WO2008093861A1 - Dispositif de direction de puissance électrique - Google Patents

Dispositif de direction de puissance électrique Download PDF

Info

Publication number
WO2008093861A1
WO2008093861A1 PCT/JP2008/051710 JP2008051710W WO2008093861A1 WO 2008093861 A1 WO2008093861 A1 WO 2008093861A1 JP 2008051710 W JP2008051710 W JP 2008051710W WO 2008093861 A1 WO2008093861 A1 WO 2008093861A1
Authority
WO
WIPO (PCT)
Prior art keywords
torque
worm
output shaft
electric power
power transmission
Prior art date
Application number
PCT/JP2008/051710
Other languages
English (en)
Japanese (ja)
Inventor
Toru Segawa
Haruhiko Kiyota
Original Assignee
Nsk Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nsk Ltd. filed Critical Nsk Ltd.
Priority to JP2008556210A priority Critical patent/JP5309997B2/ja
Publication of WO2008093861A1 publication Critical patent/WO2008093861A1/fr

Links

Classifications

    • 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
    • B62D5/0409—Electric motor acting on the steering column
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/22—Toothed members; Worms for transmissions with crossing shafts, especially worms, worm-gears
    • F16H55/24—Special devices for taking up backlash
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H2057/0213—Support of worm gear shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F16H2057/126—Self-adjusting during operation, e.g. by a spring

