内側円筒部と、内側円筒部の外周から径方向外方に放射状に延在する複数の内側腕部と、を有し、外側リングは、内側円筒部を覆う円筒状の外側円筒部と、外側円筒部の外周から径方向外方に放射状に延在し、内側腕部を覆う複数の外側腕部と、を有し、内側リング及び外側リングは、剛性が互いに異なり、トルク伝達部は、内側腕部と外側腕部とを有し、内側リング及び外側リングのそれぞれには、互いに嵌合することで位置ずれを規制する嵌合凹凸部が設けられている。 According to an aspect of the present invention, there is a shaft coupler, the first joint connected to the first shaft, the second joint connected to the second shaft, and between the first joint and the second joint. And the first joint and the second joint have a plurality of protrusions extending in the axial direction, the protrusions are arranged alternately in the circumferential direction, and the coupling is And a torque transmitting portion that is sandwiched between adjacent projecting portions of the first joint and the second joint and transmits the rotational torque of the first shaft to the second shaft, and the coupling includes an inner ring and an axial direction of the inner ring. An outer ring that exposes both end surfaces and covers the radially outer peripheral surface of the inner ring, and the inner ring extends radially outward from the outer periphery of the inner cylindrical portion and the inner cylindrical portion. A plurality of inner arms, The side ring includes a cylindrical outer cylindrical portion covering the inner cylindrical portion, and a plurality of outer arm portions extending radially outward from the outer periphery of the outer cylindrical portion and covering the inner arm portion, The inner ring and the outer ring are different in rigidity, and the torque transmission part has an inner arm part and an outer arm part, and each of the inner ring and the outer ring is engaged with each other to regulate displacement. A fitting uneven part is provided.
図１は、電動パワーステアリング装置の断面図である。FIG. 1 is a cross-sectional view of an electric power steering apparatus. 図２は、ウォーム側ジョイントとモータ側ジョイントの斜視図である。FIG. 2 is a perspective view of the worm side joint and the motor side joint. 図３（ａ）は本発明の第１実施形態に係るカップリングの平面図であり、図３（ｂ）は図３（ａ）のＩＩＩｂ－ＩＩＩｂ線に沿う断面図である。3A is a plan view of the coupling according to the first embodiment of the present invention, and FIG. 3B is a cross-sectional view taken along the line IIIb-IIIb in FIG. 3A. 図４は、軸連結器の軸方向中心面に沿う断面図である。FIG. 4 is a sectional view taken along the axial center plane of the shaft coupler. 図５（ａ）は本発明の第２実施形態に係るカップリングの平面図であり、図５（ｂ）は図５（ａ）のＶｂ－Ｖｂ線に沿う断面図である。図５（ｃ）は図５（ａ）のＶｃ－Ｖｃ線に沿う断面図である。FIG. 5A is a plan view of a coupling according to the second embodiment of the present invention, and FIG. 5B is a cross-sectional view taken along the line Vb-Vb in FIG. FIG. 5C is a cross-sectional view taken along the line Vc-Vc in FIG. 図６（ａ）は本発明の第３実施形態に係るカップリングの平面図であり、図６（ｂ）は図６（ａ）のＶＩｂ－ＶＩｂ線に沿う断面図である。図６（ｃ）は図６（ａ）のＶＩｃ－ＶＩｃ線に沿う断面図である。FIG. 6A is a plan view of the coupling according to the third embodiment of the present invention, and FIG. 6B is a cross-sectional view taken along the line VIb-VIb in FIG. FIG. 6C is a cross-sectional view taken along the line VIc-VIc in FIG. 図７（ａ）は本発明の第４実施形態に係るカップリングの平面図であり、図７（ｂ）は図７（ａ）のＶＩＩｂ－ＶＩＩｂ線に沿う断面図である。図７（ｃ）は図７（ａ）のＶＩＩｃ－ＶＩＩｃ線に沿う断面図である。FIG. 7A is a plan view of the coupling according to the fourth embodiment of the present invention, and FIG. 7B is a cross-sectional view taken along the line VIIb-VIIb in FIG. 7A. FIG. 7C is a cross-sectional view taken along the line VIIc-VIIc in FIG.
　以下、図面を参照して、本発明の実施形態について説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
　＜第１実施形態＞
　本発明の実施形態に係る軸連結器は、電動パワーステアリング装置におけるウォームシャフトと電動モータの出力シャフトとを連結する。 <First Embodiment>
The shaft coupler which concerns on embodiment of this invention connects the worm shaft in an electric power steering device, and the output shaft of an electric motor.
　図１を参照して、電動パワーステアリング装置１０１について説明する。 The electric power steering apparatus 101 will be described with reference to FIG.
　電動パワーステアリング装置１０１は、車両に搭載され、ドライバーが操舵ハンドルに加える操舵力を補助する装置である。 The electric power steering device 101 is a device that is mounted on the vehicle and assists the steering force applied by the driver to the steering wheel.
　電動パワーステアリング装置１０１は、操舵ハンドルに連係する操舵軸に設けられるウォームホイール１と、ウォームホイール１に噛み合うウォームシャフト２と、ウォームシャフト２と軸連結器１００を介して連結された電動モータ７と、を備える。電動モータ７の駆動に伴ってウォームシャフト２が回転し、ウォームシャフト２の回転が減速してウォームホイール１に伝達される。ウォームホイール１とウォームシャフト２にてウォーム減速機が構成される。 The electric power steering device 101 includes a worm wheel 1 provided on a steering shaft linked to a steering handle, a worm shaft 2 meshing with the worm wheel 1, and an electric motor 7 connected to the worm shaft 2 via a shaft coupler 100. . The worm shaft 2 rotates as the electric motor 7 is driven, and the rotation of the worm shaft 2 is decelerated and transmitted to the worm wheel 1. The worm wheel 1 and the worm shaft 2 constitute a worm speed reducer.
　軸連結器１００は、ウォームシャフト２と電動モータ７の出力シャフト７ａとを連結する。軸連結器１００については、後に詳細に説明する。 The shaft coupler 100 connects the worm shaft 2 and the output shaft 7 a of the electric motor 7. The shaft coupler 100 will be described in detail later.
　電動モータ７から出力されるトルクは、ウォームシャフト２からウォームホイール１に伝達されて操舵軸にアシストトルクとして付与される。電動モータ７が出力するトルクは、操舵軸を構成する入力軸と出力軸との相対回転によって捩れるトーションバーの捩れ量に基づいて演算される操舵トルクに対応する。 The torque output from the electric motor 7 is transmitted from the worm shaft 2 to the worm wheel 1 and applied to the steering shaft as assist torque. The torque output by the electric motor 7 corresponds to the steering torque calculated based on the torsion amount of the torsion bar that is twisted by the relative rotation between the input shaft and the output shaft constituting the steering shaft.
　ウォームシャフト２は金属製のギヤケース３に収容される。ウォームシャフト２の一部には、ウォームホイール１の歯部１ａと噛み合う歯部２ａが形成される。ギヤケース３の内周面には歯部２ａに対応する位置に開口部３ｃが形成され、その開口部３ｃを通じてウォームシャフト２の歯部２ａとウォームホイール１の歯部１ａとが噛み合う。なお、ギヤケース３は樹脂製であってもよい。 The worm shaft 2 is accommodated in a metal gear case 3. A part of the worm shaft 2 is formed with a tooth part 2 a that meshes with the tooth part 1 a of the worm wheel 1. An opening 3c is formed on the inner peripheral surface of the gear case 3 at a position corresponding to the tooth 2a, and the tooth 2a of the worm shaft 2 and the tooth 1a of the worm wheel 1 mesh with each other through the opening 3c. The gear case 3 may be made of resin.
　ウォームシャフト２の電動モータ７側である基端側は、第１軸受４によって回転自在に支持される。第１軸受４は、環状の内輪と外輪の間にボールが介在されている。第１軸受４の外輪は、ギヤケース３に形成された段部３ａとロックナット５との間で挟持される。第１軸受４の内輪は、ウォームシャフト２の段部２ｂとウォームシャフト２に接続されたウォーム側ジョイント６との間で挟持される。これにより、ウォームシャフト２の軸方向への移動が規制される。 The base end side which is the electric motor 7 side of the worm shaft 2 is rotatably supported by the first bearing 4. The first bearing 4 has a ball interposed between an annular inner ring and an outer ring. The outer ring of the first bearing 4 is sandwiched between a step 3 a formed in the gear case 3 and the lock nut 5. The inner ring of the first bearing 4 is sandwiched between the step 2 b of the worm shaft 2 and the worm side joint 6 connected to the worm shaft 2. Thereby, the movement to the axial direction of the worm shaft 2 is controlled.
　ギヤケース３の底部には、断面がＬ字状の環状の弾性部材としてのＬ字リング１０を介して第２軸受１１が収装される。ウォームシャフト２の先端側は第２軸受１１によって回転自在に支持される。第２軸受１１は、環状の内輪と外輪の間にボールが介在されている。第２軸受１１の内輪にはウォームシャフト２の先端部付近に形成された段部２ｃが係止される。 The second bearing 11 is housed on the bottom of the gear case 3 via an L-shaped ring 10 as an annular elastic member having an L-shaped cross section. The tip end side of the worm shaft 2 is rotatably supported by the second bearing 11. The second bearing 11 has a ball interposed between an annular inner ring and an outer ring. A step 2c formed near the tip of the worm shaft 2 is locked to the inner ring of the second bearing 11.
　第２軸受１１はＬ字リング１０の付勢力によってウォームシャフト２の段部２ｃに押し付けられるため、第２軸受１１の軸方向のガタつきが低減される。つまり、Ｌ字リング１０は、ギヤケース３の底部と第２軸受１１の底部との間にて圧縮され、第２軸受１１を軸方向に与圧している。 Since the second bearing 11 is pressed against the step 2c of the worm shaft 2 by the urging force of the L-shaped ring 10, the backlash in the axial direction of the second bearing 11 is reduced. That is, the L-shaped ring 10 is compressed between the bottom portion of the gear case 3 and the bottom portion of the second bearing 11 to pressurize the second bearing 11 in the axial direction.
　ギヤケース３の端部側の外周面には、端面１７ａが平面状のフランジ部１７が突出して形成される。フランジ部１７には、第２軸受１１の外周面に臨んで開口する貫通孔１３が形成される。フランジ部１７の端面１７ａに開口する貫通孔１３の開口部はプラグ１４によって閉塞される。 A flange portion 17 having a flat end surface 17a is formed on the outer peripheral surface of the gear case 3 on the end side. The flange portion 17 is formed with a through-hole 13 that opens toward the outer peripheral surface of the second bearing 11. The opening of the through hole 13 that opens to the end surface 17 a of the flange portion 17 is closed by the plug 14.
　貫通孔１３には、プラグ１４の先端面と第２軸受１１の外周面との間で圧縮された付勢部材としてのコイルスプリング１２が収装される。コイルスプリング１２は、ウォームシャフト２の歯部２ａとウォームホイール１の歯部１ａとの隙間が小さくなる方向に第２軸受１１を付勢する。つまり、コイルスプリング１２は、第２軸受１１を介してウォームシャフト２をウォームホイール１に向けて付勢する。 A coil spring 12 as an urging member compressed between the tip end surface of the plug 14 and the outer peripheral surface of the second bearing 11 is accommodated in the through hole 13. The coil spring 12 biases the second bearing 11 in a direction in which the gap between the tooth portion 2a of the worm shaft 2 and the tooth portion 1a of the worm wheel 1 is reduced. That is, the coil spring 12 biases the worm shaft 2 toward the worm wheel 1 via the second bearing 11.
　ギヤケース３における第２軸受１１の外周面を囲う内周面３ｂは、第２軸受１１がコイルスプリング１２の付勢力によってウォームホイール１に向けて移動できるように、互いに平行な一対の平面部を有する長穴形状に形成される。なお、内周面３ｂは、第２軸受１１が内周面３ｂの内側で移動できる限り、どのような形状であってもよい。たとえば、内周面３ｂは、その内径が第２軸受１１の外径よりも大きい丸穴形状であってもよく、互いに平行な一対の平面部が形成されている必要はない。 The inner peripheral surface 3 b surrounding the outer peripheral surface of the second bearing 11 in the gear case 3 has a pair of plane portions parallel to each other so that the second bearing 11 can move toward the worm wheel 1 by the biasing force of the coil spring 12. It is formed in a long hole shape. The inner peripheral surface 3b may have any shape as long as the second bearing 11 can move inside the inner peripheral surface 3b. For example, the inner peripheral surface 3b may have a round hole shape whose inner diameter is larger than the outer diameter of the second bearing 11, and it is not necessary to form a pair of plane portions parallel to each other.
