WO2016171092A1 - トルク伝達用継手及びウォーム減速機 - Google Patents
トルク伝達用継手及びウォーム減速機 Download PDFInfo
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- WO2016171092A1 WO2016171092A1 PCT/JP2016/062179 JP2016062179W WO2016171092A1 WO 2016171092 A1 WO2016171092 A1 WO 2016171092A1 JP 2016062179 W JP2016062179 W JP 2016062179W WO 2016171092 A1 WO2016171092 A1 WO 2016171092A1
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- Prior art keywords
- cup
- driven
- circumferential
- drive
- worm
- Prior art date
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Classifications
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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
- F16D3/54—Couplings comprising a chain or strip surrounding two wheels arranged side by side and provided with teeth or the equivalent
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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
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/02—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for connecting two abutting shafts or the like
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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
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
-
- 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
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/18—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts the coupling parts (1) having slidably-interengaging teeth
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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
- F16D3/72—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 with axially-spaced attachments to the coupling parts
- F16D3/74—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 with axially-spaced attachments to the coupling parts the intermediate member or members being made of rubber or other rubber-like flexible material
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- 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
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- 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
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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
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
- F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
Definitions
- the torque transmission joint of the present invention is incorporated in various mechanical devices and transmits torque between the drive shaft and the driven shaft.
- the worm speed reducer of the present invention is incorporated in, for example, an electric power steering device.
- a power steering device is widely used as a device to reduce the force required for the driver to operate the steering wheel when giving a steering angle to the steered wheels (usually the front wheels except for special vehicles such as forklifts).
- an electric power steering device that uses an electric motor as an auxiliary power source has also started to spread in recent years.
- auxiliary power of the electric motor is applied to the steering shaft that rotates as the steering wheel is operated or a member that is displaced as the steering shaft rotates through the reduction gear.
- the direction of the auxiliary power applied from the electric motor is the same as the force applied from the steering wheel.
- a worm speed reducer is generally used.
- a worm that is rotationally driven by an electric motor and a worm wheel mesh with each other.
- the worm wheel rotates together with a rotating shaft that is a member that is engaged with a steering shaft or a member that is displaced along with the rotation of the steering shaft so that power can be transmitted.
- the auxiliary power of the electric motor can be transmitted to the rotating shaft.
- an unpleasant noise called a rattling noise caused by backlash existing in the meshing part of the worm and the worm wheel when changing the rotation direction of the rotating shaft. May occur.
- FIG. 20 to 21 show an example of the electric power steering apparatus described in Patent Document 1.
- FIG. A front end portion of the steering shaft 2 that is rotated in a predetermined direction by the steering wheel 1 is rotatably supported inside the housing 3, and the worm wheel 4 is fixed to this portion.
- worm teeth 6 are provided at the axially intermediate portion of the worm 8.
- the coil spring 11 presses the worm teeth 6 of the worm 8 toward the teeth 5 of the worm wheel 4 via the pressing piece 10. With such a configuration, backlash between the worm teeth 6 and the tooth portions 5 is suppressed, and generation of rattling noise is suppressed.
- a spline hole 13 is formed at the base end of the worm 8 in order to couple the tip of the output shaft 12 of the electric motor 7 and the base end of the worm 8 so that torque can be transmitted. Yes.
- the spline hole 13 opens toward the base end surface of the worm 8.
- a spline shaft portion 14 is formed at the distal end portion of the output shaft 12. Then, the spline shaft portion 14 and the spline hole 13 are spline-engaged, so that the output shaft 12 and the worm 8 are coupled so as to transmit torque.
- the coupling portion (spline engagement) between the distal end portion of the output shaft 12 and the proximal end portion of the worm 8
- No abnormal noise occurs in the joint section.
- the worm teeth 6 of the worm 8 are elastically pressed toward the tooth portions 5 of the worm wheel 4 by the coil spring 11, and backlash between the worm teeth 6 and the tooth portions 5 is prevented.
- the backlash of the spline engaging portion cannot be completely eliminated and it is difficult to prevent the generation of abnormal noise.
- Patent Document 2 describes a structure in which the swing displacement of the worm shaft can be made smooth by connecting the output shaft of the electric motor and the worm shaft via a metal-made cylindrical power transmission member. .
- spline shaft portions male splines
- the worm shaft and the electric motor Backlash exists in each spline engaging portion of each spline hole (female spline) provided at each end of the output shaft. For this reason, when changing the rotation direction of the rotating shaft, there is a possibility that abnormal noise is generated.
- the present invention can smoothly transmit torque between the drive shaft and the driven shaft even if the central axes of the drive shaft and the driven shaft are not coincident with each other. It is possible to realize a torque transmission joint that can easily prevent noise from being generated between the drive shaft and the driven shaft.
- the torque transmission joint and the torque transmission joint of the worm reducer according to the present invention are arranged between one axial end of the drive shaft and the other axial end of the driven shaft, which are arranged in series with respect to the axial direction.
- the torque is transmitted by the motor, and includes a coupling, a drive side transmission unit, and a driven side transmission unit.
- the coupling is formed on one of the inner and outer peripheral surfaces in the radial direction (in the case where the one peripheral surface is the inner peripheral surface, radially inward. Is provided with a cup-side concavo-convex portion formed by arranging cup-side convex portions projecting radially outward.
- the drive-side transmission portion is provided directly on one end of the drive shaft in the axial direction or via another member. Of the inner and outer peripheral surfaces, the drive-side transmission portion is radially disposed on the peripheral surface facing the cup-side uneven portion. When the peripheral surface facing the cup-side uneven portion is the outer peripheral surface, the drive-side convex portions projecting radially outward (or radially inward when the peripheral surface is also the inner peripheral surface) The driving side uneven portion is provided by being arranged on the surface.
- the driven-side transmission portion is provided directly on the other axial end portion of the driven shaft or via another member, and has a diameter on a peripheral surface facing the cup-side uneven portion of both the inner and outer peripheral surfaces.
- the driven-side convex portion projecting in the direction (radially outward when the circumferential surface facing the cup-side irregular portion is an outer circumferential surface, and radially inward when the circumferential surface is the inner circumferential surface)
- Driven side uneven portions are provided at a plurality of locations in the circumferential direction.
- each drive-side convex portion is in a state in which the central axes of the drive shaft and the driven shaft are aligned with each other.
- One end in the axial direction of the side surfaces and the circumferential side surface of each cup-side convex portion are brought into contact or close to each other without rattling in the circumferential direction.
- the circumferential side surface of each cup-side convex portion When implementing the torque transmission joint of the present invention as described above, the circumferential side surface of each cup-side convex portion, the width dimension in the circumferential direction of each cup-side convex portion is the largest in the axial intermediate portion, Inclination in a direction that decreases as it goes toward both ends in the axial direction (inclination in a direction in which the amount of protrusion in the circumferential direction decreases as it approaches the end in the axial direction).
- the circumferential side surface of each of the cup-side convex portions may be a crowning shape having a circular arc shape when viewed from the radial direction, or a tapered shape that is also linear. it can.
- a flat surface portion parallel to each other may be provided in the axial intermediate portion of both side surfaces in the circumferential direction of each cup-side convex portion, and a tapered surface portion having a linear shape when viewed from the radial direction may be provided at both axial end portions.