Definitions

  • the present invention relates to a torque transfer mechanism suitable for being provided in a torque transfer mechanism for transferring torque from an electric motor to a reduction mechanism or the like.
  • the present invention detects the steering torque applied to the steering wheel with a torque sensor, and assist steering torque generated from the electric motor in response to the detected steering torque through the speed reduction mechanism, and the steering mechanism.
  • the present invention relates to an electric power steering apparatus for transmitting power to an output shaft of a motor.
  • an auxiliary steering torque generated from the electric motor in response to a steering torque applied to a steering wheel is steered through a power transmission mechanism including a reduction mechanism. It is transmitted to the output shaft of the mechanism.
  • a worm wheel is coupled to a worm connected to a drive shaft of an electric motor, and the worm wheel is connected to a steering mechanism. It is fitted on the shaft.
  • JP 2002-518242 discloses a motor-assisted steering device in which a motor rotor and an input shaft are connected by a flexible joint.
  • the flexible joint comprises 16 radial bearings. It has a rubber spider with eight identical, circumferentially spaced arms that define a dynamic surface.
  • the hub that supports the motor shaft at the end on the input shaft side is provided with four drive teeth that project axially toward the input shaft.
  • the cup formed at the end of the motor shaft of the input shaft is provided with four drive teeth that project axially toward the motor, and the four drive teeth are bent Engaged between the remaining arms of the fitting. In such a configuration, torque is transmitted from the motor rotor to the input shaft through the flexible joint.
  • the flexible shaft allows the input shaft to move.
  • the contact surface of the member that supports the pivot so as to be able to bias the worm shaft toward the worm wheel side with other members is the same.
  • An electric power steering apparatus is disclosed which is formed by an elastic layer made of an inertia material.
  • the power transmission joint for connecting the output shaft of the electric motor and the ohmic shaft is interposed between the first and second engagement members of the power transmission joint.
  • the power transmission surface of the transmission member is formed by the elastic layer.
  • the present invention has been made in view of the above-mentioned circumstances, and the output shaft of the worm motor drive system is not required to have precision, and the manufacturing cost can be reduced. It is an object of the present invention to provide an electric power steering device capable of obtaining stable performance without being affected by the assembly accuracy of the vehicle.
  • an electric power steering apparatus is characterized in that, in order to transmit an auxiliary steering torque generated from an electric motor to an output shaft of a steering mechanism via a worm reduction gear,
  • the output shaft of the motor and the worm are coupled by a coupling disposed between respective opposite side ends,
  • the side end of the output shaft is provided at a predetermined interval in the circumferential direction, and a torque transmission portion formed of a torque transmission member axially projecting toward the worm is formed, and the side end of the worm
  • the torque receiving portion is formed of a torque receiving member provided at predetermined intervals in the circumferential direction and axially projecting toward the output shaft, and the torque transmitting member and the torque receiving member have a circumferential shape.
  • the force-pulling is an elastic member that intervenes between the torque transmitting portion and the torque receiving portion, and transmits torque between the torque transmitting portion and the torque receiving portion.
  • the elastic member has a portion extending at right angles to the axis, and the torque transmission member is inserted into the portion.
  • a first opening having a torque receiving surface in contact with the transmission member and to which torque is transmitted from the torque transmission member, and the torque receiving member is inserted, and contacts the torque receiving member at the time of torque transmission to receive the torque receiving member.
  • a second opening having a torque transmission surface for transmitting torque to the member;
  • the first opening and the second opening each have a plurality of radially arranged holes.
  • the elastic member forms a central hole connected to the plurality of radially arranged holes in a radiation central portion of the plurality of radially arranged holes.
  • a cylindrical projection formed at the central end of the side end of the output shaft or the side end of the worm at the central hole is inserted and positioned.
  • the elastic member has an annular portion formed in an annular shape on the outer peripheral side of the connecting portion.
  • arm portions protruding in the axial direction are alternately formed at predetermined intervals in the circumferential direction.
  • the coupling is characterized in that it forms a plurality of holes for individually inserting these arm portions, and is made of an elastic body in which a torque transmission portion is formed between the adjacent holes.
  • the coupling has an annular portion formed in an annular shape on the outer peripheral side of the connecting portion.
  • the arm formed at the side end of the output shaft and the side end of the worm extends in a radial direction.
  • the plurality of holes in which the arms are inserted and the plurality of holes of the spring are formed radially.
  • the coupling has a central hole formed in a radial center portion of the radial hole and connected to the radial hole.
  • a cylindrical projection formed at the center of the side end of the output shaft or the side end of the worm is inserted and positioned.
  • the torque transmitting portion of the force plucking includes the side end surface of the output shaft and the side end of the ohmic member.
  • a convex portion is in contact with at least one of the surfaces.
  • the electric power steering apparatus includes a preloading mechanism for biasing the worm to a worm wheel.
  • an electric power steering apparatus wherein: the electric steering wheel is configured to transmit auxiliary steering torque generated from the electric motor to an output shaft of a steering mechanism via a worm reduction gear.
  • the output shaft of the evening and the worm are coupled by a coupling disposed between the respective opposite side ends,
  • first and second connecting members each having a plurality of arms formed to engage with the pull-up
  • the coupling includes a plurality of power transmission members having curved surfaces interposed between the arms and transmitting torque between the first and second connection members.
  • the contact surface of the arm portion with the power transmission member may be configured by a curved surface having a smaller curvature than the power transmission member.
  • the curved surface of the arm portion has a substantially partially spherical recess.
  • the power transmission member is circumferentially connected to the inner diameter side of the annular member, and the annular member is the annular member. It is biased toward the center of the member.
  • the electric power steering apparatus includes a preloading mechanism for biasing the worm to a worm wheel.
  • an electric power steering apparatus comprising: an output shaft of the electric motor for transmitting auxiliary steering torque generated from the electric motor to an output shaft of a steering mechanism via a worm reduction gear.
  • the motor and the worm are coupled by a coupling disposed between the respective opposite side ends,
  • a plurality of axially projecting arms are formed at predetermined intervals in the circumferential direction on surfaces facing each other in the axial direction.
  • First and second connecting members are provided;
  • the arm portions of the first connection member and the arm portions of the second connection member are alternately arranged in the circumferential direction
  • a plurality of power transmission members which are interposed between the adjacent arm portions and transmit torque between the first and second coupling members, are formed in the coupling at predetermined intervals in a circumferential direction,
  • the first and second connection members are provided with a restricting means for restricting the displacement of the power transmission member in the radial direction by the centrifugal force generated by the rotation of the output shaft of the motorized motor. I assume.
  • the respective arm portions of the first and second connection members project in the circumferential direction from the outer diameter side of the surface on the circumferential direction side of the arm portion, and are disposed in the circumferential direction adjacent to the respective arm portions.
  • a convex portion is formed in contact with a portion on the substantially outer diameter side of the power transmission member to restrict displacement of the power transmission member in the radial direction.
  • the coupling has an annular member on the outer side in the radial direction of the power transmission member disposed in the circumferential direction.