　ギヤケース３内へのウォームシャフト２の組み付けが完了した初期時点では、第２軸受１１は、コイルスプリング１２の付勢力によってウォームホイール１側に付勢され、バックラッシュがない状態となる。この状態では、ウォームシャフト２は、コイルスプリング１２の付勢力によって第１軸受４を支点として傾き、ウォームシャフト２と電動モータ７の出力シャフト７ａとの軸がずれた状態となる。このウォームシャフト２と電動モータ７の出力シャフト７ａとの軸ずれは、軸連結器１００にて許容される。 When the assembly of the worm shaft 2 into the gear case 3 is completed, the second bearing 11 is urged toward the worm wheel 1 by the urging force of the coil spring 12, and there is no backlash. In this state, the worm shaft 2 is inclined with the first bearing 4 as a fulcrum by the urging force of the coil spring 12, and the worm shaft 2 and the output shaft 7 a of the electric motor 7 are out of alignment. Axial displacement between the worm shaft 2 and the output shaft 7 a of the electric motor 7 is allowed by the shaft coupler 100.
　電動パワーステアリング装置１０１の駆動に伴ってウォームシャフト２とウォームホイール１の歯部１ａ，２ａの摩耗が進めば、コイルスプリング１２の付勢力によって第２軸受１１がギヤケース３の長穴内を移動し、ウォームシャフト２とウォームホイール１との歯部１ａ，２ａのバックラッシュが低減される。したがって、バックラッシュが安定して低減されるためには、軸連結器１００によってウォームシャフト２と電動モータ７の出力シャフト７ａとの軸ずれが許容され、ウォームシャフト２が電動モータ７の出力シャフト７ａに対してスムーズに傾動することが必要となる。 If the wear of the worm shaft 2 and the tooth portions 1a, 2a of the worm wheel 1 is advanced as the electric power steering device 101 is driven, the second bearing 11 is moved in the elongated hole of the gear case 3 by the urging force of the coil spring 12. Backlash of the teeth 1a and 2a between the worm shaft 2 and the worm wheel 1 is reduced. Therefore, in order to stably reduce the backlash, the shaft coupler 100 allows the shaft misalignment between the worm shaft 2 and the output shaft 7a of the electric motor 7 so that the worm shaft 2 is used as the output shaft 7a of the electric motor 7. It is necessary to tilt smoothly.
　次に、主に図２～４を参照して、軸連結器１００について説明する。図２はウォーム側ジョイント６とモータ側ジョイント８の斜視図である。図３（ａ）はカップリング２０の平面図であり、図３（ｂ）は図３（ａ）のＩＩＩｂ－ＩＩＩｂ線に沿う断面図である。図４は軸連結器１００の軸方向中心面に沿う断面図である。 Next, the shaft coupler 100 will be described mainly with reference to FIGS. FIG. 2 is a perspective view of the worm side joint 6 and the motor side joint 8. 3A is a plan view of the coupling 20, and FIG. 3B is a cross-sectional view taken along the line IIIb-IIIb in FIG. 3A. FIG. 4 is a cross-sectional view along the axial center plane of the shaft coupler 100.
　図１に示すように、軸連結器１００は、電動モータ７の出力シャフト７ａに接続されるモータ側ジョイント８と、ウォームシャフト２に接続されるウォーム側ジョイント６と、モータ側ジョイント８とウォーム側ジョイント６との間に設けられ電動モータ７の出力シャフト７ａの回転トルクをウォームシャフト２に伝達するためのカップリング２０と、を備える。 As shown in FIG. 1, the shaft coupler 100 includes a motor side joint 8 connected to the output shaft 7 a of the electric motor 7, a worm side joint 6 connected to the worm shaft 2, a motor side joint 8 and the worm side. And a coupling 20 provided between the joint 6 and for transmitting the rotational torque of the output shaft 7a of the electric motor 7 to the worm shaft 2.
　図２に示すように、モータ側ジョイント８は、電動モータ７の出力シャフト７ａの先端側外周面に圧入される嵌合穴３１ａが形成された環状の基部３１と、基部３１の外周縁から突出して形成され軸方向に延びる複数の突出部３２と、を有する。モータ側ジョイント８は鉄鋼材料からなる。 As shown in FIG. 2, the motor-side joint 8 protrudes from an annular base 31 in which a fitting hole 31 a to be press-fitted into the outer peripheral surface of the output shaft 7 a of the electric motor 7 is formed, and from the outer peripheral edge of the base 31. And a plurality of protrusions 32 extending in the axial direction. The motor side joint 8 is made of a steel material.
　モータ側ジョイント８は、出力シャフト７ａの先端側外周面に嵌合穴３１ａを圧入することによって出力シャフト７ａに接続され、出力シャフト７ａに対する抜け止めと回り止めが図られる。出力シャフト７ａへのモータ側ジョイント８の接続方法は、圧入に限られず、出力シャフト７ａに対するモータ側ジョイント８の抜け止めと回り止めが実現されれば、他の方法を用いてもよい。 The motor side joint 8 is connected to the output shaft 7a by press-fitting the fitting hole 31a into the outer peripheral surface of the output shaft 7a, thereby preventing the output shaft 7a from coming off and rotating. The method for connecting the motor side joint 8 to the output shaft 7a is not limited to press-fitting, and other methods may be used as long as the motor side joint 8 is prevented from being detached and prevented from rotating with respect to the output shaft 7a.
　突出部３２は、周方向に等間隔に並んで４つ形成される。４つの突出部３２は、基部３１の中心軸を中心として略円弧形状に形成される。突出部３２の外周面は、略径方向に延びる一対の平面部３２ａを有する。 The four protrusions 32 are formed at equal intervals in the circumferential direction. The four protruding portions 32 are formed in a substantially arc shape with the central axis of the base portion 31 as the center. The outer peripheral surface of the protrusion part 32 has a pair of plane part 32a extended in a substantially radial direction.
　ウォーム側ジョイント６は、ウォームシャフト２の基端側外周面に圧入される嵌合穴４１ａが形成された環状の基部４１と、基部４１の外周縁から突出して形成され軸方向に延びる複数の突出部４２と、を有する。ウォーム側ジョイント６は鉄鋼材料からなる。 The worm side joint 6 has an annular base 41 formed with a fitting hole 41a to be press-fitted into the outer peripheral surface of the proximal end of the worm shaft 2, and a plurality of protrusions that protrude from the outer peripheral edge of the base 41 and extend in the axial direction. Part 42. The worm side joint 6 is made of a steel material.
　ウォーム側ジョイント６は、ウォームシャフト２の基端側外周面に嵌合穴４１ａを圧入することによってウォームシャフト２に接続され、ウォームシャフト２に対する抜け止めと回り止めが図られる。ウォーム側ジョイント６は、基部４１の端面４１ｂがウォームシャフト２の段部２ｄ及び第１軸受４の内輪に当接するまでウォームシャフト２の基端側外周面に圧入される（図１参照）。ウォームシャフト２へのウォーム側ジョイント６の接続方法は、モータ側ジョイント８と同様に圧入に限られない。 The worm side joint 6 is connected to the worm shaft 2 by press-fitting a fitting hole 41 a into the outer peripheral surface of the proximal end of the worm shaft 2, so that the worm side joint 6 is prevented from being detached and prevented from rotating. The worm side joint 6 is press-fitted into the proximal end side outer peripheral surface of the worm shaft 2 until the end surface 41b of the base portion 41 comes into contact with the stepped portion 2d of the worm shaft 2 and the inner ring of the first bearing 4 (see FIG. 1). The method for connecting the worm side joint 6 to the worm shaft 2 is not limited to press-fitting as with the motor side joint 8.
　突出部４２は、周方向に等間隔に並んで４つ形成される。４つの突出部４２は、基部４１の中心軸を中心として略円弧形状に形成される。突出部４２の外周面は、略径方向に延びる一対の平面部４２ａを有する。 The four protrusions 42 are formed at equal intervals in the circumferential direction. The four protruding portions 42 are formed in a substantially arc shape with the central axis of the base portion 41 as the center. The outer peripheral surface of the protrusion part 42 has a pair of plane part 42a extended in a substantially radial direction.
　モータ側ジョイント８とウォーム側ジョイント６は、同一形状であり、図４に示すように、互いの突出部３２，４２が周方向に交互に等間隔で並ぶように対向して配置される。 The motor side joint 8 and the worm side joint 6 have the same shape, and as shown in FIG. 4, the protrusions 32 and 42 are arranged to face each other so that they are alternately arranged at equal intervals in the circumferential direction.
　図３を参照して、カップリング２０について説明する。なお、カップリング２０の中心軸ＣＡは、後述する内側リング２１及び外側リング２５の中心軸と一致する。なお、軸方向とは、中心軸ＣＡに平行な方向である。 The coupling 20 will be described with reference to FIG. The center axis CA of the coupling 20 coincides with the center axes of the inner ring 21 and the outer ring 25 described later. The axial direction is a direction parallel to the central axis CA.
　図３（ａ）及び図３（ｂ）に示すように、カップリング２０は、内側リング２１と、内側リング２１の径方向外周面を覆う外側リング２５と、を有している。内側リング２１は、円筒状の内側円筒部２２と、矩形平板状の複数の内側腕部２３と、を有している。複数の内側腕部２３は、内側円筒部２２の外周から中心軸ＣＡを中心として径方向外方に放射状に延在している。本実施形態では、８つの内側腕部２３が周方向に等間隔（すなわち、４５度間隔）で配置されている。内側リング２１の外周面の形状は、中心軸ＣＡを中心とした回転対称形状を呈している。回転対称形状とは、対称軸である中心軸ＣＡの回りに一定の角度だけ回転移動させたときに、その形状が変わらない形状のことである。本実施形態に係る内側リング２１は、中心軸ＣＡの周りを（３６０／ｎ）度（ｎ＝８）回転させると、自らと重なる８回対称の形状を有している。 3 (a) and 3 (b), the coupling 20 includes an inner ring 21 and an outer ring 25 that covers the radially outer peripheral surface of the inner ring 21. The inner ring 21 has a cylindrical inner cylindrical portion 22 and a plurality of rectangular arm-shaped inner arm portions 23. The plurality of inner arm portions 23 extend radially outward from the outer periphery of the inner cylindrical portion 22 about the central axis CA. In the present embodiment, the eight inner arm portions 23 are arranged at equal intervals in the circumferential direction (that is, at intervals of 45 degrees). The shape of the outer peripheral surface of the inner ring 21 is a rotationally symmetric shape with the central axis CA as the center. A rotationally symmetric shape is a shape that does not change when it is rotated about a central axis CA, which is a symmetry axis, by a certain angle. The inner ring 21 according to the present embodiment has an eight-fold symmetrical shape that overlaps itself when rotated around the central axis CA by (360 / n) degrees (n = 8).
　外側リング２５は、円筒状の外側円筒部２６と、中空直方体形状の複数の外側腕部２７と、を有している。複数の外側腕部２７は、外側円筒部２６の外周から中心軸ＣＡを中心として径方向外方に放射状に延在している。外側円筒部２６は、内側円筒部２２の外側面全体を覆い、外側腕部２７は内側腕部２３の外側面全体を覆っている。外側腕部２７は内側腕部２３に対応して設けられている。本実施形態では、８つの外側腕部２７が周方向に等間隔（すなわち、４５度間隔）で配置されている。外側リング２５の内周面及び外周面の形状は、中心軸ＣＡを中心とした回転対称形状を呈している。本実施形態に係る外側リング２５は、中心軸ＣＡの周りを（３６０／ｎ）度（ｎ＝８）回転させると、自らと重なる８回対称の形状を有している。 The outer ring 25 includes a cylindrical outer cylindrical portion 26 and a plurality of outer arm portions 27 having a hollow rectangular parallelepiped shape. The plurality of outer arm portions 27 extend radially outward from the outer periphery of the outer cylindrical portion 26 about the central axis CA. The outer cylindrical portion 26 covers the entire outer surface of the inner cylindrical portion 22, and the outer arm portion 27 covers the entire outer surface of the inner arm portion 23. The outer arm portion 27 is provided corresponding to the inner arm portion 23. In the present embodiment, the eight outer arm portions 27 are arranged at equal intervals in the circumferential direction (that is, at intervals of 45 degrees). The shapes of the inner peripheral surface and the outer peripheral surface of the outer ring 25 are rotationally symmetric with respect to the central axis CA. The outer ring 25 according to the present embodiment has an eight-fold symmetrical shape that overlaps itself when rotated around the central axis CA by (360 / n) degrees (n = 8).