- the continuous portion between the flat surface portion and the tapered surface portion is continuous by a convex curved surface having an arcuate cross section.
- both side surfaces in the circumferential direction of the convex portions on the driving side and the driven side can be flat surfaces parallel to each other, and the configuration of the invention described in claim 3 described later is adopted. You can also do things.
- each drive-side convex portion is inclined such that the width dimension of each drive-side convex portion in the circumferential direction is the largest in the axial middle portion and decreases toward the both axial end portions.
- the circumferential side surface of each driven-side convex portion is inclined in such a direction that the width dimension in the circumferential direction of each driven-side convex portion is the largest in the intermediate portion in the axial direction and becomes smaller toward the both end portions in the axial direction.
- the circumferential side surfaces of the respective convex portions on the driving side and the driven side have a circular shape when viewed from the radial direction, a crowning shape, or a tapered shape that is also linear. Can be.
- a tapered surface portion that is provided with flat surface portions parallel to each other in the axial direction on both sides in the circumferential direction of the respective convex portions on the driving side and the driven side, and that the shape viewed from the radial direction is also linear at both axial end portions. May be provided.
- the continuous portion between the flat surface portion and the tapered surface portion is continuous by a convex curved surface having an arcuate cross section.
- grease is interposed between the driving-side and driven-side uneven portions and the cup-side uneven portion.
- a cup-side protruding portion protruding in the radial direction is preferably formed on one of the inner and outer peripheral surfaces of the coupling, The cup side protrusion is positioned between the driving side transmission unit and the driven side transmission unit in the axial direction.
- cup side grooves are formed at a plurality of circumferential positions on both side surfaces in the axial direction of the coupling, and the cup side grooves are formed in the circumferential direction.
- the cup-side concave portion that is formed between the cup-side convex portions adjacent to each other and that constitutes the cup-side concave-convex portion is disposed at a position overlapping in the circumferential direction.
- the worm speed reducer includes, for example, a housing, a worm wheel, a worm, and an electric motor.
- the worm wheel is rotatably supported with respect to the housing.
- the worm is supported rotatably with respect to the housing in a state in which worm teeth provided at an intermediate portion in the axial direction are engaged with the worm wheel.
- the electric motor is for rotationally driving the worm.
- the worm and the output shaft of the electric motor are connected by a torque transmission joint so that torque can be transmitted.
- the torque transmission joint is the torque transmission joint of the present invention as described above.
- the output shaft of the electric motor corresponds to the drive shaft
- the worm shaft corresponds to the driven shaft.
- the tip of the worm (the end opposite to the side connected to the output shaft of the electric motor via the torque transmission joint)
- a preload applying mechanism that elastically presses the worm toward the worm wheel is provided between the housing and the housing.
- the driving side gap and the cover are circumferential gaps between the cup side uneven part and the drive side uneven part and between the cup side uneven part and the drive side uneven part. A drive side clearance is provided.
- the coupling is based on at least one of the drive shaft and the driven shaft based on the existence of the drive side clearance and the driven side clearance. Lean against. Thereby, torque can be smoothly transmitted between the drive shaft and the driven shaft.
- the coupling can be swung based on the existence of the driving side gap and the driven side gap. For this reason, on the circumferential side surface of the cup-side convex portion, one axial end portion of the circumferential side surface of the driving-side convex portion and the other axial end portion of the circumferential side surface of the driven-side convex portion, They can be brought into contact with each other without rattling in the circumferential direction or can be made to face each other.
- a part of the circumferential side surface of a drive side convex part and a driven side convex part will be irrespective of whether the central axes of a drive shaft and a driven shaft correspond or do not correspond. Is brought into contact with or in close proximity to the circumferential side surface of each cup-side convex portion. Therefore, it is possible to prevent the circumferential side surfaces of the driving-side convex portion and the driven-side convex portion and the circumferential side surfaces of the respective cup-side convex portions from strongly colliding with each other. The generation of abnormal noise at the abutting part can be prevented.
- FIG. 2B is a cross-sectional view taken along the line aa in FIG. 2A.
- FIG. 3B is a sectional view taken along line bb in FIG. 3A.
- FIG. 4C is a sectional view taken along the line cc of FIG. 4A.
- Dd sectional drawing of FIG. FIG. 5B is an ee cross-sectional view of FIG. 5A.
- the figure equivalent to Drawing 5A showing the 2nd example of an embodiment.
- the principal part expanded sectional view which shows the 3rd example of embodiment The principal part expanded sectional view which shows the modification of the 3rd example of embodiment.
- the principal part expanded sectional view which shows the modification of the 3rd example of embodiment The principal part expanded sectional view which shows the modification of the 3rd example of embodiment.
- the principal part expanded sectional view which shows the modification of the 3rd example of embodiment The principal part expanded sectional view which shows the modification of the 3rd example of embodiment.
- the partial expanded view of the metal core which comprises a coupling.
- FIG. 21 is an enlarged ff cross-sectional view of FIG. 20 showing an example of a conventional structure of an electric power steering device.
- FIG. 1 to 5 show a first example of an embodiment of the present invention.
- the feature of this example is that even if the central axes of the output shaft 12a of the electric motor 7 that is the drive shaft and the worm 8a that is the driven shaft are not coincident with each other, the output shaft 12a and the worm 8a It is in the point which implement
- the worm speed reducer 15 of this example includes a housing 3, a worm wheel 4, a worm 8 a, and an electric motor 7.
- the worm wheel 4 is rotatably supported inside the housing 3.
- a tooth portion 5 is formed on the outer peripheral surface of the worm wheel 4.
- the worm 8a has two positions in the axial direction (positions on both sides of the worm teeth 6 in the axial direction) with the worm teeth 6 sandwiched between the teeth 5 of the worm wheel 4 in a state where the worm teeth 6 provided in the intermediate portion in the axial direction are engaged with the teeth 5 of the worm wheel 4.
- a preload applying mechanism 16 (see FIG. 21) including a pressing piece 10 and a coil spring 11 is provided between the tip of the worm 8a and the housing 3.
- the preload applying mechanism 16 presses the worm teeth 6 provided on the worm 8 a toward the tooth portions 5 of the worm wheel 4. With such a configuration, backlash between the worm tooth 6 and the tooth portion 5 is suppressed, and generation of rattling noise is suppressed.
- the electric motor 7 is supported and fixed to the housing 3.
- the distal end portion (one axial end portion, left end portion in FIG. 1) of the output shaft 12a of the electric motor 7 is connected to the proximal end portion (the other axial end portion, right end portion in FIG. 1) of the worm 8a.
- the worm 8a can be driven to rotate by the electric motor 7.
- the distal end portion of the output shaft 12a of the electric motor 7 and the proximal end portion of the worm 8a are coupled via a torque transmission joint 17 so that torque can be transmitted.
- the torque transmission joint 17 includes a drive side transmission unit 18, a driven side transmission unit 19, and a coupling 20.
- the drive-side transmission unit 18 is configured such that a drive-side transmission member 22 provided separately from the output shaft main body 21 is supported and fixed at the tip of the output shaft main body 21 of the output shaft 12a.
- the drive side transmission member 22 is made of a material such as a synthetic resin such as a polyamide resin or a sintered metal.