  • the power transmission member is integrally connected to the annular member in one-to-one correspondence with a plurality of support portions formed on the inner peripheral side of the annular member, and between the convex portion and the support portion There is always a gap.
  • the coupling has an annular member inward in a radial direction of the power transmission member disposed in the circumferential direction.
  • the power transmission member is integrally connected to the annular member in one-to-one correspondence with a plurality of support portions formed on the outer peripheral side of the annular member, the first connecting member or the second connecting member A cylindrical portion for supporting the annular member is provided on one side.
  • the electric power steering apparatus includes a preloading mechanism for biasing the worm to a worm wheel.
  • the output shaft to be rotationally driven and the input shaft to which the rotational torque of the output shaft is transmitted are powers disposed between the respective opposite side ends.
  • a first connecting member integrally rotatably connected to the output shaft is provided at the side end of the output shaft, and the side end of the input shaft is connected to the input shaft so as to be integrally rotatable.
  • a second connecting member provided between the first and second connecting members,
  • a power transmission member for transmitting torque between the first and second connection members is interposed between the first and second connection members, and the output shaft is provided in the first and second connection members.
  • a restriction means is provided for restricting the radial displacement of the power transmission member due to the centrifugal force generated by the rotation of the motor.
  • the second aspect of the present invention in addition to the effects of the first aspect, it is possible to simplify the connection process between the motor and the motor. Also, the possibility of inhibiting the rocking of the worm can be reduced. In addition, displacement of the power transmission member can be prevented, and even if permanent distortion occurs in the power transmission member, occurrence of guarding can be prevented.
  • FIG. 1A is an overall view showing a cross section of a part of a power assist portion of an electric parking steering apparatus according to a first embodiment of the present invention, and FIG. It is a cross-sectional view enlarging the main part of the
  • FIG. 2A is a view of the worm side connecting portion according to the first embodiment as viewed from the axial direction
  • FIG. 2B is an axial view of the electric motor side connecting portion according to the first embodiment
  • FIG. 2C is a front view of the coupling portion of the coupling according to the first embodiment as viewed from the axial direction
  • FIG. 2D is a modification of the first embodiment
  • FIG. 6 is a front view of the coupling portion of the coupling as viewed from the axial direction.
  • 3A is a perspective view of the worm side connecting portion according to the first embodiment
  • FIG. 3B is a perspective view of the electric motor side connecting portion according to the first embodiment
  • FIG. FIG. 3 is a cross-sectional view taken along line 3 c-3 c in FIG. 2C of the coupling portion of the coupling according to the first embodiment.
  • Fig. 4 shows a connecting portion in a state where the worm side connecting portion and the electric motor side connecting portion are connected via a coupling according to the first embodiment, taken along line 4c-4c in Fig. 2C. It is an expanded sectional view shown corresponding to a section.
  • FIG. 5 is a cross-sectional view of a portion of a power assist portion of the electric power steering apparatus according to the second embodiment.
  • FIG. 6A is a partial perspective view of the connecting structure of the output shaft of the motorized motor and the worm shaft in the second embodiment
  • FIG. 6B is a sectional view taken along the line A-A in FIG. It is the figure seen from.
  • FIG. 7 is a cross-sectional view of a portion of a power assist portion of an electric power steering apparatus according to a third embodiment.
  • FIG. 8 is an exploded perspective view of the connection structure between the output shaft of the electric motor and the worm shaft in the third embodiment.
  • FIG. 9 is a view of the connecting structure portion in the axial direction of the cross section taken along line A_A of FIG. 7 in the third embodiment.
  • FIG. 10 is a view of the linked structure in an axial direction in a cross section corresponding to the line A-A in FIG. 7 in the fourth embodiment.
  • FIG. 1A is an overall view showing a cross section of a part of a power assisting portion of an electric power steering apparatus according to a first embodiment of the present invention
  • FIG. 1B is a cross-sectional view enlarging a main part of FIG. It is a front view.
  • FIG. 2A is a view of the worm side connecting portion as viewed in the axial direction
  • Fig. 2B is a view of the electric motor side connecting portion as viewed in the axial direction
  • Fig. 2C is a view of the first embodiment
  • FIG. 2D is a front view of the coupling portion of the coupling according to the embodiment as viewed from the axial direction
  • FIG. 2D is a front view of the coupling portion of the coupling according to the modification of the first embodiment as viewed from the axial direction.
  • FIG. 3A is a perspective view of the worm side connecting portion
  • FIG. 3B is a perspective view of the electric motor side connecting portion
  • FIG. 3C is a view of the connecting portion of the coupling according to the first embodiment. It is a 3 c- 3 c line sectional view in 2 C.
  • FIG. 4 is a cross-sectional view taken along line 4 c-4 c in FIG. 2 C, showing the connecting portion in the state where the worm side connecting portion and the electric motor side connecting portion are connected via the coupling in the first embodiment. Is an enlarged sectional view corresponding to FIG.
  • An electric motor 1 which is an auxiliary power source of the electric power steering apparatus, is fixed to the housing 2.
  • a worm 3 constituting a worm reduction gear and a worm wheel 4 fitted to the worm 3 are provided.
  • the worm 3 is supported on the housing 2 by two bearings 5, 6.
  • the motor side bearing 5 is capable of rotating the worm 3 and is rockable with the motor side bearing 5 as a fulcrum and is supported so as not to move in the axial direction.
  • the worm side bearing 6 is fitted with a gap between the inner ring 6 a and the worm 3.
  • a preload mechanism 7 Adjacent to the worm side bearing 6, there is provided a preload mechanism 7 for urging the worm 3 in the worm wheel 4 direction (the kneading direction) by the elastic body 7a, and from the tire (not shown) The hitting noise between the gear teeth of worm 3 and worm wheel 4 due to input is suppressed.
  • a detailed description is abbreviate
  • the output shaft 8 of the motorized motor 1 is coupled to the worm 3 via a torque transmission coupling mechanism 20 which will be described in detail later, and transmits torque.
  • Numeral 9 is a torque sensor.
  • the rotation of the worm 3 is reduced via the worm wheel 4 which fits into the worm 3 It is quickly transmitted to the output shaft 1 1.
  • the output shaft 11 is connected to the steering gear of the steering mechanism via a universal joint (not shown), a ground steering shaft and the like.
  • a connecting portion 15 is provided at the stern end 3 a of the worm 3.
  • the connecting portion 15 is formed on the center of the axis on the flat portion 16 radially extending at the motor side end, as shown in FIGS. 2A and 3A, and is axially directed toward the output shaft 8 of the electric motor 1.
  • the flat portion 16 is provided with at least two (three in the illustrated example) arm portions 19 extending substantially radially from the cylindrical portion 17 and axially projecting from the flat portion 16. .
  • the arms 19 are formed on the flat portion 16 at equal intervals in the circumferential direction.
  • a flat torque receiving surface 19a is provided on one of the surfaces on both sides in the circumferential direction of each arm 19 so as to transmit torque with a force pulling 20 described later.
  • the torque receiving surface 19a and the flat portion 16 are substantially perpendicular.
  • the outer diameter of the connecting portion 15 is the same diameter as the bearing press-in portion so as not to hinder the press-in of the motor-side bearing 5 or a small diameter within a range which does not affect the use of the retaining ring 23.
  • a connecting portion 30 is provided at the end of the output shaft 8 facing the motor side end 3 a of the worm 3.
  • the connecting portion 30 is a cylindrical portion axially projecting toward the worm side end portion 3 a at the axial center on the flat portion 32 extending in the radial direction of the shaft end as shown in FIGS. 2A and 3B.
  • the flat portion 32 is provided with at least two (three in the illustrated example) arm portions 36 extending substantially radially from the axial center.
  • the arm portions 36 are formed on the flat portion 32 at equal intervals in the circumferential direction.
  • the connecting portion 30 on the output shaft 8 side is different from the connecting portion 15 on the warm 3 side, and the cylindrical portion 34 at the center of the axis and the arm portion 36 are not connected. Further, the axial length of the cylindrical portion 34 from the flat portion 32 is set to be shorter than the axial length of the arm 36 from the flat portion 32.
  • a torque transmission surface 3 6 a for transmitting torque to the coupling 20 is provided on both sides of the arm 36 in the circumferential direction.