　外側円筒部２６は、軸方向に貫通する円形状の貫通孔２６ｈを有し、外側腕部２７は軸方向に貫通する矩形状の貫通孔２７ｈを有している。貫通孔２６ｈ及び貫通孔２７ｈは連通しており、内側リング２１が挿入される開口部２５ｈを形成している。内側円筒部２２、内側腕部２３、外側円筒部２６、及び外側腕部２７の軸方向寸法は同じである。内側リング２１の軸方向端面と外側リング２５の軸方向端面とは面一とされ、内側リング２１の軸方向両端面は、それぞれ外側リング２５の開口部２５ｈから露出している。 The outer cylindrical portion 26 has a circular through hole 26h penetrating in the axial direction, and the outer arm portion 27 has a rectangular through hole 27h penetrating in the axial direction. The through hole 26h and the through hole 27h are in communication with each other and form an opening 25h into which the inner ring 21 is inserted. The axial dimensions of the inner cylindrical portion 22, the inner arm portion 23, the outer cylindrical portion 26, and the outer arm portion 27 are the same. The axial end surface of the inner ring 21 and the axial end surface of the outer ring 25 are flush with each other, and both axial end surfaces of the inner ring 21 are exposed from the opening 25h of the outer ring 25, respectively.
　図４に示すように、内側リング２１が外側リング２５に組み付けられると、内側腕部２３と外側腕部２７とが重ねられ、周方向で積層構造となるトルク伝達部５１が形成される。トルク伝達部５１は、モータ側ジョイント８及びウォーム側ジョイント６の隣り合う突出部３２，４２の平面部３２ａと平面部４２ａに挟まれて、電動モータ７の回転トルクをウォームシャフト２に伝達する。 As shown in FIG. 4, when the inner ring 21 is assembled to the outer ring 25, the inner arm portion 23 and the outer arm portion 27 are overlapped to form a torque transmission portion 51 having a laminated structure in the circumferential direction. The torque transmission unit 51 is sandwiched between the planar portions 32 a and the planar portions 42 a of the adjacent projecting portions 32 and 42 of the motor side joint 8 and the worm side joint 6, and transmits the rotational torque of the electric motor 7 to the worm shaft 2.
　トルク伝達部５１は、隣り合う突出部３２，４２の隙間に嵌るように、略径方向に延びている。複数のトルク伝達部５１は、電動モータ７の出力シャフト７ａを中心として放射状に配置される。これにより、電動モータ７の回転トルクは、モータ側ジョイント８の突出部３２からトルク伝達部５１を通じてウォーム側ジョイント６の突出部４２に伝達され、ウォームシャフト２に伝達されることになる。 The torque transmission part 51 is extended in the substantially radial direction so that it may fit in the clearance gap between the adjacent protrusion parts 32 and 42. As shown in FIG. The plurality of torque transmission parts 51 are arranged radially around the output shaft 7 a of the electric motor 7. Thereby, the rotational torque of the electric motor 7 is transmitted from the projecting portion 32 of the motor side joint 8 to the projecting portion 42 of the worm side joint 6 through the torque transmitting portion 51 and is transmitted to the worm shaft 2.
　内側リング２１及び外側リング２５は、剛性が互いに異なる。本実施形態では、内側リング２１が、相対的に剛性の小さい（すなわち、ヤング率が小さい）柔軟性のあるゴムにより形成され、外側リング２５が、相対的に剛性の大きい（すなわち、ヤング率が大きい）樹脂により形成される。 The inner ring 21 and the outer ring 25 have different rigidity. In the present embodiment, the inner ring 21 is formed of a flexible rubber having a relatively low rigidity (that is, a small Young's modulus), and the outer ring 25 is relatively rigid (that is, a Young's modulus is small). Large) resin.
　外側リング２５が内側リング２１の外周面を覆っているので、トルク伝達部５１は周方向にゴムを樹脂で挟んだ３層構造となる。このように、トルク伝達部５１を剛性の異なる２種類の材料で構成することにより、剛性と柔軟性を兼ね備えた特性とすることができる。したがって、カップリング２０は、電動モータ７の回転トルクをウォームシャフト２へ効率良く伝達する共に、ウォームシャフト２と電動モータ７の出力シャフト７ａとの軸ずれを許容するように機能する。 Since the outer ring 25 covers the outer peripheral surface of the inner ring 21, the torque transmitting portion 51 has a three-layer structure in which rubber is sandwiched between resins in the circumferential direction. In this way, by configuring the torque transmitting portion 51 with two types of materials having different rigidity, it is possible to obtain characteristics having both rigidity and flexibility. Therefore, the coupling 20 functions to efficiently transmit the rotational torque of the electric motor 7 to the worm shaft 2 and to allow an axial deviation between the worm shaft 2 and the output shaft 7 a of the electric motor 7.
　しかし、内側リング２１と外側リング２５との間に位置ずれが発生すると、両者の接触面積が減少し、剛性特性が変化して、トルクの伝達性能が低下するおそれがある。位置ずれにより、図３に示す内側腕部２３の先端角部と外側腕部２７の貫通孔２７ｈの内周面とのエッジ当たりや、外側円筒部２６の開口部２５ｈの縁と、内側円筒部２２の外周面とのエッジ当たりが発生してしまうおそれもある。このように、内側リング２１と外側リング２５の位置ずれは、カップリング２０の剛性特性の変化、磨耗及び破損の原因となり得る。 However, if a displacement occurs between the inner ring 21 and the outer ring 25, the contact area between the two decreases, the rigidity characteristics change, and the torque transmission performance may be reduced. Due to the positional deviation, the edge contact between the tip corner of the inner arm 23 and the inner peripheral surface of the through hole 27h of the outer arm 27 shown in FIG. 3, the edge of the opening 25h of the outer cylindrical portion 26, and the inner cylindrical portion There is also a possibility that edge contact with the outer peripheral surface of 22 occurs. As described above, misalignment between the inner ring 21 and the outer ring 25 may cause a change in rigidity characteristics, wear, and breakage of the coupling 20.
　そこで、本実施形態では、内側リング２１及び外側リング２５の位置ずれを規制する嵌合凹凸部を内側リング２１及び外側リング２５に設けている。以下、嵌合凹凸部について詳しく説明する。 Therefore, in the present embodiment, fitting uneven portions for restricting the positional deviation of the inner ring 21 and the outer ring 25 are provided in the inner ring 21 and the outer ring 25. Hereinafter, the fitting uneven portion will be described in detail.
　図３（ａ）及び図３（ｂ）に示すように、隣り合う内側腕部２３間の内側円筒部２２の外周面には、径方向外方に突出する嵌合凸部２２ｆが設けられている。嵌合凸部２２ｆは直方体形状である。本実施形態では、８つの嵌合凸部２２ｆが設けられている。嵌合凸部２２ｆは、内側リング２１の軸方向中心部において、カップリング２０の軸方向中心面ＣＰに対して面対称に形成されている。カップリング２０の軸方向中心面ＣＰとは、カップリング２０の軸方向の中心に位置する平面であって、中心軸ＣＡに直交する平面である。カップリング２０の軸方向中心面ＣＰは、内側リング２１及び外側リング２５の軸方向中心面と一致する。 As shown in FIGS. 3A and 3B, the outer peripheral surface of the inner cylindrical portion 22 between the adjacent inner arm portions 23 is provided with a fitting convex portion 22f protruding radially outward. Yes. The fitting convex portion 22f has a rectangular parallelepiped shape. In the present embodiment, eight fitting convex portions 22f are provided. The fitting protrusion 22 f is formed symmetrically with respect to the axial center plane CP of the coupling 20 at the axial center of the inner ring 21. The axial center plane CP of the coupling 20 is a plane located at the axial center of the coupling 20 and is a plane orthogonal to the central axis CA. The axial center plane CP of the coupling 20 coincides with the axial center planes of the inner ring 21 and the outer ring 25.
　隣り合う外側腕部２７間の外側円筒部２６の内周面には、径方向外方に窪む嵌合凹部２６ｆが設けられている。本実施形態では、８つの嵌合凹部２６ｆが設けられている。嵌合凹部２６ｆは、外側リング２５の軸方向中心部において、カップリング２０の軸方向中心面ＣＰに対して面対称に形成されている。 On the inner peripheral surface of the outer cylindrical portion 26 between the adjacent outer arm portions 27, a fitting recess 26f that is recessed radially outward is provided. In the present embodiment, eight fitting recesses 26f are provided. The fitting recess 26 f is formed symmetrically with respect to the axial center plane CP of the coupling 20 at the axial center of the outer ring 25.
　嵌合凸部２２ｆが嵌合凹部２６ｆに嵌入された状態では、図３（ｂ）に示すように、嵌合凸部２２ｆの軸方向両端面が、嵌合凹部２６ｆの軸方向両端面に当接する。このため、嵌合凸部２２ｆ及び嵌合凹部２６ｆが互いに嵌合することで、内側リング２１及び外側リング２５の軸方向の位置ずれが規制される。 In a state in which the fitting convex portion 22f is fitted in the fitting concave portion 26f, as shown in FIG. 3B, both axial end surfaces of the fitting convex portion 22f are in contact with both axial end surfaces of the fitting concave portion 26f. Touch. For this reason, when the fitting convex part 22f and the fitting concave part 26f fit each other, the positional deviation of the inner ring 21 and the outer ring 25 in the axial direction is restricted.
　図１に示すように、電動モータ７の出力シャフト７ａは、モータ側ジョイント８の嵌合穴３１ａに強固に固定するために嵌合穴３１ａの全長に亘って圧入され、出力シャフト７ａの先端部が嵌合穴３１ａから突出している。同様に、ウォームシャフト２は、ウォーム側ジョイント６の嵌合穴４１ａに強固に固定するために嵌合穴４１ａの全長に亘って圧入され、ウォームシャフト２の先端部が嵌合穴４１ａから突出している。 As shown in FIG. 1, the output shaft 7a of the electric motor 7 is press-fitted over the entire length of the fitting hole 31a in order to be firmly fixed to the fitting hole 31a of the motor side joint 8, and the tip of the output shaft 7a. Protrudes from the fitting hole 31a. Similarly, the worm shaft 2 is press-fitted over the entire length of the fitting hole 41a in order to be firmly fixed to the fitting hole 41a of the worm side joint 6, and the tip of the worm shaft 2 protrudes from the fitting hole 41a. Yes.
　図３（ａ）及び図３（ｂ）に示すように、内側円筒部２２は、軸方向に貫通する円形状の貫通孔２２ｈを有している。貫通孔２２ｈは、出力シャフト７ａ及びウォームシャフト２と干渉しないように、出力シャフト７ａ及びウォームシャフト２の外径よりも大きい内径を有している。換言すれば、内側円筒部２２の貫通孔２２ｈの内周面と、出力シャフト７ａとの間には所定長さの隙間９０ａが形成される。同様に、内側円筒部２２の貫通孔２２ｈの内周面と、ウォームシャフト２との間には所定長さの隙間９０ｂが形成される。 As shown in FIGS. 3A and 3B, the inner cylindrical portion 22 has a circular through hole 22h penetrating in the axial direction. The through hole 22h has an inner diameter larger than the outer diameter of the output shaft 7a and the worm shaft 2 so as not to interfere with the output shaft 7a and the worm shaft 2. In other words, a gap 90a having a predetermined length is formed between the inner peripheral surface of the through hole 22h of the inner cylindrical portion 22 and the output shaft 7a. Similarly, a gap 90 b having a predetermined length is formed between the inner peripheral surface of the through hole 22 h of the inner cylindrical portion 22 and the worm shaft 2.
　なお、隙間９０ａ，９０ｂの径方向長さが、図３に示す嵌合凸部２２ｆの突出高さ寸法（径方向の突出長さ）よりも大きい場合であって、内側リング２１が外側リング２５に対して径方向にずれしてしまったときには、嵌合凸部２２ｆが嵌合凹部２６ｆから脱落してしまうおそれがある。このため、本実施形態では、隙間９０ａ，９０ｂの径方向長さが嵌合凸部２２ｆの突出高さ寸法よりも小さくなるように、内側円筒部２２の貫通孔２２ｈの径が設定されている。隙間９０ａ，９０ｂの径方向長さを嵌合凸部２２ｆの突出高さ寸法よりも小さく設定し、内側リング２１の径方向の移動量を規制することにより、内側リング２１及び外側リング２５の径方向の位置ずれが規制される。 Note that the radial lengths of the gaps 90a and 90b are larger than the protruding height dimension (radially protruding length) of the fitting convex portion 22f shown in FIG. However, when it is displaced in the radial direction, the fitting convex portion 22f may fall off the fitting concave portion 26f. For this reason, in the present embodiment, the diameter of the through hole 22h of the inner cylindrical portion 22 is set so that the radial lengths of the gaps 90a and 90b are smaller than the protruding height dimension of the fitting convex portion 22f. . The diameters of the inner ring 21 and the outer ring 25 are set by setting the radial lengths of the gaps 90a and 90b to be smaller than the protruding height dimension of the fitting convex portion 22f and restricting the amount of movement of the inner ring 21 in the radial direction. Directional misregistration is regulated.