- the driving side transmission member 22 includes a driving side cylindrical portion 24 and a driving side uneven portion 26.
- a driving side engagement hole 23 is formed at the center of the driving side cylindrical portion 24.
- the drive-side concavo-convex part 26 has drive-side convex parts 25, 25 protruding radially outward (radially) at a plurality of circumferential positions on the outer peripheral surface of the drive-side cylindrical part 24 over the entire axial width. Formed.
- the drive-side engagement hole 23 of the drive-side cylindrical portion 24 is in a state in which relative rotation is prevented by an interference fit, spline engagement, key engagement, or the like on the outer peripheral surface of the distal end portion of the output shaft main body 21 (torque transmission is possible)
- the drive-side transmission member 22 is supported and fixed to the tip end portion of the output shaft main body 21 by being externally fitted and fixed.
- the circumferential side surfaces of the drive-side convex portions 25 and 25 of the drive-side concavo-convex portion 26 have the largest (thick) width dimension in the circumferential direction of the respective drive-side convex portions 25 and 25, and the shaft
- the crowning shape in which the shape viewed from the radial direction is inclined in a direction that becomes smaller (thinner) toward both ends in the direction is a partial arc shape.
- the circumferential width sides of the drive-side convex portions 25, 25 are the largest in the circumferential direction in the circumferential direction of the drive-side convex portions 25, 25 and become smaller toward the both axial end portions.
- the shape may be a tapered shape that is inclined in the direction and is linear when viewed from the radial direction.
- a flat surface portion that is parallel to each other is provided at the axially intermediate portions on both sides in the circumferential direction of the drive-side convex portions 25, 25, and tapered surface portions that are linear in the radial direction are provided at both axial ends. Also good.
- the continuous portion of the flat surface portion and the tapered surface portion is continuous with a convex curved surface having an arcuate cross section.
- the width dimension in the circumferential direction of each drive-side convex portion 25, 25 is substantially constant over the radial direction.
- the driven-side transmission portion 19 is formed by supporting and fixing a driven-side transmission member 28 provided separately from the worm shaft main body 27 at the base end portion of the worm shaft main body 27 of the worm 8a.
- the driven side transmission member 28 is made of a material such as a synthetic resin such as a polyamide resin or a sintered metal.
- the driven side transmission member 28 includes a driven side cylindrical portion 30 and a driven side uneven portion 32.
- a driven side engagement hole 29 is formed at the center of the driven side cylindrical portion 30.
- the driven-side concavo-convex portion 32 has the driven-side convex portions 31, 31 protruding radially outward (radial direction) at equal intervals at a plurality of circumferential positions on the outer peripheral surface of the driven-side cylindrical portion 30 in the axial direction. It is formed in a row.
- the driven side engagement hole 29 of the driven side cylindrical portion 30 is in a state in which relative rotation is prevented by an interference fit, spline engagement, key engagement or the like on the outer peripheral surface of the proximal end portion of the worm shaft main body 27 (torque
- the driven-side transmission member 28 is supported and fixed to the base end portion of the worm shaft main body 27 by being externally fitted and fixed.
- the circumferential widths of the driven-side convex portions 31 and 31 of the driven-side concavo-convex portion 32 are the largest (thickened) in the circumferential direction of the driven-side convex portions 31 and 31 in the circumferential direction.
- the circumferential width of each driven-side convex portion 31, 31 is such that the width dimension in the circumferential direction of each of the driven-side convex portions 31, 31 is the largest in the axially intermediate portion, and is closer to both axial ends.
- the taper shape may be a linear shape that is inclined in a decreasing direction and viewed from the radial direction.
- flat surface portions that are parallel to each other are provided in the axially intermediate portions on both side surfaces in the circumferential direction of each driven-side convex portion 31, 31, and taper surface portions that are linear in shape when viewed from the radial direction are also provided at both axial ends. It may be provided.
- the continuous portion between the flat surface portion and the tapered surface portion is continued by a convex curved surface having a circular arc cross section.
- the width dimension in the circumferential direction of each driven-side convex portion 31 is made substantially constant over the radial direction.
- the driven-side convex portions 31 and 31 and the driving-side convex portions 25 and 25 have the same shape.
- the coupling 20 is generally formed in a substantially cylindrical shape by a synthetic resin such as a polyamide resin, an elastomer such as rubber, or a material in which a reinforcing fiber (for example, glass fiber or carbon fiber) is mixed in the synthetic resin or elastomer. It is what was done.
- the coupling 20 includes a cup side cylindrical portion 33 and a cup side uneven portion 35.
- the cup-side concavo-convex portion 35 is formed by forming cup-side convex portions 34 and 34 and cup-side concave portions 43 and 43 in the axial direction.
- the cup-side convex portions 34, 34 protrude radially inward at a plurality of locations in the circumferential direction on the inner peripheral surface of the cup-side cylindrical portion 33.
- the cup side concave portions 43 and 43 are formed between the cup side convex portions 34 and 34 adjacent in the circumferential direction.
- the circumferential side surfaces of the cup-side convex portions 34, 34 of the cup-side concavo-convex portion 35 have the largest (thickness) width dimension in the circumferential direction of the cup-side convex portions 34, 34, and both axial ends.
- the crowning shape in which the shape seen from the radial direction is inclined in a direction that becomes smaller (thinner) toward the portion is a partial arc shape.
- the circumferential widths of the cup-side convex portions 34, 34 of the cup-side convex portions 34, 34 have the largest width dimension in the circumferential direction of the cup-side convex portions 34, 34, and become smaller toward the both axial end portions.
- the shape may be a tapered shape that is inclined in the direction and is linear when viewed from the radial direction.
- flat surface portions that are parallel to each other are provided at the axially intermediate portions of both side surfaces in the circumferential direction of the cup-side convex portions 34, 34, and tapered surface portions that are linear in shape in the radial direction are also provided at both axial ends. May be.
- the continuous portion between the flat surface portion and the tapered surface portion is continued by a convex curved surface having a circular arc cross section.
- the width dimension regarding the circumferential direction of each cup side convex part 34 and 34 is so small that it goes radially inward (taper shape).
- the width dimension in the circumferential direction of each cup-side convex portion 34, 34 is larger than the width dimension in the circumferential direction of each of the driving-side and driven-side convex portions 25, 31 (cup-side concave portion 43). It is sufficiently large (for example, about 3 to 7 times) in the entire axial direction.
- the driving side uneven portion 26 of the driving side transmission member 22 supported and fixed to the tip portion of the output shaft 12 a (output shaft main body 21) is replaced with the cup side uneven portion of the coupling 20.
- 35 is engaged with the other half in the axial direction (the right half in FIG. 1). That is, the drive-side convex portions 25, 25 are engaged with the cup-side concave portions 43, 43, and the drive-side convex portions 25, 25 and the cup-side convex portions 34, 34 are alternately arranged in the circumferential direction in the circumferential direction. Deploy.
- the driven-side uneven portion 32 of the driven-side transmission member 28 supported and fixed to the base end portion of the worm 8a (worm shaft main body 27) is connected to the cup-side uneven portion 35 of the coupling 20 in one axial half. (The left half of FIG. 1) is engaged. That is, the driven-side convex portions 31 and 31 are engaged with the cup-side concave portions 43 and 43, and the driven-side convex portions 31 and 31 and the cup-side convex portions 34 and 34 are axially one-side halves with respect to the circumferential direction. Place them alternately. Note that the driving-side uneven portion 26 and the driven-side uneven portion 32 do not overlap in the axial direction and are arranged in series in the axial direction. As a result, the driving side transmission unit 18 and the driven side transmission unit 19 are coupled via the coupling 20 so as to be able to transmit torque.