  • the torque transmission surface 3 6 a is a plane substantially perpendicular to the flat portion 32 of the connecting portion 30.
  • the connecting portion 15 and the worm 3, and the connecting portion 30 and the output shaft 8 are respectively integrally molded, but in the case where it is desired to increase the diameter of the connecting portion in consideration of transmission of large torque, , Machining ⁇ If integral molding is difficult due to the convenience of assembly, etc., it may be a separate member. In that case, however, it is necessary to devise a fitting or fixing method such as serrations, press fitting, screwing, welding, etc.
  • the shapes of the arms 19 and the arms 36 may be interchanged with each other. Both may be in the shape of arms 36. That is, 1.
  • the arm of the connecting part 15 has the shape of FIG. 2A, FIG. 3B, and the arm of the connecting part 30 has the shape of FIG. 2B, FIG. 3B as in this embodiment. 2.
  • Both the arm part of the part 15 and the arm part of the connecting part 30 can be combined in three ways, as shown in FIGS. 2B and 3B.
  • the shaft end of the worm 3 configured as described above and the shaft end of the motor output shaft 8 are connected via a coupling 20.
  • the coupling 20 is a cylindrical elastic body as shown in FIGS. 2C and 3C.
  • An axial hole 38 is formed in the axial center of the coupling 20 for positioning the connecting portion 15 and the connecting portion 30.
  • a hole 40 extending substantially radially from the axial hole 38 is formed. Are formed continuously (in the present embodiment, six).
  • the cylindrical portion 17 of the connecting portion 15 is inserted into the axial hole 38 of the coupling 20 from the worm 3 side, and the cylindrical portion 34 of the connecting portion 30 is inserted from the output shaft 8 side. There is. In the radial holes 40, the arms 19 are alternately inserted from the side of the worm 3 and the arms 36 from the output shaft 8 side.
  • the radial holes 40 are formed including the number, phase, and thickness of the arms 19 and the arms 36. Therefore, when arm 19 and arm 36 are inserted, there is no space between torque receiving surface 19 a of arm 19 and torque transmitting surface 36 a of arm 36. It is set to have some or some margin.
  • the generally fan-shaped small pieces 4 2 of the coupling 20, which are surrounded by adjacent radial holes 40, have a function of transmitting torque between the couplings. That is, the torque generated from the motorized motor 1 is transmitted to the arm 36 of the connecting portion 30 of the output shaft 8, and the small piece 42 is pushed from the torque transmitting surface 36 a to the coupling 20. Reportedly.
  • the torque transmitted to the coupling 20 is transmitted through the small piece 4 2 and transmitted to the worm 3 by pressing the torque receiving surface 1 9 a of the arm 1 9 inserted into the adjacent radial hole 40. In this way, the torque generated from the electric motor 1 is transmitted to the worm 3.
  • the arm portion 19 of the connecting portion 15 and the arm portion 36 of the connecting portion 30 are in the form of the combination of the above-described 3 ⁇ , that is, the arm portion 19 of the connecting portion 15 and the connecting portion 30
  • the coupling 20 is, as in the variant of FIG. 2D, an axial bore in which the cylindrical part 34 is inserted.
  • An axial hole 41 into which the arm portion 36 is inserted is formed outward of the axial hole 38 in the radial direction of the axial hole 38 (six in this modification).
  • an annular member 44 is disposed on the outer periphery of the coupling 20 to suppress deformation.
  • the annular member 44 is made of a material such as metal, resin, or the like according to the required rigidity. Further, it is preferable that the annular member 44 be integrally fixed to the elastic material forming the small piece portion 42 by adhesion, slip molding, or the like.
  • the flat portion 16 of the worm 3 is in close contact with one surface in the axial direction of the small piece portion 42 of the coupling 20.
  • the flat portion 32 of the output shaft 8 is in close contact with the other surface in the axial direction of the small piece 42.
  • a convex portion 14 is formed on at least one of two end faces in the axial direction of the small piece portion 42 of the coupling 20.
  • the convex portion 14 is formed on the surface of the small piece portion 42 on the worm 3 side.
  • the convex portion 14 is flat. It is axially compressed by the face portion 16 and the small piece portion 42 to generate a reaction force in the axial direction. By this reaction force, the internal clearance between the bearing 5 and the bearing 6 can be eliminated, and the generation of abnormal noise can be suppressed.
  • connection portions 15 and 30 of both the worm 3 and the output shaft 8 of the electric motor 1 allow eccentricity and swing due to deformation of the elastic body of the coupling 20. Therefore, the accuracy of the output shaft 8 of the worm 3 or the electric motor 1 is not required, the manufacturing cost can be reduced, and stable performance can be obtained without being affected by the assembling accuracy of the electric motor.
  • the preloading mechanism has been described as an electric power steering apparatus with a preloading mechanism as a countermeasure against the tapping noise of the gear tooth surface generated from the displacement of the shaft center of the worm and the shaft center of the output shaft. Regardless of the presence or absence, as described above, eccentricity and oscillation resulting from the drilling accuracy and the assembly accuracy can be suppressed inexpensively.
  • a second embodiment of the present invention will be described. In the second embodiment, a configuration different from the first embodiment will be described. The same reference numerals are used for the same configuration as that of the first embodiment.
  • FIG. 5 is a cross-sectional view of a portion of a power assist portion of the electric power steering apparatus according to the second embodiment.
  • the structure for connecting the output shaft 8 of the motorized motor 1 and the worm 3 is different from that of the first embodiment.
  • FIG. 6A is an exploded perspective view of the connecting structure of the output shaft 8 of the electric motor 1 and the worm 3 in the present embodiment
  • FIG. 6B is a sectional view taken along the line A-A in FIG. It is the figure seen from.
  • a first connecting member 50 is provided at an end 8 a of the motor output shaft 8 on the worm 3 side.
  • the first connecting member 50 includes a flange portion 51 disposed on the outer peripheral side of the output shaft 8, and a plurality of arm portions 52 formed on the flange portion 51.
  • the flange portion 51 is formed with a center hole 53 through which the end 8a of the output shaft 8 on the worm 3 side is passed.
  • the central hole 53 is formed in a cylindrical fitting portion 54 axially projecting toward the worm 3.
  • the end 8a on the worm 3 side of the output shaft 8 is fitted in the fitting portion 54, and the output shaft 8 and the first connecting member 50 are connected to rotate integrally.
  • the plurality of arm portions 52 of the flange portion 51 are formed on the surface 55 on the worm 3 side so as to axially project toward the worm 3 side.
  • three arms 5 2 are formed.
  • the arm portions 52 are formed on the surface 5 5 on the worm 3 side of the flange portion 51 at equal intervals in the circumferential direction.
  • the arm 52 protrudes more than the fitting portion 54 toward the worm 3 side.
  • the inner peripheral side of the arm portion 52 is continuous with the outer periphery of the fitting portion 54, and extends from the fitting portion 54 in the radial direction to a position having the same diameter as the outer periphery of the flange portion 51.
  • a torque transmission surface 52a is formed on both sides of the arm 52 in the circumferential direction.
  • the torque transmitting surface 52 a is a curved surface having a predetermined curvature which is recessed inward of the arm 52.
  • the curved surface of the torque transfer surface 5 2 a may be formed into a substantially partially spherical depression.
  • the torque transmission surface 52a contacts the power transmission member 65 of the coupling 60 described later to transmit torque.
  • the second connecting member 70 having the same configuration as the first connecting member 50 is also connected to the end 3 a on the output shaft 8 side of the worm 3, and the worm 3 and the second connecting member 70 are integrated. Rotate.
  • the second connecting member 70 is, as shown in FIG. 6A, similarly to the first connecting member 50, the flange portion 71, the central hole 73, and the central hole 73 toward the output shaft 8 And an extending fitting portion 74.
  • a plurality of arms 72 are formed projecting on the surface 7 5 on the motor output shaft 8 side of the flange 7 1, and torque receiving surfaces 7 2 a are formed on both sides of the arm 72 in the circumferential direction. Is formed.
  • the first connecting member 50 of the output shaft 8 and the second connecting member 70 of the worm 3 are connected via a coupling 60.
  • the first connecting member 50 and the second connecting member 70 are formed on the side where the respective arm portions 52 and 72 are formed.
  • the arm portions 52 of the first connecting member 50 and the arm portions 72 of the second connecting member 70 are disposed in such a manner as shown in FIG. 6B. As shown, they are arranged alternately in the circumferential direction.