　軸連結器１００の組み立て手順について説明する。外側リング２５及び内側リング２１は、予めモールド成形により個別に作製される。 The assembly procedure of the shaft coupler 100 will be described. The outer ring 25 and the inner ring 21 are individually manufactured in advance by molding.
　外側リング２５の開口部２５ｈに内側リング２１を挿入する。内側リング２１の軸方向両端面と、外側リング２５の両端面のそれぞれが面一となるまで、内側リング２１を外側リング２５の開口部２５ｈに挿入する。内側リング２１は、外側リング２５の軸方向一端側から挿入してもよいし、外側リング２５の軸方向他端側から挿入してもよい。 The inner ring 21 is inserted into the opening 25h of the outer ring 25. The inner ring 21 is inserted into the opening 25 h of the outer ring 25 until both axial end surfaces of the inner ring 21 and both end surfaces of the outer ring 25 are flush with each other. The inner ring 21 may be inserted from one axial end side of the outer ring 25 or may be inserted from the other axial end side of the outer ring 25.
　内側リング２１を外側リング２５の開口部２５ｈに挿入する過程において、内側円筒部２２を中心軸ＣＡ側に弾性変形させることで、嵌合凸部２２ｆを外側リング２５の貫通孔２６ｈに挿入することができる。内側リング２１の端面と外側リング２５の端面とが一致するまで、内側リング２１を外側リング２５の開口部２５ｈに挿入させた後、内側円筒部２２の内側を径方向外方に押圧し、嵌合凸部２２ｆを嵌合凹部２６ｆに嵌め込む。これにより、内側リング２１と外側リング２５の組み付けが完了し、カップリング２０が完成する。 In the process of inserting the inner ring 21 into the opening 25 h of the outer ring 25, the fitting convex portion 22 f is inserted into the through hole 26 h of the outer ring 25 by elastically deforming the inner cylindrical portion 22 toward the central axis CA. Can do. The inner ring 21 is inserted into the opening 25h of the outer ring 25 until the end surface of the inner ring 21 and the end surface of the outer ring 25 coincide with each other, and then the inner side of the inner cylindrical portion 22 is pressed outward in the radial direction. The mating convex portion 22f is fitted into the fitting concave portion 26f. Thereby, the assembly of the inner ring 21 and the outer ring 25 is completed, and the coupling 20 is completed.
　モータ側ジョイント８の嵌合穴３１ａを電動モータ７の出力シャフト７ａの先端側外周面に圧入することによって、モータ側ジョイント８を出力シャフト７ａに接続する。ウォーム側ジョイント６の嵌合穴４１ａをウォームシャフト２の基端側外周面に圧入することによって、ウォーム側ジョイント６をウォームシャフト２に接続する。 The motor side joint 8 is connected to the output shaft 7a by press-fitting the fitting hole 31a of the motor side joint 8 into the outer peripheral surface on the tip side of the output shaft 7a of the electric motor 7. The worm side joint 6 is connected to the worm shaft 2 by press-fitting the fitting hole 41 a of the worm side joint 6 into the base end side outer peripheral surface of the worm shaft 2.
　カップリング２０をモータ側ジョイント８及びウォーム側ジョイント６の一方に取り付けてから、ウォームシャフト２と電動モータ７の出力シャフト７ａとを連結する。たとえば、カップリング２０をモータ側ジョイント８の各突出部３２に嵌める。各突出部３２の一対の平面部３２ａのうちの一方にカップリング２０の各トルク伝達部５１を接触させておく。ウォーム側ジョイント６の各突出部４２が隣り合うトルク伝達部５１の間の隙間に挿入されるように、ギヤケース３と電動モータ７とを接続する。これにより、カップリング２０のトルク伝達部５１は、モータ側ジョイント８及びウォーム側ジョイント６の隣り合う突出部３２，４２に挟まれた状態となる（図４に示す状態）。 After attaching the coupling 20 to one of the motor side joint 8 and the worm side joint 6, the worm shaft 2 and the output shaft 7a of the electric motor 7 are connected. For example, the coupling 20 is fitted to each protrusion 32 of the motor side joint 8. Each torque transmitting portion 51 of the coupling 20 is brought into contact with one of the pair of flat surface portions 32a of each protruding portion 32. The gear case 3 and the electric motor 7 are connected so that each protrusion 42 of the worm side joint 6 is inserted into a gap between the adjacent torque transmission parts 51. Thereby, the torque transmission part 51 of the coupling 20 will be in the state pinched | interposed into the adjacent protrusion parts 32 and 42 of the motor side joint 8 and the worm side joint 6 (state shown in FIG. 4).
　以上のようにして、ウォームシャフト２と電動モータ７の出力シャフト７ａとが軸連結器１００を介して連結される。 As described above, the worm shaft 2 and the output shaft 7 a of the electric motor 7 are connected via the shaft coupler 100.
　なお、カップリング２０をモータ側ジョイント８及びウォーム側ジョイント６のいずれに先に組み付けるかは、ウォームシャフト２と電動モータ７の組み上げる順番によらない。つまり、電動モータ７を先に組み上げる場合に、カップリング２０をモータ側ジョイント８に先に組み付けておいてもよいし、後に組み上げたウォームシャフト２のウォーム側ジョイント６に先にカップリング２０を組み付けてからウォームシャフト２と電動モータ７の出力シャフト７ａとを連結してもよい。また、ウォームシャフト２を先に組み上げる場合に、カップリング２０をウォーム側ジョイント６に先に組み付けておいてもよいし、後に組み上げた電動モータ７のモータ側ジョイント８に先にカップリング２０を組み付けてからウォームシャフト２と電動モータ７の出力シャフト７ａとを連結してもよい。 Note that whether the coupling 20 is assembled first to the motor side joint 8 or the worm side joint 6 does not depend on the order in which the worm shaft 2 and the electric motor 7 are assembled. That is, when the electric motor 7 is assembled first, the coupling 20 may be assembled to the motor side joint 8 first, or the coupling 20 is assembled to the worm side joint 6 of the worm shaft 2 assembled later. After that, the worm shaft 2 and the output shaft 7a of the electric motor 7 may be connected. Further, when the worm shaft 2 is assembled first, the coupling 20 may be assembled to the worm side joint 6 first, or the coupling 20 is assembled to the motor side joint 8 of the electric motor 7 assembled later. After that, the worm shaft 2 and the output shaft 7a of the electric motor 7 may be connected.
　上述した実施の形態によれば、次の作用効果が得られる。 According to the embodiment described above, the following operational effects can be obtained.
　（１）カップリング２０は、内側リング２１と、内側リング２１の軸方向両端面を露出させ、内側リング２１の径方向外周面を覆う外側リング２５と、を有している。外側リング２５に組み付けられた内側リング２１の軸方向両端面が露出する構成であるので、外側リング２５の軸方向両側のいずれからでも内側リング２１を取り付けることができる。つまり、取付方向の自由度が高く、内側リング２１と外側リング２５の組付性を向上できる。 (1) The coupling 20 includes an inner ring 21 and an outer ring 25 that exposes both axial end surfaces of the inner ring 21 and covers the radially outer peripheral surface of the inner ring 21. Since both end surfaces in the axial direction of the inner ring 21 assembled to the outer ring 25 are exposed, the inner ring 21 can be attached from either side of the outer ring 25 in the axial direction. That is, the degree of freedom in the mounting direction is high, and the assemblability of the inner ring 21 and the outer ring 25 can be improved.
　（２）内側リング２１及び外側リング２５は、剛性が互いに異なる。このため、内側腕部２３と外側腕部２７とで構成されるトルク伝達部５１の剛性特性の最適化を図ることができ、電動モータ７の回転トルクをウォームシャフト２へ効率良く伝達すると共に、ウォームシャフト２と電動モータ７の出力シャフト７ａとの軸ずれを許容できる。 (2) The inner ring 21 and the outer ring 25 have different rigidity. For this reason, it is possible to optimize the rigidity characteristics of the torque transmission unit 51 constituted by the inner arm part 23 and the outer arm part 27, and efficiently transmit the rotational torque of the electric motor 7 to the worm shaft 2, An axial deviation between the worm shaft 2 and the output shaft 7a of the electric motor 7 can be allowed.
　（３）内側リング２１及び外側リング２５のそれぞれには、互いに嵌合することで位置ずれを規制する嵌合凹凸部が設けられている。本実施形態では、嵌合凹凸部として、内側リング２１に嵌合凸部２２ｆが設けられ、外側リング２５に嵌合凹部２６ｆが設けられている。嵌合凸部２２ｆと嵌合凹部２６ｆとが互いに嵌合することにより、内側リング２１及び外側リング２５の軸方向の位置ずれが規制される。 (3) Each of the inner ring 21 and the outer ring 25 is provided with a fitting uneven portion that regulates the displacement by fitting with each other. In the present embodiment, the fitting protrusion 22f is provided on the inner ring 21 and the fitting recess 26f is provided on the outer ring 25 as the fitting irregularities. When the fitting convex portion 22f and the fitting concave portion 26f are fitted to each other, the axial displacement of the inner ring 21 and the outer ring 25 is restricted.
　内側リング２１及び外側リング２５の位置ずれを抑制できるので、トルク伝達部５１の剛性特性の変化を抑制でき、トルク伝達の効率低下を防止することができる。さらに、位置ずれを起因とした、カップリング２０の磨耗や破損を防止することもできる。 Since the displacement of the inner ring 21 and the outer ring 25 can be suppressed, a change in the rigidity characteristic of the torque transmission part 51 can be suppressed, and a decrease in torque transmission efficiency can be prevented. Furthermore, it is possible to prevent the coupling 20 from being worn or damaged due to misalignment.
　（４）内側リング２１の外周面（嵌合凸部２２ｆを含む外周面）の形状及び外側リング２５の内周面（嵌合凹部２６ｆを含む外周面）の形状は、カップリング２０の中心軸ＣＡを中心とした回転対称形状である。本実施形態では、隣り合うトルク伝達部５１の間の計８箇所の全てに、嵌合凸部２２ｆと嵌合凹部２６ｆが設けられている。このように、内側腕部２３及び外側腕部２７、並びに嵌合凸部２２ｆ及び嵌合凹部２６ｆが、中心軸ＣＡに対して位相が均等に割り振られるように配置されている。これにより、周方向に特定の位相でなくても内側リング２１と外側リング２５の組み付けが可能となる。たとえば、内側腕部２３と外側腕部２７の位相が１ピッチずれた状態でも組み付けが可能となる。本実施形態によれば、内側リング２１と外側リング２５の回転方向の位置合わせの自由度を向上できるので、内側リング２１と外側リング２５の組付性を向上できる。 (4) The shape of the outer peripheral surface of the inner ring 21 (the outer peripheral surface including the fitting convex portion 22f) and the shape of the inner peripheral surface of the outer ring 25 (the outer peripheral surface including the fitting concave portion 26f) are the central axis of the coupling 20 It is a rotationally symmetric shape centered on CA. In this embodiment, the fitting convex part 22f and the fitting concave part 26f are provided in all eight places between the adjacent torque transmission parts 51 in total. In this way, the inner arm portion 23 and the outer arm portion 27, and the fitting convex portion 22f and the fitting concave portion 26f are arranged so that the phases are evenly allocated to the central axis CA. Thereby, the inner ring 21 and the outer ring 25 can be assembled even if the phase is not a specific phase in the circumferential direction. For example, assembly is possible even when the phases of the inner arm portion 23 and the outer arm portion 27 are shifted by one pitch. According to this embodiment, since the freedom degree of the alignment of the rotation direction of the inner side ring 21 and the outer side ring 25 can be improved, the assembly property of the inner side ring 21 and the outer side ring 25 can be improved.