- the shapes of the driving side convex portions 25 and 25, the driven side convex portions 31 and 31, and the cup side convex portions 34 and 34 viewed from the radial direction are partially arcuate. It is a crowning shape.
- each drive-side convex portion is engaged with the drive-side concavo-convex portion 26 engaged with the other half portion in the axial direction of the cup-side concavo-convex portion 35 and the center axes of the output shaft 12a and the worm 8a are aligned with each other.
- the circumferential side surfaces of 25 and 25 one end portion in the axial direction and the circumferential side surface of each cup-side convex portion 34 and 34 abut against each other without rattling in the circumferential direction, or face each other.
- the driven side uneven portion 32 is engaged with one half of the cup side uneven portion 35 in the axial direction and the center axes of the output shaft 12a and the worm 8a are aligned with each other on each driven side.
- the other axial end portion and the circumferential side surface of the cup side convex portions 34, 34 abut on each other without rattling in the circumferential direction, or face each other.
- the distance from the intermediate portion in the axial direction of the circumferential side surfaces of the driven-side convex portions 31 and 31 toward the one side in the axial direction between the one end portion and the circumferential side surface of the respective cup-side convex portions 34 and 34 is increased.
- a driven-side gap 37 having an increased width dimension in the circumferential direction is interposed.
- grease as a lubricant is applied to the engaging portion between the driving side uneven portion 26 and the cup side uneven portion 35 and the engaging portion between the driven side uneven portion 32 and the cup side uneven portion 35.
- the driving is a circumferential gap between the cup-side uneven portion 35 and the driving-side uneven portion 26 and between the cup-side uneven portion 35 and the driven-side uneven portion 32.
- a side gap 36 and a driven side gap 37 are provided. Accordingly, when the worm teeth 6 are pressed toward the tooth portion 5 by the preload applying mechanism 16, the worm 8a swings and the center axes of the output shaft 12a and the worm 8a become inconsistent with each other.
- the coupling 20 is inclined with respect to at least one of the output shaft 12a and the worm 8a (the coupling 20 swings). As a result, torque can be smoothly transmitted between the output shaft 12a and the worm 8a.
- the coupling 20 can be swung based on the presence of the drive side gap 36 and the driven side gap 37. For this reason, as in the structure of this example described above, the axial direction of the circumferential side surfaces of the drive-side convex portions 25 and 25 (with the central axes of the output shaft 12a and the worm 8a aligned).
- One end portion can be brought into contact with the circumferential side surface of each cup-side convex portion 34, 34 without rattling in the circumferential direction, or can be made to face each other, and the circumferential side surface of each driven-side convex portion 31, 31 can be Of these, the other axial end can be brought into contact with the circumferential side surface of each cup-side convex portion 34, 34 without rattling in the circumferential direction, or can be opposed to each other.
- the cup-side convex portions 34, 34 can be brought into contact with or in close proximity to the circumferential side surfaces. Accordingly, at the start of torque transmission between the output shaft 12a and the worm 8a, the circumferential side surfaces of the driving side convex portions 25 and the driven side convex portions 31 and the circumferential side surfaces of the cup side convex portions 34 and 34 are provided. Can be prevented from strongly colliding (collision vigorously), and abnormal noise such as rattling noise at the engaging portion of the driving side uneven portion 26 and the driven side uneven portion 32 and the cup side uneven portion 35 can be prevented. Occurrence can be prevented.
- the crowning shape in which the shape of the driving side convex portion 25, the driven side convex portion 31, and the circumferential side surfaces of the cup side convex portions 34, 34 viewed from the radial direction is a partial arc shape. It is said. Therefore, even when the coupling 20 is inclined with respect to at least one of the output shaft 12a and the worm 8a, the driving side uneven portion 26, the driven side uneven portion 32, and the cup side uneven portion 35 are provided. It is possible to prevent contact with one side (partial contact) (that is, secure a certain amount of contact area between the circumferential side surfaces of the drive-side convex portion 25 and the driven-side convex portion 31 and the cup-side convex portions 34 and 34).
- Each of these minute recesses functions as an oil retaining recess for holding grease, so that grease is applied to the engaging portion of the driving side uneven portion 26 and the driven side uneven portion 32 and the cup side uneven portion 35. Easy to hold. For this reason, torque transmission between the output shaft 12a and the worm 8a becomes smooth, and the per side contact between the driving side uneven portion 26 and the driven side uneven portion 32 and the cup side uneven portion 35 is reduced. Generation can be suppressed more effectively.
- the drive side transmission portion 18 (driven side transmission portion 19) does not go through the drive side transmission member 22 (driven side transmission member 28), but the front end portion of the output shaft of the electric motor ( You may form directly in the base end part of a worm shaft.
- a drive-side concavo-convex portion is formed on the inner peripheral surface of the concave portion provided at the distal end portion of the output shaft of the electric motor
- a driven-side concavo-convex portion is formed on the inner peripheral surface of the concave portion provided at the base end portion of the worm shaft.
- it can also comprise so that the coupling side uneven
- FIG. 6 shows a second example of the embodiment of the present invention.
- both side surfaces in the circumferential direction of the drive-side convex portions 25a and 25a constituting the drive-side uneven portion 26a of the drive-side transmission member 22a are flat surfaces parallel to each other. That is, the width dimension in the circumferential direction of each drive-side convex portion 25a, 25a is the same over the axial direction.
- both side surfaces in the circumferential direction of the driven-side convex portions 31a and 31a constituting the driven-side uneven portion 32a of the driven-side transmission member 28a are flat surfaces parallel to each other.
- the width dimensions of the driven-side convex portions 31a and 31a in the circumferential direction are the same in the axial direction.
- both the circumferential side surfaces of the cup-side convex portions 34, 34 constituting the cup-side uneven portion 35 of the coupling 20 are the same as those in the first example of the above-described embodiment.
- 34 is a crowning shape in which the width dimension in the circumferential direction is the largest in the middle portion in the axial direction and is inclined in a direction that becomes smaller toward both ends in the axial direction, and the shape viewed from the radial direction is a partial arc shape.
- the driving side uneven portion 26a is engaged with the other half portion in the axial direction of the cup side uneven portion 35, and the central axes of the output shaft 12a and the worm 8a (see FIG. 1) Of the drive side convex portions 25a, 25a with one end in the axial direction and the circumferential side surface of each cup side convex portion 34, 34 without rattling in the circumferential direction. Touch or close each other.
- the axially intermediate portion of the circumferential side surfaces of the drive-side convex portions 25a and 25a is directed to the other side in the axial direction between the other end portion and the circumferential side surfaces of the cup-side convex portions 34 and 34.
- Drive-side gaps 36a, 36a that increase the width dimension in the circumferential direction are interposed.
- each driven side convex portion is in a state where the driven side uneven portion 32a is engaged with one end portion in the axial direction of the cup side uneven portion 35 and the central axes of the output shaft 12a and the worm 8a are aligned with each other.