  • the first connecting member 50 and the second connecting member 70 are made of a highly rigid material such as metal.
  • the coupling 60 includes a plurality of power transmission members 65 that transmit torque between the first connection member 50 and the second connection member 70, and a power transmission member 65. It comprises a short cylindrical annular member 66 connected to the inner peripheral side.
  • the power transmission member 65 is made of a relatively low-rigidity elastic material and is formed into a substantially spherical shape.
  • the material of the power transmission member 65 is preferably a rubber such as ditolyl rubber, silicone rubber, urethane rubber, an elastomer such as polyurethane, or a resin, but not limited thereto.
  • the power transmission member 65 is disposed between the arms 52 and 72 of the first and second connection members 50 and 70 alternately arranged in the circumferential direction. It is done. More specifically, the torque transmission surface 5 2 a and the torque receiving surface 7 2 a that face each other in the circumferential direction of the arm portion 52 of the adjacent first connection member 50 and the arm portion 72 of the second connection member 70. It is arranged with a clearance in between. In the present embodiment, since three arms are formed on each of the first connection member 50 and the second connection member 70, six power transmission members 65 are disposed. .
  • the annular members 66 are, as shown in FIG. 6B, in the radial direction of the arms 52 of the first connection member 50 and the arms 72 of the second connection member 70 alternately arranged in the circumferential direction. It is located outside. On the inner circumferential side of the annular member 66, a plurality of support portions 67 projecting toward the center of the annular member 66 are provided at equal intervals in the circumferential direction. A power transmission member 65 is connected to an end of the support member 67 located on the center side of the annular member 66. Since the coupling 60 has such a configuration, it can not rotate relative to the first and second coupling members 50, 70. The annular member 66 pre-loads the coupled power transmission member 65 in the central direction of the annular member 66 in the assembled state. In the present embodiment, the annular member 66, the power transmission member 65, and the support portion 6 7 And are integrally formed.
  • the torque transmission path is as follows. That is, the torque generated from the electric motor 1 is transmitted to the arm 52 of the first connecting member 50 connected to the output shaft 8, and the torque transmission surface 52 a of the arm 52 is coupled to the coupling 6.
  • the power transmission member 0 is transmitted to the coupling 60 by pushing the power transmission member 6 5.
  • the torque transmitted to the coupling 60 is transmitted to the power transmission member 65 and transmitted to the worm 3 in such a manner as to push the torque receiving surface 7 2 a of the arm 7 2 of the second transmission member 70. In this way, the torque generated from the electric motor 1 is transmitted to the worm 3.
  • the power transmission member 65 is formed into a substantially spherical shape as described above. Therefore, the portion of the power transmission member 65 that contacts the torque transmission surface 5 2 a of the arm 52 and the torque receiving surface 7 2 a of the arm 72 is partially spherical.
  • the torque transmitting surface 52a and the torque receiving surface 72a formed on the arms 52 and 72 of the first and second connecting members 50 and 70 are the arms 52 and 7 as described above. It is a curved surface that is recessed toward the inside of 2.
  • the curved surface constituting the torque transfer surface 52a and the torque receiving surface 72a is a curved surface having a curvature smaller than that of the power transfer member 65 of the coupling 60. Since the power transmission member 65, the torque transmission surface 52a and the torque receiving surface 72a have such a configuration, the power transmission member 65, the torque transmission surface 52a and the torque receiving surface 72a and The contacts are in surface contact with each other.
  • eccentricity and rocking of the motor output shaft and the worm are permitted by the inertia deformation of the power transmission member of the coupling. Therefore, the accuracy of the worm and motor output shaft is not required, the manufacturing cost can be reduced, and stable performance can be obtained without being affected by the assembly accuracy of the electric motor.
  • the contact state between the power transmission member and the torque transmission surface and the torque receiving surface is stabilized.
  • the allowable angle for the phasing of the coupling in the connection process between the motorized motor and the worm is relaxed.
  • the connection process between the electric motor and the worm can be simplified.
  • the torque transmitting surface and the torque receiving surface respectively formed on the arm portions of the first and second connecting members are curved surfaces having a curvature smaller than that of the power transmitting member of the coupling. Therefore, when high torque is transmitted, the contact area with the power transmission member can be increased, and stress can be relieved. When there is no torque transmission, or when transmitting low torque, the contact area is small, so the change in the elastic reaction force against the interference is small, and it is difficult for frictional resistance to occur. Therefore, the possibility of inhibiting the rocking of the worm is reduced.
  • the inertia reaction force of the power transmission member generates a force in the direction perpendicular to the torque transmission surface of the arm or the contact surface of the torque receiving surface with the power transmission member.
  • the contact surface between the power transmission member and the torque transmission surface or the torque receiving surface is a flat surface, relative torsion occurs between the motor output shaft and the torque so that the contact surfaces are not parallel to each other.
  • the force is applied to the power transmission member in the radial direction to cause displacement.
  • the contact surface is a curved surface and has a curvature, the elastic reaction of the power transmission member is directed substantially in the central direction of the power transmission member.
  • the contact surface of the arm portion or the contact surface of the torque receiving surface with the power transmission member is configured as a substantially partial spherical recess, the power transmission member is displaced in the worm axial direction. It becomes difficult.
  • the annular member of the coupling Since the extension member is preloaded in the center direction of the annular member, the wedge effect between the curved surfaces on which the power transmission member is disposed does not cause the generation of gestation.
  • the third embodiment is substantially the same as the second embodiment, so a configuration different from the second embodiment will be described.
  • the same symbols are used for the same configuration as the second embodiment.
  • FIG. 7 is a cross-sectional view of a portion of a power assist portion of an electric power steering apparatus according to a third embodiment.
  • FIG. 8 is an exploded perspective view of the connection structure between the output shaft 8 and the worm 3 of the electric motor 1 according to the third embodiment.
  • FIG. 9 is a view of the connecting structure portion in the axial direction taken along line A-A of FIG. 7 in the third embodiment.
  • an end 8a on the worm 3 side of the motor output shaft 8 and an end 3a on the output shaft 8 side of the worm 3 respectively have the first connection as in the second embodiment.
  • a member 150 and a second connecting member 170 are provided.
  • the first connecting member 150 integrally rotates with the output shaft 8
  • the second connecting member 1 70 integrally rotates with the worm 3.
  • the first connecting member 150 and the second connecting member 170 are connected by a coupling 160 as shown in FIG.
  • the configuration of the coupling 160 is the same as that of the coupling 60 in the second embodiment, and can not be rotated relative to the first and second coupling members 150 and 170. There is.
  • the first connecting member 150 is, as shown in FIG. 8, a flange portion 15 1 disposed on the outer peripheral side of the output shaft 8 and a plurality of arm portions 1 5 2 formed on the flange portion 15 1. And have.
  • the flange portion 15 1 is formed with a central hole 1 5 3 through which the end 8 a of the output shaft 8 on the worm 3 side is inserted.
  • the hole 15 3 3 is formed in a cylindrical fitting 1 5 4 axially projecting toward the worm 3.
  • the end 8 a of the worm 3 side of the output shaft 8 is fitted in the fitting portion 1 54.
  • the plurality of arm portions 1 5 2 of the flange portion 1 5 1 are formed so as to project in the axial direction toward the worm 3 side on the surface 1 5 5 on the worm 3 side.
  • the arm Three parts 15 2 are formed.
  • the arms 1 52 are formed on the surface 15 5 on the worm 3 side of the flange 1 5 1 at equal intervals in the inner circumferential direction.
  • the arm portion 152 protrudes more than the fitting portion 154 toward the worm 3 side.
  • the inner peripheral side of the arm portion 152 is continuous with the outer periphery of the fitting portion 154, and extends from the fitting portion 154 in the radial direction to a position having the same diameter as the outer periphery of the flange portion 151. ing.