　（５）嵌合凸部２２ｆ及び嵌合凹部２６ｆは、カップリング２０の軸方向中心面ＣＰに対して面対称に形成されている。これにより、内側リング２１を外側リング２５の開口部２５ｈに挿入する際、内側リング２１の軸方向両端のいずれから挿入しても内側リング２１を外側リング２５に組み付けることができる。つまり、内側リング２１及び外側リング２５の裏表の組み合わせに関係なく組み付けが可能である。内側リング２１を外側リング２５の開口部２５ｈに挿入する際の内側リング２１の向きの自由度が高いため、内側リング２１と外側リング２５の組付性を向上できる。 (5) The fitting convex portion 22f and the fitting concave portion 26f are formed symmetrically with respect to the axial center plane CP of the coupling 20. Accordingly, when the inner ring 21 is inserted into the opening 25 h of the outer ring 25, the inner ring 21 can be assembled to the outer ring 25 regardless of whether the inner ring 21 is inserted from both axial ends. That is, the inner ring 21 and the outer ring 25 can be assembled regardless of the combination of the front and back sides. Since the degree of freedom of the orientation of the inner ring 21 when inserting the inner ring 21 into the opening 25h of the outer ring 25 is high, the assembling property of the inner ring 21 and the outer ring 25 can be improved.
　（６）内側円筒部２２の貫通孔２２ｈの内周面と出力シャフト７ａとの隙間９０ａ、及び、貫通孔２２ｈの内周面とウォームシャフト２との隙間９０ｂの径方向長さは、それぞれ嵌合凸部２２ｆの突出高さ寸法よりも小さい。これにより、出力シャフト７ａ及びウォームシャフト２によって、外側リング２５に対する内側リング２１の径方向の位置ずれを規制することができる。 (6) The radial lengths of the gap 90a between the inner peripheral surface of the through hole 22h of the inner cylindrical portion 22 and the output shaft 7a and the gap 90b between the inner peripheral surface of the through hole 22h and the worm shaft 2 are respectively fitted. It is smaller than the protrusion height dimension of the joint protrusion 22f. Thereby, the radial displacement of the inner ring 21 with respect to the outer ring 25 can be regulated by the output shaft 7 a and the worm shaft 2.
　（７）このように、剛性特性の変化の少ないカップリング２０を用いることで、長期に亘って性能を維持できる電動パワーステアリング装置１０１を提供できる。 (7) Thus, by using the coupling 20 with little change in rigidity characteristics, the electric power steering apparatus 101 that can maintain the performance over a long period of time can be provided.
　＜第２実施形態＞
　図５を参照して、本発明の第２実施形態に係る軸連結器のカップリング２２０について説明する。以下では、上記第１実施形態と異なる点を中心に説明し、図中、上記第１実施形態で説明した構成と同一の構成または相当する構成には同一の符号を付して説明を省略する。 Second Embodiment
With reference to FIG. 5, the coupling 220 of the shaft coupler which concerns on 2nd Embodiment of this invention is demonstrated. The following description will focus on differences from the first embodiment, and in the figure, the same or corresponding components as those described in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted. .
　図５（ａ）はカップリング２２０の平面図であり、図５（ｂ）は図５（ａ）のＶｂ－Ｖｂ線に沿う断面図である。図５（ｃ）は図５（ａ）のＶｃ－Ｖｃ線に沿う断面図である。第１実施形態では、嵌合凹凸部（嵌合凸部２２ｆ、嵌合凹部２６ｆ）が、周方向に等間隔で複数箇所に設けられていた。これに対して、第２実施形態では、内側リング２２１の外周面と外側リング２２５の内周面の全周に亘って、嵌合凹凸部（嵌合凸部２２１ｆ，嵌合凹部２２５ｆ）が設けられている。以下、カップリング２２０について詳しく説明する。なお、第２実施形態の電動パワーステアリング装置におけるカップリング２２０以外の構成は、第１実施形態と同様であるので説明を省略する。 5A is a plan view of the coupling 220, and FIG. 5B is a cross-sectional view taken along the line Vb-Vb of FIG. 5A. FIG. 5C is a cross-sectional view taken along the line Vc-Vc in FIG. In 1st Embodiment, the fitting uneven | corrugated part (fitting convex part 22f, the fitting recessed part 26f) was provided in the multiple places at equal intervals in the circumferential direction. On the other hand, in the second embodiment, fitting concave and convex portions (fitting convex portions 221f and fitting concave portions 225f) are provided over the entire circumference of the outer peripheral surface of the inner ring 221 and the inner peripheral surface of the outer ring 225. It has been. Hereinafter, the coupling 220 will be described in detail. In addition, since structures other than the coupling 220 in the electric power steering apparatus of the second embodiment are the same as those of the first embodiment, description thereof is omitted.
　内側円筒部２２２には、外周面から外方に所定長さだけ突出した嵌合凸部２２２ｆが設けられている。内側腕部２２３には、外周面から外方に所定長さだけ突出した嵌合凸部２２３ｆが設けられている。嵌合凸部２２２ｆと嵌合凸部２２３ｆとは連続しており、内側リング２２１の外周に沿う環状の嵌合凸部２２１ｆを構成している。 The inner cylindrical portion 222 is provided with a fitting convex portion 222f that protrudes outward from the outer peripheral surface by a predetermined length. The inner arm portion 223 is provided with a fitting convex portion 223f that protrudes outward from the outer peripheral surface by a predetermined length. The fitting convex portion 222f and the fitting convex portion 223f are continuous, and constitute an annular fitting convex portion 221f along the outer periphery of the inner ring 221.
　外側円筒部２２６には、内周面から外方に所定長さだけ窪んだ嵌合凹部２２６ｆが設けられている。外側腕部２２７には、内周面から外方に所定長さだけ窪んだ嵌合凹部２２７ｆが設けられている。嵌合凹部２２６ｆと嵌合凹部２２７ｆとは連続しており、外側リング２２５の内周に沿う環状の嵌合凹部２２５ｆを構成している。 The outer cylindrical portion 226 is provided with a fitting concave portion 226f that is recessed by a predetermined length outward from the inner peripheral surface. The outer arm portion 227 is provided with a fitting recess 227f that is recessed by a predetermined length outward from the inner peripheral surface. The fitting recess 226f and the fitting recess 227f are continuous, and form an annular fitting recess 225f along the inner periphery of the outer ring 225.
　このような第２実施形態によれば、第１実施形態と同様の作用効果に加え、次の作用効果を奏する。 According to such a second embodiment, in addition to the same functions and effects as those of the first embodiment, the following functions and effects are achieved.
　（８）嵌合凹凸部を内側リング２２１及び外側リング２２５の当接面の全周に亘って設けることにより、嵌合凸部２２１ｆと嵌合凹部２２５ｆの接触面積を大きくできるので、軸方向の位置ずれの抑制効果を高めることができる。 (8) By providing the fitting uneven part over the entire circumference of the contact surface of the inner ring 221 and the outer ring 225, the contact area between the fitting convex part 221f and the fitting concave part 225f can be increased. The effect of suppressing the displacement can be enhanced.
　＜第３実施形態＞
　図６を参照して、本発明の第３実施形態に係る軸連結器のカップリング３２０について説明する。以下では、上記第１実施形態と異なる点を中心に説明し、図中、上記第１実施形態で説明した構成と同一の構成または相当する構成には同一の符号を付して説明を省略する。 <Third Embodiment>
With reference to FIG. 6, the coupling 320 of the shaft coupler which concerns on 3rd Embodiment of this invention is demonstrated. The following description will focus on differences from the first embodiment, and in the figure, the same or corresponding components as those described in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted. .
　図６（ａ）はカップリング３２０の平面図であり、図６（ｂ）は図６（ａ）のＶＩｂ－ＶＩｂ線に沿う断面図である。図６（ｃ）は図６（ａ）のＶＩｃ－ＶＩｃ線に沿う断面図である。第１実施形態では、嵌合凹凸部（嵌合凸部２２ｆ、嵌合凹部２６ｆ）が、内側リング２１及び外側リング２５の軸方向の位置ずれを規制する構成とされていた。これに対して、第３実施形態では、嵌合凹凸部（嵌合凹部３２３ｆ、嵌合凸部３２６ｆ）が、内側リング３２１及び外側リング３２５の径方向の位置ずれを規制する構成とされている。以下、カップリング３２０について詳しく説明する。なお、第３実施形態の電動パワーステアリング装置におけるカップリング３２０以外の構成は、第１実施形態と同様であるので説明を省略する。 6 (a) is a plan view of the coupling 320, and FIG. 6 (b) is a cross-sectional view taken along the line VIb-VIb of FIG. 6 (a). FIG. 6C is a cross-sectional view taken along the line VIc-VIc in FIG. In 1st Embodiment, the fitting uneven | corrugated part (fitting convex part 22f, fitting recessed part 26f) was set as the structure which controls the position shift of the axial direction of the inner side ring 21 and the outer side ring 25. As shown in FIG. On the other hand, in 3rd Embodiment, it is set as the structure by which a fitting uneven | corrugated part (fitting recessed part 323f, fitting convex part 326f) regulates the position shift of the radial direction of the inner side ring 321 and the outer side ring 325. FIG. . Hereinafter, the coupling 320 will be described in detail. In addition, since structures other than the coupling 320 in the electric power steering apparatus of the third embodiment are the same as those of the first embodiment, description thereof is omitted.
　図６（ａ）及び図６（ｂ）に示すように、第３実施形態では、内側円筒部３２２に第１実施形態で説明した嵌合凸部２２ｆ（図３（ａ）参照）が設けられておらず、外側円筒部３２６に第１実施形態で説明した嵌合凹部２６ｆ（図３（ｂ）参照）が設けられてない。したがって、第３実施形態では、カップリング３２０に軸方向の位置ずれを規制する部分が存在しない。 As shown in FIGS. 6A and 6B, in the third embodiment, the inner cylindrical portion 322 is provided with the fitting convex portion 22f described in the first embodiment (see FIG. 3A). In addition, the outer cylindrical portion 326 is not provided with the fitting recess 26f (see FIG. 3B) described in the first embodiment. Therefore, in the third embodiment, there is no portion in the coupling 320 that regulates the positional deviation in the axial direction.
　図６（ａ）及び図６（ｃ）に示すように、内側腕部３２３には、その基端部が幅狭となるように窪む嵌合凹部３２３ｆが設けられている。嵌合凹部３２３ｆは、内側腕部３２３の軸方向一端から他端に亘って形成されている。 As shown in FIGS. 6A and 6C, the inner arm portion 323 is provided with a fitting recess 323f that is recessed so that the base end portion is narrow. The fitting recess 323f is formed from one end to the other end of the inner arm 323 in the axial direction.
　図６（ａ）の拡大図に示すように、内側腕部３２３は基端側の幅狭部３５５と先端側の幅広部３５６とを有し、幅狭部３５５の周方向両端面と幅広部３５６の周方向両端面とは、一対の傾斜面３５７によって接続されている。一対の傾斜面３５７は、台形柱形状の嵌合凹部３２３ｆの一側面を構成している。 As shown in the enlarged view of FIG. 6A, the inner arm portion 323 has a narrow portion 355 on the proximal end side and a wide portion 356 on the distal end side, and both end surfaces in the circumferential direction of the narrow portion 355 and the wide portion. Both end surfaces in the circumferential direction of 356 are connected by a pair of inclined surfaces 357. The pair of inclined surfaces 357 constitute one side surface of the trapezoidal columnar fitting recess 323f.
　外側円筒部３２６には、内側腕部３２３の嵌合凹部３２３ｆに嵌合する嵌合凸部３２６ｆが設けられている。嵌合凸部３２６ｆが嵌合凹部３２３ｆに嵌入された状態では、一対の傾斜面３５７を構成する嵌合凹部３２３ｆの一側面と、外側円筒部３２６の嵌合凸部３２６ｆの一側面とが当接する。このように、内側腕部３２３の幅狭部３５５と幅広部３５６との間の段部が、一対の嵌合凸部３２６ｆに引っ掛かる構造とされているので、内側リング３２１と外側リング３２５の径方向の位置ずれが規制される。 The outer cylindrical portion 326 is provided with a fitting convex portion 326f that fits into the fitting concave portion 323f of the inner arm portion 323. In a state where the fitting convex portion 326f is fitted in the fitting concave portion 323f, one side surface of the fitting concave portion 323f constituting the pair of inclined surfaces 357 and one side surface of the fitting convex portion 326f of the outer cylindrical portion 326 are in contact with each other. Touch. As described above, since the step portion between the narrow portion 355 and the wide portion 356 of the inner arm portion 323 is configured to be caught by the pair of fitting convex portions 326f, the diameters of the inner ring 321 and the outer ring 325 are set. Directional misregistration is regulated.
　このような第３実施形態によれば、第１実施形態で説明した（１），（２），（４），（５），（７）と同様の作用効果に加え、次の作用効果を奏する。 According to such 3rd Embodiment, in addition to the effect similar to (1), (2), (4), (5), (7) demonstrated in 1st Embodiment, the following effect is obtained. Play.