- the other end in the axial direction of the circumferential side surfaces of 31a and 31a and the circumferential side surface of the cup-side convex portions 34 and 34 abut on each other in the circumferential direction or face each other closely.
- the axially intermediate portion of each driven side convex portion 31a, 31a is directed to one axial direction between the one end portion and the circumferential side surface of each cup side convex portion 34, 34. Driven-side gaps 37a and 37a that increase the width in the circumferential direction are interposed.
- FIG. 7 to 12 show a third example of the embodiment of the present invention.
- at least one cup-side protruding portion 38 is formed at the axially intermediate portion of the inner peripheral surface of the cup-side cylindrical portion 33.
- the cup side protruding portion 38 is formed between the driving side transmission portion 18 and the driven side transmission portion 19 in the axial direction.
- the cup side protruding portion 38 protrudes radially inward from the cup side protruding portion 34. And the cup side protrusion part 38, the drive side cylindrical part 24, and the to-be-driven side cylindrical part 30 are facing through the clearance gap in the axial direction. However, as in the example of FIG. 8, the cup-side protruding portion 38, the driving-side cylindrical portion 24, and the driven-side cylindrical portion 30 may contact each other without an axial gap. In the example of FIGS. 7 and 8, one cup-side protrusion 38 is formed on each cup-side protrusion 34. However, at least one cup-side protrusion 38 may be formed.
- cup side convex portions 34 may be selected, and the cup side protruding portions 38 may be formed on the selected cup side convex portions 34, respectively.
- the axial displacement of the coupling 20 is caused by the drive-side cylindrical portion. 24 or the driven cylindrical portion 30.
- the cup-side protrusion 38 protrudes radially inward from the cup-side recess 43.
- the tip end portion (radially inner end portion) of the cup-side protruding portion 38 is located radially inward from the driving side uneven portion 26 and the driven side uneven portion 32.
- the cup side protrusion part 38, the drive side convex part 25 and the driven side convex part 31, and the drive side cylindrical part 24 and the driven side cylindrical part 30 are opposed to each other via a gap in the axial direction.
- the cup-side protruding portion 38, the driving-side convex portion 25 and the driven-side convex portion 31, and the driving-side cylindrical portion 24 and the driven-side cylindrical portion 30 have an axial clearance. You may contact
- one cup-side protrusion 38 is formed in each cup-side recess 43. However, at least one cup-side protrusion 38 may be formed. For example, several cup-side recesses 43 may be selected, and the cup-side protrusions 38 may be formed in the selected cup-side recesses 43, respectively.
- At least one cup-side protruding portion 38 faces the driving-side convex portion 25 and the driven-side convex portion 31, and the driving-side cylindrical portion 24 and the driven-side cylindrical portion 30 in the axial direction.
- the axial displacement of the coupling 20 is regulated by the driving side convex portion 25 and the driven side convex portion 31 and the driving side cylindrical portion 24 or the driven side cylindrical portion 30.
- the example of FIG. 11 is the same as the example of FIG. 9 in that the cup side protrusion 38 protrudes radially inward from the cup side recess 43. However, the example of FIG. 11 is different from the example of FIG. 9 in that the tip end portion (radially inner end portion) of the cup-side protruding portion 38 overlaps the driving side uneven portion 26 and the driven side uneven portion 32 in the radial direction. .
- the cup-side protruding portion 38, the driving-side protruding portion 25, and the driven-side protruding portion 31 face each other with a gap in the axial direction.
- the example of FIG. 11 face each other with a gap in the axial direction.
- the cup-side protruding portion 38, the driving-side convex portion 25, and the driven-side convex portion 31 may contact each other without an axial gap.
- one cup side protrusion 38 is formed in each cup side recess 43.
- at least one cup-side protrusion 38 may be formed.
- several cup-side recesses 43 may be selected, and the cup-side protrusions 38 may be formed in the selected cup-side recesses 43, respectively.
- the axial displacement of the coupling 20 is the drive-side protrusion. 25 and the driven-side convex portion 31.
- the coupling 20 may be configured by combining a plurality of types of cup side protrusions 38 shown in FIGS.
- the cup side protruding portion 38 of FIG. 7 may be formed on the cup side protruding portion 34
- the cup side protruding portion 38 of FIG. 9 may be formed on the cup side recessed portion 43.
- the cup-side cylindrical portion 33 is formed with an annular cup-side protruding portion 38 between the drive-side transmission portion 18 and the driven-side transmission portion 19 in the axial direction on the inner peripheral surface of the cup-side cylindrical portion 33.
- the axial displacement of the ring 20 is regulated by the driving side transmission unit 18 or the driven side transmission unit 19, and the axial position of the coupling 20 is stabilized.
- FIG. 13 and 14 show a fourth example of the embodiment of the present invention.
- an annular cored bar 39 is disposed inside the cup-side cylindrical portion 33 as a whole.
- the core metal 39 includes a cylindrical portion 40 concentric with the coupling 20.
- the cylindrical portion 40 overlaps at least the engaging portion of the driving side uneven portion 26 and the driven side uneven portion 32 and the cup side uneven portion 35 in the axial direction.
- the axial length of the cylindrical portion 40 is about half of the axial length of the coupling 20, but may be the same as the axial length of the coupling 20.
- the cored bar 39 may include a plurality of convex portions 41 that protrude radially inward from the inner peripheral surface of the cylindrical portion 40 at equal intervals in the circumferential direction.
- the same number of the plurality of convex portions 41 is provided at positions that overlap the plurality of cup-side convex portions 34 of the coupling 20 in the circumferential direction.
- the plurality of convex portions 41 may not be the same number as the plurality of cup-side convex portions 34.
- the circumferential length of the convex portion 41 is less than or equal to the circumferential length of the cup-side convex portion 34.
- the rigidity of the coupling 20 can be improved.
- the metal core 39 overlaps at least the engaging portion of the driving side uneven portion 26 and the driven side uneven portion 32 and the cup side uneven portion 35 in the axial direction, so that the rigidity of the coupling 20 with respect to rotational torque is improved.
- the effect of can be enhanced.
- the plurality of convex portions 41 are provided on the cored bar 39, the rigidity of the coupling 20 is further improved.
- [Fifth Example of Embodiment] 15 and 16 show a fifth example of the embodiment of the present invention. Also in the coupling 20 of this example, the cored bar 39 is disposed inside the cup-side cylindrical portion 33 as in the fourth example. However, the core metal 39 of this example is configured by rounding a wire net-like sheet or a chain-like metal member as shown in FIG. 16 into a cylindrical shape.
- the coupling 20 in addition to improving the rigidity of the coupling 20, the coupling 20 is easy to bend, so that when the worm 8a swings, the coupling 20 swings more flexibly. This facilitates torque transmission between the output shaft 12a and the worm 8a.
- FIG. 18 show a sixth example of the embodiment of the present invention.
- a plurality of cup-side groove portions 42 that are recessed inward in the axial direction are formed at equal intervals in the circumferential direction on both side surfaces in the axial direction of the coupling 20 of this example.
- the cup-side groove portion 42 is provided in the radial direction from the radially outer end portion of the cup-side cylindrical portion 33 to the radially inner end portion.