  • Torque transmitting surfaces 1 5 2 a are formed on both sides of the arm 1 5 2 in the circumferential direction.
  • the torque transmitting surface 1 52 2 a is a curved surface having a predetermined curvature which is recessed inward of the arm portion 1 5 2.
  • the curved surface of the torque transmission surface 1 52 2 a may be formed into a substantially partially spherical depression.
  • the torque transmission surface 1 5 2 a contacts the power transmission member 1 6 5 of the coupling 1 6 0 to perform torque transmission.
  • the second connecting member 170 is, similarly to the first connecting member 150, the flange portion 1 71, the central ridge L 1 7 3 and the periphery of the central hole 1 7 3 And a fitting portion 1 74 that extends toward the output shaft 8.
  • a plurality of arms 1 72 are formed projecting on the surface 1 7 5 on the side of the output shaft 8 of the flange 1 7 1, and torque receiving surfaces 1 are formed on both sides of the arms 1 2 2 in the circumferential direction. 7 2 a is formed.
  • the first connecting member 150 of the output shaft 8 and the second connecting member 170 of the ohmic 3 are connected via a coupling 160.
  • the first connecting member 150 and the second connecting member 170 are such that the surfaces 15 5 and 17 5 of the flange on the side on which the respective arms 1 52 and 1 72 are formed face each other. As shown in FIG. 9, the arm portions 152 of the first connecting member 150 and the arm portions 172 of the second connecting member 150 are alternately arranged in the circumferential direction. It is arranged as.
  • the first connecting member 150 and the second connecting member 170 are made of a highly rigid material such as metal.
  • a portion of the torque transmitting surface 1 52 2 a formed on the arm portion 1 52 of the first connecting member 150 is protruded in the circumferential direction to form a convex portion 180.
  • the convex portion 180 projects toward a support portion 167 that supports the power transmission member 1 6 5 on the annular member 1 6 6.
  • the surface 180a of the first connecting member 150 of the convex portion 180 on the axial center side is near the connecting portion between the power transmission member 165 and the support portion 167, and is substantially spherical.
  • the power transmission member 165 is in contact with the power transmission member 165 at a portion that faces the inner periphery of the annular member 166 substantially in the radial direction. That is, a convex portion 1 8 0 is formed between the portion of the power transmission member 16 5 facing the inner peripheral side of the annular member 16 6 in the substantially radial direction and the inner peripheral side of the annular member 1 66. Is located.
  • the end face 1800 on the circumferential direction of the convex portion 180 does not contact the support portion 167 connecting the power transmission member 16.5 and the annular member 1660. Therefore, a gap 182 is present between the tip end surface 1803 of the convex portion 180 and the support portion 167. This gap 182 is set to exist even when transmitting the torque of the maximum specification.
  • the portion of the torque receiving surface 1 72 2a formed on the arm portion 1 72 of the second connecting member 1 70 is also protruded in the circumferential direction to be convex like the first connecting member 150. It forms part 190.
  • the end face 1 90 b on the circumferential direction side of the convex portion 1 90 formed on the arm 1 72 of the second connecting member 1 7 0 also has the power transmission member 1 6 5 and the annular member 1 6 6 There is no contact with the support part 167 to be connected. Therefore, a gap 192 is present between the end face 1 90 b of the convex portion 190 of the second connecting member 1 70 and the support portion 1 6 7. This clearance 192 is set to exist even when transmitting the maximum specification torque.
  • the power transmission member 1 65 is a torque transmission surface 1 5 2 a of the first connection member 1 50 in the circumferential direction of the first and second connection members 1 5 0 and 1 7 0 in the circumferential direction.
  • the second connecting member 1 70 respectively in contact with the torque receiving surface 1 7 2 a of the first connecting member 1 5 0 in contact with the annular member 1 6 6 substantially radially.
  • the torque of the power transmission member 16 is the torque of the first connection member 150
  • the first connecting member 1 is in contact with the transmission surface 15 2 2 a, the torque receiving surface 1 7 2 a of the second connecting member 1 70, and the convex portion 1 80 and the convex portion 1 90. Torque is transmitted between the contact surfaces of 50 and the second connecting member 1 70.
  • the first connection member 1 5 0 is provided on the side of the power transmission member 1 6 that faces the annular member 1 6 6 in the substantially radial direction.
  • the present embodiment is not limited to the above-described electric power steering apparatus, but is a member used for a rotation transmission mechanism, which wants to restrict radial displacement due to centrifugal force. Is also applicable.
  • the fourth embodiment is substantially the same as the second embodiment and the third embodiment, and so a configuration different from these embodiments will be described.
  • the same reference numerals are used for the same configuration as the second and third embodiments.
  • FIG. 10 is a view of the linked structure in an axial direction in a cross section corresponding to the line A-A in FIG. 7 in the fourth embodiment.
  • a first connecting member 20 0 and a second connecting member 2 20 are provided at an end 8 a of the worm 3 side of the motor output shaft 8 and an end 3 a of the output shaft 8 side of the worm 3 respectively. Is provided.
  • the first connecting member 200 rotates integrally with the output shaft 8
  • the second connecting member 220 rotates integrally with the ohm 3.
  • the configurations of the first connecting member 200 and the coupling 230 are different from those of the second embodiment.
  • a cylindrical portion 240 projecting in the axial direction is formed.
  • the cylindrical portion 240 is disposed radially inward of the plurality of arm portions 202 of the first connecting member 200 disposed at predetermined intervals in the circumferential direction.
  • the outer peripheral side of the cylindrical portion 240 and the inner peripheral side of the arm portion 202 are not continuous, and the cylindrical portion 240 projects in the same direction as the arm portion 202 toward the worm 3 direction.
  • the configuration is different from the fitting portion 54 and the arm portion 52 in the second embodiment.
  • the end 8 a of the output shaft 8 is internally fitted on the inner peripheral side of the cylindrical portion 240.
  • the configuration of the second connecting member 220 is the same as the configuration of the second connecting member 72 in the second embodiment.
  • the first connecting member 200 and the second connecting member 220 are connected by a coupling 230 as shown in FIG.
  • the coupling 230 in the present embodiment includes a plurality of power transmission members that perform torque transmission between the first connection member 200 and the second connection member 220. 5 and an annular member 2 32 in which a power transmission member 2 6 5 is linked on the outer peripheral side.
  • a cylindrical portion 2 40 formed in the first connecting member 200 is penetrated on the inner peripheral side of the annular member 2 32 to support the annular member 2 32.
  • the annular members 2 32 are radially inward of the arm portions 2 0 2 of the first connection member 2 0 0 and the arm portions 2 2 2 of the second connection member 2 0 2 arranged alternately in the circumferential direction.
  • a plurality of support portions 223 projecting toward the outer diameter direction of the annular member 232 are provided at equal intervals in the circumferential direction.
  • a power transmission member 2 6 5 is connected to each of the support portions 2 3 5 at an end portion of the annular member 2 3 2 that is radially outward.
  • the coupling 230 can not rotate relative to the first and second coupling members 200 0 and 220.
  • the end portion 2 0 2 b of the arm portion 2 0 2 formed on the first connecting member 2 0 0 is not formed with a portion corresponding to the convex portion 1 8 0 in the third embodiment.
  • a gap 2 3 8 exists between the end 2 0 0 2 b near the inner peripheral side of the arm 2 0 2 2 and the support 2 3 5. This clearance 2 3 8 is set to exist even when transmitting the maximum specification torque.
  • the end 22 2 b of the arm 22 2 formed on the second connecting member 220 is also not in contact with the support 23 5 in the same manner.
  • a gap 2 4 8 exists between the end 2 2 2 b closer to the inner circumferential side and the support portion 2 3 5.
  • the transmission member 2 6 5 is a torque transmission surface 2 0 2 a formed on the arm 2 0 2 of the first connection member 2 0 0 and a torque formed on the arm 2 2 2 of the second connection member 2 2 0
  • the torque is transmitted each time by contacting approximately the same place on each of the transmission surfaces 22 2 a.
  • this embodiment is not limited to the above-described electric power steering device, but may be any member used in the rotation transmission mechanism for restricting radial displacement due to centrifugal force. It is applicable.