　（９）内側リング３２１及び外側リング３２５のそれぞれには、互いに嵌合することで位置ずれを規制する嵌合凹凸部が設けられている。本実施形態では、嵌合凹凸部として、内側リング３２１に嵌合凹部３２３ｆが設けられ、外側リング３２５に嵌合凸部３２６ｆが設けられている。嵌合凹部３２３ｆと嵌合凸部３２６ｆとが互いに嵌合することにより、内側リング３２１及び外側リング３２５の径方向の位置ずれが規制される。 (9) Each of the inner ring 321 and the outer ring 325 is provided with a fitting uneven part that regulates displacement by fitting each other. In the present embodiment, the fitting recesses 323f are provided on the inner ring 321 and the fitting projections 326f are provided on the outer ring 325 as the fitting unevenness portions. When the fitting concave portion 323f and the fitting convex portion 326f are fitted to each other, positional displacement in the radial direction of the inner ring 321 and the outer ring 325 is restricted.
　内側リング３２１及び外側リング３２５の位置ずれを抑制できるので、トルク伝達部３５１の剛性特性の変化を抑制でき、トルク伝達の効率低下を防止することができる。さらに、位置ずれを起因とした、カップリング３２０の磨耗や破損を防止することもできる。 Since the displacement of the inner ring 321 and the outer ring 325 can be suppressed, a change in the rigidity characteristic of the torque transmission portion 351 can be suppressed, and a decrease in torque transmission efficiency can be prevented. Furthermore, it is possible to prevent the coupling 320 from being worn or damaged due to misalignment.
　（１０）カップリング３２０の構成部材に嵌合凹凸部を設けたので、別部材によって、内側リング３２１及び外側リング３２５の径方向の位置ずれを規制する必要がない。たとえば、出力シャフト７ａ及びウォームシャフト２によって内側リング２１の径方向内側への位置ずれを規制する（第１実施形態参照）必要がない。このため、隙間９０ａ，９０ｂを大きくとることができ、カップリング３２０の生産効率の向上を図ることができる。 (10) Since the concave and convex portions are provided on the constituent members of the coupling 320, it is not necessary to regulate the positional deviation in the radial direction of the inner ring 321 and the outer ring 325 by another member. For example, there is no need to regulate the displacement of the inner ring 21 inward in the radial direction by the output shaft 7a and the worm shaft 2 (see the first embodiment). For this reason, the gaps 90a and 90b can be made large, and the production efficiency of the coupling 320 can be improved.
　＜第４実施形態＞
　図７を参照して、本発明の第４実施形態に係る軸連結器のカップリング４２０について説明する。以下では、上記第１実施形態と異なる点を中心に説明し、図中、上記第１実施形態で説明した構成と同一の構成または相当する構成には同一の符号を付して説明を省略する。 <Fourth embodiment>
With reference to FIG. 7, the coupling 420 of the shaft coupler which concerns on 4th Embodiment of this invention is demonstrated. The following description will focus on differences from the first embodiment, and in the figure, the same or corresponding components as those described in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted. .
　図７（ａ）はカップリング４２０の平面図であり、図７（ｂ）は図７（ａ）のＶＩＩｂ－ＶＩＩｂ線に沿う断面図である。図７（ｃ）は図７（ａ）のＶＩＩｃ－ＶＩＩｃ線に沿う断面図である。第１実施形態及び第２実施形態では、嵌合凹凸部が内側リング２１，２２１及び外側リング２５，２２５の軸方向の位置ずれを規制する構成とされていた。第３実施形態では、嵌合凹凸部が内側リング３２１及び外側リング３２５の径方向の位置ずれを規制する構成とされていた。これに対して、第４実施形態では、嵌合凹凸部が、内側リング４２１及び外側リング４２５の軸方向及び径方向の位置ずれを規制する構成とされている。以下、カップリング４２０について詳しく説明する。なお、第４実施形態の電動パワーステアリング装置におけるカップリング４２０以外の構成は、第１実施形態と同様であるので説明を省略する。 7A is a plan view of the coupling 420, and FIG. 7B is a cross-sectional view taken along the line VIIb-VIIb of FIG. 7A. FIG. 7C is a cross-sectional view taken along the line VIIc-VIIc in FIG. In 1st Embodiment and 2nd Embodiment, the fitting uneven | corrugated | grooved part was set as the structure which controls the position shift of the axial direction of the inner side rings 21 and 221 and the outer side rings 25 and 225. In 3rd Embodiment, it was set as the structure by which a fitting uneven | corrugated | grooved part controls the position shift of the radial direction of the inner ring 321 and the outer ring 325. On the other hand, in 4th Embodiment, it is set as the structure by which a fitting uneven | corrugated | grooved part controls the position shift of the axial direction and radial direction of the inner side ring 421 and the outer side ring 425. FIG. Hereinafter, the coupling 420 will be described in detail. In addition, since structures other than the coupling 420 in the electric power steering apparatus of the fourth embodiment are the same as those of the first embodiment, description thereof is omitted.
　図７（ａ）～図７（ｃ）に示すように、内側腕部４２３は、径方向と軸方向に平行な一対の平面部４５７と、一対の平面部４５７の径方向端部同士を接続する帯状部４５８と、を備えている。平面部４５７及び帯状部４５８は、それぞれ矩形状である。 As shown in FIGS. 7A to 7C, the inner arm portion 423 connects a pair of plane portions 457 parallel to the radial direction and the axial direction, and ends of the pair of plane portions 457 in the radial direction. And a belt-like portion 458. The plane part 457 and the band-like part 458 are each rectangular.
　第４実施形態では、第１実施形態で説明した嵌合凸部２２ｆ及び嵌合凹部２６ｆに代えて、嵌合凸部４２３ｆ及び嵌合凹部４２５ｆを備えている。嵌合凸部４２３ｆは、内側腕部４２３の一対の平面部４５７から周方向外方に突出する直方体形状の凸部である。嵌合凹部４２５ｆは、嵌合凸部４２３ｆに嵌合する直方体形状の凹部であり、外側リング４２５の外側円筒部４２６及び外側腕部４２７に連続して設けられている。 In the fourth embodiment, instead of the fitting convex portion 22f and the fitting concave portion 26f described in the first embodiment, a fitting convex portion 423f and a fitting concave portion 425f are provided. The fitting convex portion 423f is a rectangular parallelepiped convex portion that protrudes outward in the circumferential direction from the pair of flat surface portions 457 of the inner arm portion 423. The fitting concave portion 425f is a rectangular parallelepiped concave portion that fits into the fitting convex portion 423f, and is continuously provided on the outer cylindrical portion 426 and the outer arm portion 427 of the outer ring 425.
　図７（ｃ）に示すように、嵌合凸部４２３ｆが嵌合凹部４２５ｆに嵌入された状態では、嵌合凸部４２３ｆの軸方向両端面が、嵌合凹部４２５ｆの軸方向両端面に当接する。また、図７（ａ）に示すように、嵌合凸部４２３ｆが嵌合凹部４２５ｆに嵌入された状態では、嵌合凸部４２３ｆの径方向両端面が、嵌合凹部４２５ｆの径方向両端面に当接する。したがって、嵌合凸部４２３ｆ及び嵌合凹部４２５ｆが互いに嵌合することで、内側リング４２１及び外側リング４２５の軸方向及び径方向の位置ずれが規制される。 As shown in FIG. 7C, in a state where the fitting convex portion 423f is fitted into the fitting concave portion 425f, both axial end surfaces of the fitting convex portion 423f are in contact with both axial end surfaces of the fitting concave portion 425f. Touch. Further, as shown in FIG. 7A, in a state where the fitting convex portion 423f is fitted in the fitting concave portion 425f, both radial end surfaces of the fitting convex portion 423f are both radial end surfaces of the fitting concave portion 425f. Abut. Therefore, when the fitting convex portion 423f and the fitting concave portion 425f are fitted to each other, the axial and radial positional deviations of the inner ring 421 and the outer ring 425 are restricted.
　このような第４実施形態によれば、第１実施形態で説明した（１）～（５），（７）と同様の作用効果、及び、第３実施形態で説明した（９），（１０）と同様の作用効果に加え、次の作用効果を奏する。 According to the fourth embodiment, the same effects as (1) to (5) and (7) described in the first embodiment, and (9) and (10 described in the third embodiment). ) In addition to the same function and effect, the following function and effect are exhibited.
　（１１）一組の嵌合凸部４２３ｆと嵌合凹部４２５ｆが、軸方向の位置ずれ規制機能と径方向の位置ずれ規制機能とを備えているので、それぞれの機能を別々の嵌合凹凸部で実現する場合に比べて、カップリング４２０の構成を単純にすることができる。その結果、カップリング４２０の生産コストを低減できる。 (11) Since the pair of fitting protrusions 423f and the fitting recesses 425f have an axial position deviation restricting function and a radial position deviation restricting function, the respective functions are provided as separate fitting uneven parts. Compared with the case where it implement | achieves by, the structure of the coupling 420 can be simplified. As a result, the production cost of the coupling 420 can be reduced.
　以下のような変形例も本発明の範囲内であり、変形例に示す構成と上述の実施形態で説明した構成を組み合わせたり、上述の異なる実施形態で説明した構成同士を組み合わせたり、以下の異なる変形例で説明する構成同士を組み合わせることも可能である。 The following modified examples are also within the scope of the present invention, and the configuration shown in the modified example and the configuration described in the above-described embodiment are combined, the configurations described in the above-described different embodiments are combined, or the following different It is also possible to combine the configurations described in the modification.
　たとえば、上述の異なる実施形態で説明した構成同士の組み合わせとして、第２実施形態で説明した外側リング２２５の嵌合凹部２２５ｆに第１実施形態で説明した内側リング２１の嵌合凸部２２ｆを嵌合させてもよい。その他、第４実施形態で説明した嵌合凹凸部（４２３ｆ，４２５ｆ）を第１実施形態のカップリング２０にさらに設けるようにしてもよい。第１実施形態で説明した嵌合凹凸部（２２ｆ，２６ｆ）や第４実施形態で説明した嵌合凹凸部（４２３ｆ，４２５ｆ）を第３実施形態のカップリング３２０にさらに設けるようにしてもよい。 For example, as a combination of the configurations described in the different embodiments, the fitting convex portion 22f of the inner ring 21 described in the first embodiment is fitted into the fitting concave portion 225f of the outer ring 225 described in the second embodiment. May be combined. In addition, you may make it further provide the coupling uneven | corrugated | grooved part (423f, 425f) demonstrated in 4th Embodiment in the coupling 20 of 1st Embodiment. The fitting irregularities (22f, 26f) described in the first embodiment and the fitting irregularities (423f, 425f) described in the fourth embodiment may be further provided in the coupling 320 of the third embodiment. .
　＜変形例１＞
　上記実施形態では、電動パワーステアリング装置１０１のウォームシャフト２と電動モータ７の出力シャフト７ａを連結する軸連結器１００を例に説明したが、本発明はこれに限定されない。第１の電動モータの出力シャフトと、第２の電動モータの出力シャフトとを連結する軸連結器に本発明を適用してもよい。電動パワーステアリング装置に用いる軸連結器に限定されることもなく、種々の装置の軸連結器に本発明を適用することができる。 <Modification 1>
In the above embodiment, the shaft coupler 100 that connects the worm shaft 2 of the electric power steering apparatus 101 and the output shaft 7a of the electric motor 7 has been described as an example, but the present invention is not limited to this. The present invention may be applied to a shaft coupler that connects the output shaft of the first electric motor and the output shaft of the second electric motor. The present invention can be applied to shaft couplers of various apparatuses without being limited to the shaft couplers used in the electric power steering apparatus.
　＜変形例２＞
　上記実施形態では、内側リング２１，２２１，３２１，４２１の外周面の形状及び外側リング２５，２２５，３２５，４２５の内周面の形状を、それぞれカップリング２０，２２０，３２０，４２０の中心軸ＣＡを中心とした回転対称形状とした例について説明したが、本発明はこれに限定されない。 <Modification 2>
In the above embodiment, the shape of the outer peripheral surface of the inner rings 21, 221, 321, 421 and the shape of the inner peripheral surface of the outer rings 25, 225, 325, 425 are the central axes of the couplings 20, 220, 320, 420, respectively. Although an example of a rotationally symmetric shape centered on CA has been described, the present invention is not limited to this.