- the cup side groove portion 42 is disposed between the cup side concave portion 43 that is formed between the cup side convex portions 34 adjacent in the circumferential direction and that constitutes the cup side concave and convex portion 35 in the circumferential direction.
- the circumferential width of the cup-side groove 42 is longer than the circumferential width of the cup-side recess 43.
- the driving side gap 36 and the driven side gap 37 are widened by the provision of the cup side groove 42, so that the coupling 20, the driving side transmission unit 18 and the driven side are driven.
- the contact area with the side transmission portion 19 is reduced, and the friction at the contact portion is reduced. That is, when the central shafts of the output shaft 12a and the worm 8a do not coincide with each other due to the swing of the worm 8a or the like, the coupling 20 is based on the presence of the drive side clearance 36 and the driven side clearance 37. Although it swings, the friction at that time can be reduced. There is also an effect of making it easy to absorb the swing of the driving side transmission unit 18 and the driven side transmission unit 19.
- the circumferential side surface of the cup-side convex portion provided in the coupling is crowned, and the driving-side convex portion and the driven-side convex portion It is also possible to incline the circumferential side surfaces of the circumferential direction in a direction in which the width dimension in the circumferential direction decreases as it goes toward both sides of the coupling width direction (axial direction).
Abstract
Description
このうちのカップリングは、内外両周面のうちの一方の周面に、径方向(この一方の周面が内周面である場合には、径方向内方。同じく外周面である場合には、径方向外方。)に突出するカップ側凸部を周方向複数箇所に配置して成る、カップ側凹凸部を設けている。
前記駆動側伝達部は、前記駆動軸の軸方向一端部に直接又は他の部材を介して設けられ、内外両周面のうち、前記カップ側凹凸部に対向する周面に、径方向(このカップ側凹凸部に対向する周面が外周面である場合には、径方向外方。同じく内周面である場合には、径方向内方)に突出する駆動側凸部を周方向複数箇所に配置して成る、駆動側凹凸部を設けている。
前記被駆動側伝達部は、前記被駆動軸の軸方向他端部に直接又は他の部材を介して設けられ、内外両周面のうち、前記カップ側凹凸部に対向する周面に、径方向(このカップ側凹凸部に対向する周面が外周面である場合には、径方向外方。同じく内周面である場合には、径方向内方)に突出する被駆動側凸部を周方向複数箇所に配置して成る、被駆動側凹凸部を設けている。
そして、前記駆動側凹凸部を前記カップ側凹凸部の軸方向他側半部に、前記駆動軸と前記被駆動軸との中心軸同士を一致させた状態で、前記各駆動側凸部の周方向側面と前記各カップ側凸部の周方向側面との間に軸方向他側に向かう程周方向に関する幅寸法が大きくなる駆動側隙間が介在した状態で、係合させている。
又、前記被駆動側凹凸部を前記カップ側凹凸部の軸方向一側半部に、前記駆動軸と前記被駆動軸との中心軸同士を一致させた状態で、前記各被駆動側凸部の周方向側面と前記各カップ側凸部の周方向側面との間に軸方向一側に向かう程周方向に関する幅寸法が大きくなる被駆動側隙間が介在した状態で、係合させている。
この様な発明を実施する場合に、例えば、前記駆動側、被駆動側各凸部の周方向側面と、前記各カップ側凸部の周方向側面とのうちの少なくとも一方に、ショットブラストを施す事により、前記各微小凹部を形成する。
前記カップ側突出部は、前記駆動側伝達部及び前記被駆動側伝達部の軸方向における間に位置する。
このうちのウォームホイールは、前記ハウジングに対し回転自在に支持されている。
前記ウォームは、軸方向中間部に設けられたウォーム歯をこのウォームホイールと噛合させた状態で、前記ハウジングに対し回転自在に支持されている。
前記電動モータは、前記ウォームを回転駆動する為のものである。
そして、このウォームと前記電動モータの出力軸とをトルク伝達用継手により、トルクの伝達を可能に接続している。
特に本発明のウォーム減速機に於いては、前記トルク伝達用継手を、上述の様な本発明のトルク伝達用継手とする。この場合、前記電動モータの出力軸が前記駆動軸に相当し、前記ウォーム軸が前記被駆動軸に相当する。
上述の様な本発明のウォーム減速機を実施する場合に好ましくは、前記ウォームの先端部(トルク伝達用継手を介して電動モータの出力軸に接続された側とは反対側の端部)と前記ハウジングとの間に、前記ウォームを前記ウォームホイールに向けて弾性的に押圧する予圧付与機構を設ける。
即ち、本発明の場合には、カップ側凹凸部と駆動側凹凸部との間及びカップ側凹凸部と駆動側凹凸部との間のそれぞれに、周方向の隙間である、駆動側隙間及び被駆動側隙間が設けられる。従って、駆動軸と被駆動軸との中心軸同士が不一致になると、駆動側隙間、被駆動側隙間の存在に基づいて、カップリングが、駆動軸と被駆動軸とのうちの少なくとも一方の軸に対し傾く。これにより、駆動軸と被駆動軸との間でトルクの伝達を円滑に行える。
図1~5は、本発明の実施形態の第1例を示している。尚、本例の特徴は、駆動軸である電動モータ7の出力軸12aと、被駆動軸であるウォーム8aと、の中心軸同士が互いに不一致になっても、出力軸12aとウォーム8aとの間でのトルク伝達を円滑に行う事ができる構造を実現する点にある。本例のウォーム減速機15は、ハウジング3と、ウォームホイール4と、ウォーム8aと、電動モータ7と、を備える。
さらに、ウォーム8a(ウォーム軸本体27)の基端部に支持固定された被駆動側伝達部材28の被駆動側凹凸部32を、カップリング20のカップ側凹凸部35の軸方向一側半部(図1の左側半部)に係合させる。即ち、被駆動側凸部31、31をカップ側凹部43、43に係合させ、被駆動側凸部31、31とカップ側凸部34、34の軸方向一側半部とを周方向に関して交互に配置する。
なお、駆動側凹凸部26と被駆動側凹凸部32は、軸方向位置が重なっておらず、軸方向に直列に配置される。
これにより、駆動側伝達部18と被駆動側伝達部19とを、カップリング20を介してトルクの伝達を可能に結合している。
図6は、本発明の実施形態の第2例を示している。本例のトルク伝達用継手17aの場合には、駆動側伝達部材22aの駆動側凹凸部26aを構成する駆動側凸部25a、25aの周方向両側面が、互いに平行な平坦面である。即ち、各駆動側凸部25a、25aの周方向に関する幅寸法が軸方向に亙り同じである。同様に、被駆動側伝達部材28aの被駆動側凹凸部32aを構成する被駆動側凸部31a、31aの周方向両側面が、互いに平行な平坦面である。即ち、各被駆動側凸部31a、31aの周方向に関する幅寸法が軸方向に亙り同じである。一方、カップリング20のカップ側凹凸部35を構成するカップ側凸部34、34の周方向両側面は、上述した実施形態の第1例の場合と同様に、これら各カップ側凸部34、34の周方向に関する幅寸法が軸方向中間部で最も大きく、軸方向両端部に向かう程小さくなる方向に傾斜した、径方向から見た形状が部分円弧形であるクラウニング形状である。