Landscapes

  • 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)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Gear Transmission (AREA)

Abstract

L'invention concerne un dispositif de direction de puissance électrique, dans lequel l'arbre de sortie d'un moteur électrique et une vis sans fin reliés par un dispositif d'accouplement. A la partie d'extrémité latérale de vis sans fin de l'arbre de sortie de moteur et à la partie d'extrémité latérale de l'arbre de sortie de moteur de la vis sans fin, sont formées de façon alternée des parties de bras, qui sont disposées à un intervalle prédéterminé dans une direction périphérique sur les faces opposées entre elles dans une direction axiale et qui font saillie dans la direction axiale. Le dispositif d'accouplement est fait à partir d'un élément élastique, qui a une pluralité de trous formés pour introduire ces parties de bras individuellement et qui a des parties de transmission de couple formées entre les trous adjacents.
PCT/JP2008/051710 2007-01-30 2008-01-29 Dispositif de direction de puissance électrique WO2008093861A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2008556210A JP5309997B2 (ja) 2007-01-30 2008-01-29 電動パワーステアリング装置

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2007019599 2007-01-30
JP2007-019599 2007-01-30
JP2007319900 2007-12-11
JP2007-319900 2007-12-11

Publications (1)

Publication Number Publication Date
WO2008093861A1 true WO2008093861A1 (fr) 2008-08-07

Family

ID=39674162

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2008/051710 WO2008093861A1 (fr) 2007-01-30 2008-01-29 Dispositif de direction de puissance électrique

Country Status (2)

Country Link
JP (3) JP5309997B2 (fr)
WO (1) WO2008093861A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010048355A (ja) * 2008-08-22 2010-03-04 Nsk Ltd 弾性軸継手及び電動式パワーステアリング装置
WO2011066520A1 (fr) * 2009-11-30 2011-06-03 Baldor Electric Company Ensemble de couplage souple a elements de transmission de couple incorpores
JP2011156968A (ja) * 2010-02-01 2011-08-18 Jtekt Corp 継手および電動パワーステアリング装置
JP2013144490A (ja) * 2012-01-13 2013-07-25 Honda Motor Co Ltd 電動パワーステアリング装置
EP2532908B1 (fr) * 2011-06-08 2014-06-11 Jtekt Europe Dispositif d'accouplement entre moteur et réducteur de direction assistée électrique de véhicule automobile
WO2015178341A1 (fr) * 2014-05-20 2015-11-26 日本電波工業株式会社 Sonde à ultrasons
CN108372880A (zh) * 2017-02-01 2018-08-07 株式会社万都 电动助力转向设备的减速器
WO2019002184A1 (fr) * 2017-06-27 2019-01-03 Thyssenkrupp Presta Ag Procédé destiné au montage d'un accouplement de direction de véhicule automobile au moyen d'un soudage par ultrasons

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6181021B2 (ja) * 2014-09-24 2017-08-16 本田技研工業株式会社 電動パワーステアリング装置
JP7221677B2 (ja) * 2018-12-20 2023-02-14 Ｔｏｙｏ Ｔｉｒｅ株式会社 弾性カップリング