　＜変形例２－１＞
　第１実施形態では、隣り合うトルク伝達部５１の間の計８箇所の全てに、嵌合凸部２２ｆと嵌合凹部２６ｆが設けられている例について説明したが、本発明はこれに限定されない。たとえば、第１実施形態と同様、外側円筒部２６には、計８箇所の嵌合凹部２６ｆを設けるが、内側円筒部２２には、１箇所の嵌合凸部２２ｆを設けるようにしてもよい。少なくとも１箇所の嵌合凸部２２ｆを設けることで、軸方向の位置ずれを防止することができる。また、嵌合凹部２６ｆは、計８箇所に設けられているので、回転方向の位置合わせの自由度は第１実施形態と同様であり、内側リング２１と外側リング２５の組付性を向上できる。少なくとも、嵌合凹部２６ｆが設けられる外側リング２５の内周面の形状を、中心軸ＣＡを中心とした回転対称形状とすることにより、回転方向の位置合わせの自由度を向上できるので、内側リング２１と外側リング２５の組付性を向上できる。 <Modification 2-1>
Although 1st Embodiment demonstrated the example by which the fitting convex part 22f and the fitting recessed part 26f were provided in all the eight places between the adjacent torque transmission parts 51, this invention is not limited to this. . For example, as in the first embodiment, the outer cylindrical portion 26 is provided with a total of eight fitting concave portions 26f, but the inner cylindrical portion 22 may be provided with one fitting convex portion 22f. . By providing at least one fitting projection 22f, axial displacement can be prevented. In addition, since the fitting recesses 26f are provided at a total of eight locations, the degree of freedom of alignment in the rotational direction is the same as that of the first embodiment, and the assembling property of the inner ring 21 and the outer ring 25 can be improved. . Since at least the shape of the inner peripheral surface of the outer ring 25 provided with the fitting recess 26f is rotationally symmetric about the central axis CA, the degree of freedom in alignment in the rotational direction can be improved. The assemblability of the outer ring 21 and the outer ring 25 can be improved.
　＜変形例２－２＞
　第４実施形態では、複数の内側腕部４２３のそれぞれに嵌合凸部４２３ｆが設けられている例について説明したが、本発明はこれに限定されない。たとえば、複数の内側腕部４２３のうち、少なくとも１箇所に嵌合凸部４２３ｆを設けてもよい。少なくとも、嵌合凹部４２５ｆが設けられる外側リング４２５の内周面の形状を、中心軸ＣＡを中心とした回転対称形状とすることにより、回転方向の位置合わせの自由度を向上できるので、内側リング４２１と外側リング４２５の組付性を向上できる。 <Modification 2-2>
In the fourth embodiment, the example in which the fitting convex portion 423f is provided in each of the plurality of inner arm portions 423 has been described, but the present invention is not limited to this. For example, you may provide the fitting convex part 423f in at least one place among the some inner side arm parts 423. FIG. Since at least the inner peripheral surface of the outer ring 425 provided with the fitting recess 425f has a rotationally symmetric shape with the central axis CA as the center, the degree of freedom in alignment in the rotational direction can be improved. The assemblability of 421 and the outer ring 425 can be improved.
　＜変形例２－３＞
　上記変形例２－１及び変形例２－２では、嵌合凸部２２ｆ，４２３ｆの数を嵌合凹部２６ｆ，４２５ｆの数に比べて少なくする例について説明したが、本発明はこれに限定されず、嵌合凸部４２３ｆ及び嵌合凹部４２５ｆをそれぞれ少なくとも１つ設ける構成としてもよい。 <Modification 2-3>
In the modified examples 2-1 and 2-2, the example in which the number of the fitting convex portions 22f and 423f is reduced as compared with the number of the fitting concave portions 26f and 425f has been described, but the present invention is not limited to this. Alternatively, at least one fitting convex portion 423f and fitting concave portion 425f may be provided.
　＜変形例３＞
　第１、第２及び第４実施形態では、内側リング２１，２２１，４２１に嵌合凸部２２ｆ，２２１ｆ，４２３ｆを設け、外側リング２５，２２５，４２５に嵌合凹部２６ｆ，２２５ｆ，４２５ｆを設ける例について説明したが、本発明はこれに限定されない。第３実施形態では、内側リング３２１に嵌合凹部３２３ｆを設け、外側リング３２５に嵌合凸部３２６ｆを設ける例について説明したが、本発明はこれに限定されない。嵌合凸部と嵌合凹部の関係は、逆であってもよい。 <Modification 3>
In the first, second and fourth embodiments, the inner rings 21, 221 and 421 are provided with fitting convex portions 22f, 221f and 423f, and the outer rings 25, 225 and 425 are provided with fitting concave portions 26f, 225f and 425f. Although an example has been described, the present invention is not limited to this. In the third embodiment, the example in which the fitting recess 323f is provided in the inner ring 321 and the fitting protrusion 326f is provided in the outer ring 325 has been described, but the present invention is not limited to this. The relationship between the fitting convex part and the fitting concave part may be reversed.
　＜変形例４＞
　上記実施形態では、内側リング２１，２２１，３２１，４２１をゴムで形成し、外側リング２５，２２５，３２５，４２５を内側リング２１，２２１，３２１，４２１の材料よりも剛性の大きい樹脂により形成する例について説明したが、本発明はこれに限定されない。外側リング２５，２２５，３２５，４２５をゴムで形成し、内側リング２１，２２１，３２１，４２１を外側リング２５，２２５，３２５，４２５の材料よりも剛性の大きい樹脂により形成してもよい。また、材料はゴムと樹脂の組み合わせに限定されない。内側リング２１，２２１，３２１，４２１及び外側リング２５，２２５，３２５，４２５の剛性が互いに異なるように、種々の材料の中から内側リング２１，２２１，３２１，４２１及び外側リング２５，２２５，３２５，４２５の材料を選定し、剛性特性を調整することができる。 <Modification 4>
In the above embodiment, the inner rings 21, 221, 321, 421 are formed of rubber, and the outer rings 25, 225, 325, 425 are formed of a resin having a rigidity higher than that of the material of the inner rings 21, 221, 321, 421. Although an example has been described, the present invention is not limited to this. The outer rings 25, 225, 325, and 425 may be formed of rubber, and the inner rings 21, 221, 321, and 421 may be formed of a resin having higher rigidity than the material of the outer rings 25, 225, 325, and 425. The material is not limited to a combination of rubber and resin. The inner rings 21, 221, 321, 421 and the outer rings 25, 225, 325 are made of various materials so that the inner rings 21, 221, 321, 421 and the outer rings 25, 225, 325, 425 have different rigidity. , 425 materials can be selected and the rigidity characteristics can be adjusted.
　＜変形例５＞
　上記実施形態では、モータ側ジョイント８及びウォーム側ジョイント６がそれぞれ４つの突出部３２，４２を有する構成について例示したが、突出部３２，４２の数は４つに限定されるものではなく、複数であればよい。例えば、突出部３２，４２は３つであってもよい。 <Modification 5>
In the above embodiment, the motor side joint 8 and the worm side joint 6 are exemplified as having the four protrusions 32 and 42, respectively. However, the number of the protrusions 32 and 42 is not limited to four, and a plurality of protrusions 32 and 42 are provided. If it is. For example, the number of the protrusions 32 and 42 may be three.
　＜変形例６＞
　上記実施形態では、外側リング２５，２２５，３２５，４２５及び内側リング２１，２２１，３２１，４２１を個別に成形し、外側リング２５，２２５，３２５，４２５の開口部２５ｈに内側リング２１，２２１，３２１，４２１を嵌め込んでカップリング２０，２２０，３２０，４２０を完成させる例について説明したが、本発明はこれに限定されない。たとえば、２色成形（ダブルモールド）により、外側リング２５，２２５，３２５，４２５の材料と内側リング２１，２２１，３２１，４２１の材料を組み合わせて、カップリング２０，２２０，３２０，４２０を一体成形してもよい。 <Modification 6>
In the above embodiment, the outer rings 25, 225, 325, 425 and the inner rings 21, 221, 321, 421 are individually molded, and the inner rings 21, 221, Although an example in which the couplings 20, 220, 320, and 420 are completed by fitting 321 and 421 has been described, the present invention is not limited to this. For example, by combining the materials of the outer rings 25, 225, 325, 425 and the materials of the inner rings 21, 221, 321, 421 by two-color molding (double mold), the couplings 20, 220, 320, 420 are integrally molded. May be.
　以下、本発明の実施形態の構成、作用、及び効果をまとめて説明する。 Hereinafter, the configuration, operation, and effect of the embodiment of the present invention will be described together.
　軸連結器１００は、出力シャフト（第１軸）７ａに接続されるモータ側ジョイント（第１ジョイント）８と、ウォームシャフト（第２軸）２に接続されるウォーム側ジョイント（第２ジョイント）６と、モータ側ジョイント（第１ジョイント）８とウォーム側ジョイント（第２ジョイント）６との間に設けられるカップリング２０，２２０，３２０，４２０と、を備え、モータ側ジョイント（第１ジョイント）８及びウォーム側ジョイント（第２ジョイント）６は、軸方向に延びる複数の突出部３２，４２を有し、互いの突出部３２，４２が周方向に交互に並ぶように配置され、カップリング２０，２２０，３２０，４２０は、モータ側ジョイント（第１ジョイント）８及びウォーム側ジョイント（第２ジョイント）６の隣り合う突出部３２，４２に挟まれて出力シャフト（第１軸）７ａの回転トルクをウォームシャフト（第２軸）２に伝達するトルク伝達部５１，３５１を有し、カップリング２０，２２０，３２０，４２０は、内側リング２１，２２１，３２１，４２１と、内側リング２１，２２１，３２１，４２１の軸方向両端面を露出させ、内側リング２１，２２１，３２１，４２１の径方向外周面を覆う外側リング２５，２２５，３２５，４２５と、を有し、内側リング２１，２２１，３２１，４２１は、円筒状の内側円筒部２２，２２２，３２２と、内側円筒部２２，２２２，３２２の外周から径方向外方に放射状に延在する複数の内側腕部２３，２２３，３２３，４２３と、を有し、外側リング２５，２２５，３２５，４２５は、内側円筒部２２，２２２，３２２を覆う円筒状の外側円筒部２６，２２６，３２６，４２６と、外側円筒部２６，２２６，３２６，４２６の外周から径方向外方に放射状に延在し、内側腕部２３，２２３，３２３，４２３を覆う複数の外側腕部２７，２２７，４２７と、を有し、内側リング２１，２２１，３２１，４２１及び外側リング２５，２２５，３２５，４２５は、剛性が互いに異なり、トルク伝達部５１，３５１は、内側腕部２３，２２３，３２３，４２３と外側腕部２７，２２７，４２７とを有し、内側リング２１，２２１，３２１，４２１及び外側リング２５，２２５，３２５，４２５のそれぞれには、互いに嵌合することで位置ずれを規制する嵌合凹凸部として、嵌合凸部２２ｆ，２２１ｆ，４２３ｆ及び嵌合凹部３２３ｆ並びに嵌合凹部２６ｆ，２２５ｆ，４２５ｆ及び嵌合凸部３２６ｆが設けられている。 The shaft coupler 100 includes a motor side joint (first joint) 8 connected to the output shaft (first axis) 7 a and a worm side joint (second joint) 6 connected to the worm shaft (second axis) 2. And couplings 20, 220, 320, 420 provided between the motor side joint (first joint) 8 and the worm side joint (second joint) 6, and the motor side joint (first joint) 8 The worm side joint (second joint) 6 has a plurality of protrusions 32 and 42 extending in the axial direction, and the protrusions 32 and 42 are arranged so as to be alternately arranged in the circumferential direction. Reference numerals 220, 320, and 420 denote adjacent protrusions 3 of the motor side joint (first joint) 8 and the worm side joint (second joint) 6. , 42 and the torque transmission portions 51, 351 for transmitting the rotational torque of the output shaft (first shaft) 7a to the worm shaft (second shaft) 2, and the couplings 20, 220, 320, 420 are Outer rings 25, 225 that expose both axial ends of the inner rings 21, 221, 321, 421 and the inner rings 21, 221, 321, 421 and cover the radially outer peripheral surfaces of the inner rings 21, 221, 321, 421 , 325, 425, and the inner rings 21, 221, 321, 421 are formed radially outward from the outer periphery of the inner cylindrical portions 22, 222, 322 and the inner cylindrical portions 22, 222, 322. A plurality of radially extending inner arms 23, 223, 323, and 423, and the outer rings 25, 225, 325, and 425 connect the inner cylindrical portions 22, 222, and 322, respectively. The outer cylindrical portions 26, 226, 326, and 426 having a cylindrical shape and radially extending outward from the outer periphery of the outer cylindrical portions 26, 226, 326, and 426, and inner arm portions 23, 223, 323, and 423 A plurality of outer arm portions 27, 227, and 427 covering the inner ring 21, 221, 321, 421 and the outer rings 25, 225, 325, 425 are different in rigidity and the torque transmitting portions 51, 351. Has inner arm portions 23, 223, 323, 423 and outer arm portions 27, 227, 427, and inner rings 21, 221, 321, 421 and outer rings 25, 225, 325, 425 are respectively As fitting irregularities that regulate displacement by fitting each other, fitting convex portions 22f, 221f, 423f, fitting concave portion 323f, and fitting concave portions 26f, 225f, 42 are provided. 5f and fitting convex part 326f are provided.