その他の部分の構成及び作用は、上述した実施形態の第1例と同様である。
図7~図12は、本発明の実施形態の第3例を示している。本例のカップリング20においては、カップ側円筒部33の内周面の軸方向中間部に、少なくとも一つのカップ側突出部38が形成される。カップ側突出部38は、駆動側伝達部18及び被駆動側伝達部19の軸方向における間に形成される。
なお、図7及び図8の例では、カップ側突出部38は、全てのカップ側凸部34に一個ずつ形成されている。しかしながら、カップ側突出部38は、少なくとも一つ形成されればよい。例えば、いくつかのカップ側凸部34を選択し、当該選択されたカップ側凸部34にそれぞれカップ側突出部38を形成してもよい。
このような例によれば、少なくとも一つのカップ側突出部38が、駆動側円筒部24及び被駆動側円筒部30と軸方向において対向するので、カップリング20の軸方向変位が駆動側円筒部24又は被駆動側円筒部30によって規制される。
なお、図9及び図10の例では、カップ側突出部38は、全てのカップ側凹部43に一個ずつ形成されている。しかしながら、カップ側突出部38は、少なくとも一つ形成されればよい。例えば、いくつかのカップ側凹部43を選択し、当該選択されたカップ側凹部43にそれぞれカップ側突出部38を形成してもよい。
このような例によれば、少なくとも一つのカップ側突出部38が、駆動側凸部25及び被駆動側凸部31並びに駆動側円筒部24及び被駆動側円筒部30と軸方向において対向するので、カップリング20の軸方向変位が駆動側凸部25及び被駆動側凸部31並びに駆動側円筒部24又は被駆動側円筒部30によって規制される。
なお、図11及び図12の例では、カップ側突出部38は、全てのカップ側凹部43に一個ずつ形成されている。しかしながら、カップ側突出部38は、少なくとも一つ形成されればよい。例えば、いくつかのカップ側凹部43を選択し、当該選択されたカップ側凹部43にそれぞれカップ側突出部38を形成してもよい。
このような例によれば、少なくとも一つのカップ側突出部38が、駆動側凸部25及び被駆動側凸部31と軸方向において対向するので、カップリング20の軸方向変位が駆動側凸部25及び被駆動側凸部31によって規制される。
図13及び図14は、本発明の実施形態の第4例を示している。本例のカップリング20においては、カップ側円筒部33の内部に、全体として円環状の芯金39が配置されている。芯金39は、カップリング20と同心の円筒部40を備える。円筒部40は、少なくとも、駆動側凹凸部26及び被駆動側凹凸部32と、カップ側凹凸部35と、の係合部と軸方向において重なる。図13の例では、円筒部40の軸方向長さがカップリング20の軸方向長さの半分程度とされているが、カップリング20の軸方向長さと同一としてもよい。
図15及び図16は、本発明の実施形態の第5例を示している。本例のカップリング20においても、第4例と同様、カップ側円筒部33の内部に芯金39が配置されている。但し、本例の芯金39は、図16に示すような金網状のシートや鎖状の金属部材を、筒状に丸めることにより構成されている。
図17~図19は、本発明の実施形態の第6例を示している。本例のカップリング20の軸方向両側面には、周方向に等間隔で、軸方向内側に凹む複数のカップ側溝部42が形成されている。図18に示すように、カップ側溝部42は、カップ側円筒部33の径方向外方端部から径方向内方端部に亘って、径方向に向かって設けられている。カップ側溝部42は、周方向に隣り合うカップ側凸部34の間に形成され且つカップ側凹凸部35を構成するカップ側凹部43と、周方向において重なる位置に配置されている。カップ側溝部42の周方向幅はカップ側凹部43の周方向幅よりも長い。
2 ステアリングシャフト
3 ハウジング
4 ウォームホイール
5 歯部
6 ウォーム歯
7 電動モータ
8、8a ウォーム
9a、9b 転がり軸受
10 押圧駒
11 コイルばね
12、12a 出力軸
13 スプライン孔
14 スプライン軸部
15 ウォーム減速機
16 予圧付与機構
17、17a トルク伝達用継手
18 駆動側伝達部
19 被駆動側伝達部
20 カップリング
21 出力軸本体
22、22a 駆動側伝達部材
23 駆動側係合孔
24 駆動側円筒部
25、25a 駆動側凸部
26、26a 駆動側凹凸部
27 ウォーム軸本体
28、28a 被駆動側伝達部材
29 被駆動側係合孔
30、30a 被駆動側円筒部
31、31a 被駆動側凸部
32、32a 被駆動側凹凸部
33 カップ側円筒部
34 カップ側凸部
35 カップ側凹凸部
36、36a 駆動側隙間
37、37a 被駆動側隙間
38 カップ側突出部
39 芯金
40 円筒部
41 凸部
42 カップ側溝部
43 カップ側凹部
Claims (8)
- 軸方向に関して互いに直列に配置された、駆動軸の軸方向一端部と被駆動軸の軸方向他端部との間でトルクを伝達する、トルク伝達用継手であって、
内外両周面のうちの一方の周面に、径方向に突出するカップ側凸部を周方向複数箇所に配置して成る、カップ側凹凸部を設けたカップリングと、
前記駆動軸の軸方向一端部に設けられ、内外両周面のうち、前記カップ側凹凸部に対向する周面に、径方向に突出する駆動側凸部を周方向複数箇所に配置して成る、駆動側凹凸部を設けた駆動側伝達部と、
前記被駆動軸の軸方向他端部に設けられ、内外両周面のうち、前記カップ側凹凸部に対向する周面に、径方向に突出する被駆動側凸部を周方向複数箇所に配置して成る、被駆動側凹凸部を設けた被駆動側伝達部と、
を備え、
前記駆動側凹凸部を前記カップ側凹凸部の軸方向他側半部に、前記駆動軸と前記被駆動軸との中心軸同士を一致させた状態で、前記各駆動側凸部の周方向側面と前記各カップ側凸部の周方向側面との間に軸方向他側に向かう程周方向に関する幅寸法が大きくなる駆動側隙間が介在した状態で、係合させており、
前記被駆動側凹凸部を前記カップ側凹凸部の軸方向一側半部に、前記駆動軸と前記被駆動軸との中心軸同士を一致させた状態で、前記各被駆動側凸部の周方向側面と前記各カップ側凸部の周方向側面との間に軸方向一側に向かう程周方向に関する幅寸法が大きくなる被駆動側隙間が介在した状態で、係合させている、
トルク伝達用継手。 - 前記各駆動側凸部の周方向側面を、前記各駆動側凸部の周方向に関する幅寸法が、軸方向中間部で最も大きく、軸方向両端部に向かう程小さくなる方向に傾斜させると共に、前記各被駆動側凸部の周方向側面を、前記各被駆動側凸部の周方向に関する幅寸法が、軸方向中間部で最も大きく、軸方向両端部に向かう程小さくなる方向に傾斜させている、請求項1に記載したトルク伝達用継手。
- 前記各カップ側凸部の周方向側面を、前記各カップ側凸部の周方向に関する幅寸法が、軸方向中間部で最も大きく、軸方向両端部に向かう程小さくなる方向に傾斜させている、請求項1又は2に記載したトルク伝達用継手。
- 前記駆動側、被駆動側各凸部の周方向側面と、前記各カップ側凸部の周方向側面との間に、グリースを介在させている、請求項1~3のうちの何れか1項に記載したトルク伝達用継手。
- 前記駆動側、被駆動側各凸部の周方向側面と、前記各カップ側凸部の周方向側面とのうちの少なくとも一方に、多数の微小凹凸部を設けている、請求項4に記載したトルク伝達用継手。
- 前記カップリングの内外両周面のうちの一方の周面には、径方向に突出するカップ側突出部が形成され、
前記カップ側突出部は、前記駆動側伝達部及び前記被駆動側伝達部の軸方向における間に位置する、請求項1~5のうちの何れか1項に記載したトルク伝達用継手。 - 前記カップリングの軸方向両側面には、周方向複数個所にカップ側溝部が形成されており、
前記カップ側溝部は、周方向に隣り合う前記カップ側凸部の間に形成され且つ前記カップ側凹凸部を構成するカップ側凹部と、周方向において重なる位置に配置されている、請求項1~6のうちの何れか1項に記載したトルク伝達用継手。 - ハウジングと、
前記ハウジングに対し回転自在に支持されたウォームホイールと、
軸方向中間部に設けられたウォーム歯を前記ウォームホイールと噛合させた状態で、前記ハウジングに対し回転自在に支持されたウォームと、
前記ウォームを回転駆動する為の電動モータと、
を備え、
前記ウォームと前記電動モータの出力軸とをトルク伝達用継手により、トルクの伝達を可能に接続している、
ウォーム減速機に於いて、
前記トルク伝達用継手が、請求項1~7のうちの何れか1項に記載のトルク伝達用継手である、ウォーム減速機。
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CN201680020926.4A CN107407337B (zh) | 2015-04-22 | 2016-04-15 | 力矩传递用接头和蜗轮蜗杆减速器 |