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4816427Y1 (fr) * 1970-06-16 1973-05-10
JPS54103444U (fr) * 1977-12-29 1979-07-20
JP2002242950A (ja) * 2000-12-12 2002-08-28 Asa Denshi Kogyo Kk 軸継手
JP2006083953A (ja) * 2004-09-16 2006-03-30 Nok Corp トルク伝達装置
JP2006175891A (ja) * 2004-12-20 2006-07-06 Favess Co Ltd 電動パワーステアリング装置
JP2006177505A (ja) * 2004-12-24 2006-07-06 Oiles Ind Co Ltd 電動式パワーステアリング装置用の軸連結機構
JP2006342886A (ja) * 2005-06-09 2006-12-21 Nabeya Bi-Tech Kk 撓み軸継手

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4890041U (fr) * 1972-02-07 1973-10-30
DE2211512A1 (de) * 1972-03-10 1973-10-18 Barth Harald Elastische klauenkupplung mit zwei im wesentlichen gleich ausgebildeten kupplungsscheiben
JPS55181026U (fr) * 1979-06-15 1980-12-26
JPS6081320U (ja) * 1983-11-09 1985-06-05 三木プーリ株式会社 スパイダ−カツプリング
JPH0288027U (fr) * 1988-12-27 1990-07-12
GB9812844D0 (en) * 1998-06-16 1998-08-12 Lucas Ind Plc Improvements relating to electrical power assisted steering
US6123620A (en) * 1998-08-18 2000-09-26 Brunswick Corporation Multirate coupler with improved vibration isolation capability
JP2004068943A (ja) * 2002-08-07 2004-03-04 Nok Corp 軸継手
JP4007159B2 (ja) * 2002-10-30 2007-11-14 株式会社ジェイテクト 電動パワーステアリング装置及びジョイント
CN100411934C (zh) * 2002-12-09 2008-08-20 日本精工株式会社 电动助力转向装置
JP4385286B2 (ja) * 2004-01-29 2009-12-16 株式会社ジェイテクト 電動パワーステアリング装置
JP2005319922A (ja) * 2004-05-10 2005-11-17 Koyo Seiko Co Ltd 電動パワーステアリング装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4816427Y1 (fr) * 1970-06-16 1973-05-10
JPS54103444U (fr) * 1977-12-29 1979-07-20
JP2002242950A (ja) * 2000-12-12 2002-08-28 Asa Denshi Kogyo Kk 軸継手
JP2006083953A (ja) * 2004-09-16 2006-03-30 Nok Corp トルク伝達装置
JP2006175891A (ja) * 2004-12-20 2006-07-06 Favess Co Ltd 電動パワーステアリング装置
JP2006177505A (ja) * 2004-12-24 2006-07-06 Oiles Ind Co Ltd 電動式パワーステアリング装置用の軸連結機構
JP2006342886A (ja) * 2005-06-09 2006-12-21 Nabeya Bi-Tech Kk 撓み軸継手

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010048355A (ja) * 2008-08-22 2010-03-04 Nsk Ltd 弾性軸継手及び電動式パワーステアリング装置
WO2011066520A1 (fr) * 2009-11-30 2011-06-03 Baldor Electric Company Ensemble de couplage souple a elements de transmission de couple incorpores
JP2011156968A (ja) * 2010-02-01 2011-08-18 Jtekt Corp 継手および電動パワーステアリング装置
EP2532908B1 (fr) * 2011-06-08 2014-06-11 Jtekt Europe Dispositif d'accouplement entre moteur et réducteur de direction assistée électrique de véhicule automobile
JP2013144490A (ja) * 2012-01-13 2013-07-25 Honda Motor Co Ltd 電動パワーステアリング装置
WO2015178341A1 (fr) * 2014-05-20 2015-11-26 日本電波工業株式会社 Sonde à ultrasons
JP2015217208A (ja) * 2014-05-20 2015-12-07 日本電波工業株式会社 超音波探触子
US10463342B2 (en) 2014-05-20 2019-11-05 Nihon Dempa Kogyo Co., Ltd. Ultrasonic transducer
CN108372880A (zh) * 2017-02-01 2018-08-07 株式会社万都 电动助力转向设备的减速器
US11173950B2 (en) * 2017-02-01 2021-11-16 Mando Corporation Reducer of electric power-assisted steering apparatus
WO2019002184A1 (fr) * 2017-06-27 2019-01-03 Thyssenkrupp Presta Ag Procédé destiné au montage d'un accouplement de direction de véhicule automobile au moyen d'un soudage par ultrasons

Also Published As

Publication number Publication date
JP2013126869A (ja) 2013-06-27
JP2013121839A (ja) 2013-06-20
JPWO2008093861A1 (ja) 2010-05-20
JP5561388B2 (ja) 2014-07-30
JP5309997B2 (ja) 2013-10-09

Similar Documents

Publication Publication Date Title
WO2008093861A1 (fr) Dispositif de direction de puissance électrique
JP4196831B2 (ja) 電動パワーステアリング装置
JP4107326B2 (ja) 電動パワーステアリング装置
JP3891747B2 (ja) 電動式舵取装置
JP4221825B2 (ja) 電動式舵取装置
CN108372880B (zh) 电动助力转向设备的减速器
WO2011077670A1 (fr) Mécanisme d'accouplement d'arbre
JP2014092187A (ja) トルク伝達用継手及び電動式パワーステアリング装置
JP2017036767A (ja) 軸連結構造および電動パワーステアリング装置
JP4980173B2 (ja) 電動パワーステアリング装置の軸継手
JP2006283810A (ja) 弾性軸継手
JP5131054B2 (ja) 弾性軸継手及び電動式パワーステアリング装置
JP4985453B2 (ja) 電動式パワーステアリング装置
WO2012086678A1 (fr) Direction électrique
JP5157666B2 (ja) 弾性軸継手及び電動式パワーステアリング装置
JP7404688B2 (ja) ウォーム減速機および電動アシスト装置
JP2013185667A (ja) 電動パワーステアリング装置
JP5181747B2 (ja) 電動式パワーステアリング装置
JP2008260471A (ja) 電動式パワーステアリング装置
JP2010048355A (ja) 弾性軸継手及び電動式パワーステアリング装置
JP4619662B2 (ja) ステアリング装置用固定式等速自在継手
JP2015113051A (ja) パワーステアリング装置
JP2004249844A (ja) 電動パワーステアリング装置
KR100951997B1 (ko) 전동식 동력조향장치의 커플링
JPH11291925A (ja) 電動式パワーステアリング装置

Legal Events

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

Ref document number: 08704389

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2008556210

Country of ref document: JP

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 08704389

Country of ref document: EP

Kind code of ref document: A1