　この構成では、外側リング２５，２２５，３２５，４２５に組み付けられた内側リング２１，２２１，３２１，４２１の軸方向両端面が露出しているので、外側リング２５，２２５，３２５，４２５の軸方向両側のいずれからでも内側リング２１，２２１，３２１，４２１を取り付けることができ、嵌合凹凸部である嵌合凸部２２ｆ，２２１ｆ，４２３ｆ及び嵌合凹部３２３ｆ並びに嵌合凹部２６ｆ，２２５ｆ，４２５ｆ及び嵌合凸部３２６ｆによって内側リング２１，２２１，３２１，４２１及び外側リング２５，２２５，３２５，４２５の位置ずれが規制される。 In this configuration, both end surfaces in the axial direction of the inner rings 21, 221, 321, 421 assembled to the outer rings 25, 225, 325, 425 are exposed, so the axial direction of the outer rings 25, 225, 325, 425 is exposed. The inner rings 21, 221, 321, 421 can be attached from either side, and the fitting convex portions 22f, 221f, 423f and the fitting concave portions 323f, the fitting concave portions 26f, 225f, 425f, which are fitting concave and convex portions, and The misalignment of the inner rings 21, 221, 321, 421 and the outer rings 25, 225, 325, 425 is restricted by the fitting convex portion 326 f.
　軸連結器１００は、嵌合凹凸部である嵌合凸部２２ｆ，２２１ｆ，４２３ｆ及び嵌合凹部２６ｆ，２２５ｆ，４２５ｆが、内側リング２１，２２１，４２１及び外側リング２５，２２５，４２５の軸方向の位置ずれを規制する。 The shaft coupler 100 includes fitting projections 22f, 221f, 423f and fitting recesses 26f, 225f, 425f, which are fitting projections and depressions, in the axial direction of the inner rings 21, 221, 421 and the outer rings 25, 225, 425. The positional deviation of is controlled.
　この構成では、内側リング２１，２２１，４２１及び外側リング２５，２２５，４２５の軸方向の位置ずれに起因した剛性特性の低下を抑制できる。 In this configuration, it is possible to suppress a decrease in rigidity characteristics due to the axial displacement of the inner rings 21, 221 and 421 and the outer rings 25, 225 and 425.
　軸連結器１００は、嵌合凹凸部である嵌合凹部３２３ｆ及び嵌合凸部４２３ｆ並びに嵌合凸部３２６ｆ及び嵌合凹部４２５ｆが、内側リング３２１，４２１及び外側リング３２５，４２５の径方向の位置ずれを規制する。 The shaft coupler 100 includes fitting recesses 323f and fitting projections 423f, and fitting projections 326f and fitting recesses 425f, which are fitting projections and depressions, in the radial direction of the inner rings 321 and 421 and the outer rings 325 and 425. Regulate misalignment.
　この構成では、内側リング３２１，４２１及び外側リング３２５，４２５の径方向の位置ずれに起因した剛性特性の低下を抑制できる。 In this configuration, it is possible to suppress the deterioration of the rigidity characteristics due to the radial position shift of the inner rings 321 and 421 and the outer rings 325 and 425.
　軸連結器１００は、内側リング２１，２２１，３２１，４２１の外周面の形状及び外側リング２５，２２５，３２５，４２５の内周面の形状が、カップリング２０，２２０，３２０，４２０の中心軸ＣＡを中心とした回転対称形状である。 In the shaft coupler 100, the shape of the outer peripheral surface of the inner rings 21, 221, 321, 421 and the shape of the inner peripheral surface of the outer rings 25, 225, 325, 425 are the central axes of the couplings 20, 220, 320, 420. It is a rotationally symmetric shape centered on CA.
　この構成では、内側リング２１，２２１，３２１，４２１と外側リング２５，２２５，３２５，４２５の回転方向の位置合わせの自由度を向上できるので、内側リング２１，２２１，３２１，４２１と外側リング２５，２２５，３２５，４２５の組付性を向上できる。 In this configuration, the degree of freedom in the alignment of the inner rings 21, 221, 321, 421 and the outer rings 25, 225, 325, 425 in the rotational direction can be improved, so the inner rings 21, 221, 321, 421 and the outer ring 25 , 225, 325, 425 can be improved.
　軸連結器１００は、嵌合凹凸部である嵌合凸部２２ｆ，２２１ｆ，４２３ｆ及び嵌合凹部３２３ｆ並びに嵌合凹部２６ｆ，２２５ｆ，４２５ｆ及び嵌合凸部３２６ｆが、カップリング２０，２２０，３２０，４２０の軸方向中心面ＣＰに対して面対称に形成されている。 The shaft coupler 100 includes coupling projections 22f, 221f, 423f and fitting recesses 323f, fitting recesses 26f, 225f, 425f, and fitting projections 326f, which are fitting projections and depressions, and couplings 20, 220, 320. , 420 are symmetrical with respect to the axial center plane CP.
　この構成では、内側リング２１，２２１，３２１，４２１を外側リング２５，２２５，３２５，４２５に取り付ける際の内側リング２１，２２１，３２１，４２１の向きの自由度が高いため、内側リング２１，２２１，３２１，４２１と外側リング２５，２２５，３２５，４２５の組付性を向上できる。 In this configuration, since the inner rings 21, 221, 321, 421 are attached to the outer rings 25, 225, 325, 425 with a high degree of freedom in the direction of the inner rings 21, 321, 321, 421, , 321, 421 and the outer ring 25, 225, 325, 425 can be improved.
　電動パワーステアリング装置１０１は、上記軸連結器１００を備え、第１軸が、電動モータ７の出力シャフト７ａであり、第２軸が、ウォームシャフト２である。 The electric power steering apparatus 101 includes the shaft coupler 100, the first axis is the output shaft 7 a of the electric motor 7, and the second axis is the worm shaft 2.
　この構成では、剛性特性の変化の少ないカップリング２０，２２０，３２０，４２０を用いることで、長期に亘って性能を維持できる電動パワーステアリング装置１０１を提供できる。 In this configuration, it is possible to provide the electric power steering apparatus 101 that can maintain the performance over a long period of time by using the couplings 20, 220, 320, and 420 with less change in rigidity characteristics.
　以上、本発明の実施形態について説明したが、上記実施形態は本発明の適用例の一部を示したに過ぎず、本発明の技術的範囲を上記実施形態の具体的構成に限定する趣旨ではない。 The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.
　本願は２０１７年３月３０日に日本国特許庁に出願された特願２０１７－０６８４２２に基づく優先権を主張し、この出願の全ての内容は参照により本明細書に組み込まれる。 This application claims priority based on Japanese Patent Application No. 2017-068422 filed with the Japan Patent Office on March 30, 2017, the entire contents of which are incorporated herein by reference.

Claims (6)

  1. 　第１軸に接続される第１ジョイントと、
    　第２軸に接続される第２ジョイントと、
    　前記第１ジョイントと前記第２ジョイントとの間に設けられるカップリングと、を備え、
    　前記第１ジョイント及び前記第２ジョイントは、軸方向に延びる複数の突出部を有し、互いの前記突出部が周方向に交互に並ぶように配置され、
    　前記カップリングは、前記第１ジョイント及び前記第２ジョイントの隣り合う前記突出部に挟まれて前記第１軸の回転トルクを前記第２軸に伝達するトルク伝達部を有し、
    　前記カップリングは、内側リングと、前記内側リングの軸方向両端面を露出させ、前記内側リングの径方向外周面を覆う外側リングと、を有し、
    　前記内側リングは、円筒状の内側円筒部と、前記内側円筒部の外周から径方向外方に放射状に延在する複数の内側腕部と、を有し、
    　前記外側リングは、前記内側円筒部を覆う円筒状の外側円筒部と、前記外側円筒部の外周から径方向外方に放射状に延在し、前記内側腕部を覆う複数の外側腕部と、を有し、
    　前記内側リング及び前記外側リングは、剛性が互いに異なり、
    　前記トルク伝達部は、前記内側腕部と前記外側腕部とを有し、
    　前記内側リング及び前記外側リングのそれぞれには、互いに嵌合することで位置ずれを規制する嵌合凹凸部が設けられている軸連結器。     A first joint connected to the first shaft;
    A second joint connected to the second shaft;
    A coupling provided between the first joint and the second joint,
    The first joint and the second joint have a plurality of protrusions extending in the axial direction, and the protrusions are arranged alternately in the circumferential direction.
    The coupling includes a torque transmission unit that is sandwiched between the adjacent protrusions of the first joint and the second joint and transmits the rotational torque of the first shaft to the second shaft,
    The coupling includes an inner ring, and an outer ring that exposes both axial end surfaces of the inner ring and covers a radially outer peripheral surface of the inner ring,
    The inner ring has a cylindrical inner cylindrical portion, and a plurality of inner arm portions extending radially outward from the outer periphery of the inner cylindrical portion,
    The outer ring includes a cylindrical outer cylindrical portion that covers the inner cylindrical portion, a plurality of outer arm portions that extend radially outward from an outer periphery of the outer cylindrical portion, and covers the inner arm portion; Have
    The inner ring and the outer ring have different rigidity from each other,
    The torque transmission part has the inner arm part and the outer arm part,
    Each of the inner ring and the outer ring is a shaft coupler provided with a fitting uneven part that regulates displacement by fitting with each other.
  2. 　請求項１に記載の軸連結器において、
    　前記嵌合凹凸部は、前記内側リング及び前記外側リングの軸方向の位置ずれを規制する軸連結器。     The shaft coupler according to claim 1,
    The fitting uneven part is a shaft coupler that regulates axial displacement of the inner ring and the outer ring.
  3. 　請求項１に記載の軸連結器において、
    　前記嵌合凹凸部は、前記内側リング及び前記外側リングの径方向の位置ずれを規制する軸連結器。     The shaft coupler according to claim 1,
    The fitting concavity and convexity part is a shaft coupler that regulates radial displacement of the inner ring and the outer ring.
  4. 　請求項１に記載の軸連結器において、
    　前記内側リングの外周面の形状及び前記外側リングの内周面の形状は、前記カップリングの中心軸を中心とした回転対称形状である軸連結器。     The shaft coupler according to claim 1,
    The shape of the outer peripheral surface of the inner ring and the shape of the inner peripheral surface of the outer ring are shaft couplers that are rotationally symmetric about the central axis of the coupling.
  5. 　請求項１に記載の軸連結器において、
    　前記嵌合凹凸部は、前記カップリングの軸方向中心面に対して面対称に形成されている軸連結器。     The shaft coupler according to claim 1,
    The fitting concavity and convexity part is an axial coupler formed symmetrically with respect to the axial center plane of the coupling.
  6. 　請求項１に記載の軸連結器を備え、
    　前記第１軸は、電動モータの出力シャフトであり、
    　前記第２軸は、ウォームシャフトである電動パワーステアリング装置。     The shaft coupler according to claim 1,
    The first shaft is an output shaft of an electric motor;
    The electric power steering device, wherein the second shaft is a worm shaft.
PCT/JP2018/008567 2017-03-30 2018-03-06 Electric power steering device and shaft coupler used for same WO2018180282A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017068422A JP2018169012A (en) 2017-03-30 2017-03-30 Electric power steering device and shaft connector used in the same
JP2017-068422 2017-03-30

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010060052A (en) * 2008-09-03 2010-03-18 Oiles Ind Co Ltd Shaft-connecting mechanism for electric power steering device
JP2010164162A (en) * 2009-01-16 2010-07-29 Oiles Ind Co Ltd Shaft coupling mechanism
JP2013189112A (en) * 2012-03-14 2013-09-26 Jtekt Corp Electric power steering device
JP2016002926A (en) * 2014-06-18 2016-01-12 株式会社ジェイテクト Power transmission joint, worm reduction gear and electric power steering device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010060052A (en) * 2008-09-03 2010-03-18 Oiles Ind Co Ltd Shaft-connecting mechanism for electric power steering device
JP2010164162A (en) * 2009-01-16 2010-07-29 Oiles Ind Co Ltd Shaft coupling mechanism
JP2013189112A (en) * 2012-03-14 2013-09-26 Jtekt Corp Electric power steering device
JP2016002926A (en) * 2014-06-18 2016-01-12 株式会社ジェイテクト Power transmission joint, worm reduction gear and electric power steering device

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