JP2017514104A JP6597774B2 (ja) | 2015-04-22 | 2016-04-15 | トルク伝達用継手及びウォーム減速機 |
US15/564,473 US10408271B2 (en) | 2015-04-22 | 2016-04-15 | Torque transmission joint and worm reduction gear |
EP16783113.0A EP3267062A4 (en) | 2015-04-22 | 2016-04-15 | Torque transmission joint and worm reduction gear |
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JP2015087823 | 2015-04-22 | ||
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PCT/JP2016/062179 WO2016171092A1 (ja) | 2015-04-22 | 2016-04-15 | トルク伝達用継手及びウォーム減速機 |
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US (1) | US10408271B2 (ja) |
EP (1) | EP3267062A4 (ja) |
JP (2) | JP6597774B2 (ja) |
CN (1) | CN107407337B (ja) |
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN109563884A (zh) * | 2017-06-29 | 2019-04-02 | 川崎重工业株式会社 | 铁道车辆用齿轮形挠曲联轴节及具备该齿轮形挠曲联轴节的铁道车辆用转向架 |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3263937B1 (en) * | 2015-04-28 | 2019-09-04 | NSK Ltd. | Joint for torque transmission and worm reduction gear |
EP3453906B1 (en) * | 2016-10-13 | 2020-12-09 | NSK Ltd. | Joint for torque transmission and electric power steering device |
KR101993295B1 (ko) * | 2017-12-19 | 2019-06-26 | 주식회사 만도 | 전동식 동력 보조 조향장치의 감속기 |
CN108895121B (zh) * | 2018-09-07 | 2024-05-03 | 莱科(衢州市)科技有限公司 | 蜗轮蜗杆减速器及减速电机 |
DE102020104204A1 (de) * | 2020-02-18 | 2021-08-19 | Brose Fahrzeugteile Se & Co. Kommanditgesellschaft, Bamberg | Antriebsanordnung zur motorischen Verstellung eines Verstellelements eines Kraftfahrzeugs |
CN115041515B (zh) * | 2022-06-02 | 2024-01-09 | 吉林建筑大学 | 一种污染场地治理自动化控制装置 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2114807A (en) * | 1937-11-04 | 1938-04-19 | Mccavitt John | Universal joint |
JPS487288U (ja) * | 1971-06-05 | 1973-01-26 | ||
GB2040397A (en) * | 1979-01-22 | 1980-08-28 | Costamasnaga Spa | Universal joints |
JPH0861450A (ja) * | 1994-08-23 | 1996-03-08 | Nippon Sharyo Seizo Kaisha Ltd | 遊星ローラ式変速機構を用いた動力伝達装置 |
JP2001003946A (ja) * | 1999-06-22 | 2001-01-09 | Koyo Seiko Co Ltd | 筒 軸 |
JP2003072563A (ja) * | 2001-06-20 | 2003-03-12 | Koyo Seiko Co Ltd | 電動式動力舵取装置 |
JP2011038600A (ja) * | 2009-08-12 | 2011-02-24 | Nakamura Jiko Co Ltd | 自在継手部品の製造方法 |
Family Cites Families (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
USRE25489E (en) * | 1963-11-26 | Anti-friction slip joint | ||
US1983007A (en) | 1932-10-25 | 1934-12-04 | Continental Diamond Fibre Co | Coupling device |
US2682760A (en) | 1950-04-18 | 1954-07-06 | American Flexible Coupling Com | Gear coupling |
GB731109A (en) | 1953-03-18 | 1955-06-01 | American Flexible Coupling Com | Gear coupling |
US2979147A (en) * | 1954-05-19 | 1961-04-11 | Daimler Benz Ag | Coupling for vehicle half axle drive assembly |
US2841966A (en) | 1955-11-14 | 1958-07-08 | Charles W Belden | Flexible couplings |
US2995908A (en) * | 1957-09-05 | 1961-08-15 | Dana Corp | Needle bearing spline |
US3045457A (en) * | 1960-01-20 | 1962-07-24 | Beaver Prec Products Inc | Ball spline assembly |
US3080732A (en) * | 1960-12-07 | 1963-03-12 | Baldwin Lima Hamilton Corp | Sound isolating misalignment coupling |
US3620043A (en) * | 1970-05-12 | 1971-11-16 | Arinc Res Corp | Spline-type pivots universal joints and flexible couplings |
JPS4882344U (ja) * | 1972-01-14 | 1973-10-06 | ||
JPS5313785B2 (ja) | 1972-02-04 | 1978-05-12 | ||
CH564999A5 (ja) * | 1974-03-07 | 1975-08-15 | Maag Zahnraeder & Maschinen Ag | |
DE2656946A1 (de) * | 1976-12-16 | 1978-06-29 | Daimler Benz Ag | Zahnwellenverbindung |
US4493622A (en) * | 1983-03-07 | 1985-01-15 | Trw Inc. | Variable displacement motor |
US4768994A (en) * | 1987-05-04 | 1988-09-06 | General Motors Corporation | Telescopic tripot universal joint |
US5356342A (en) | 1987-11-06 | 1994-10-18 | White Hydraulics, Inc. | Teeth for a wobblestick |
JP4381024B2 (ja) | 2003-04-10 | 2009-12-09 | 日本精工株式会社 | 電動式パワーステアリング装置用アシスト装置及び電動式パワーステアリング装置 |
JP4716679B2 (ja) | 2003-06-25 | 2011-07-06 | 日本精工株式会社 | ウォーム減速機及び電動式パワーステアリング装置 |
CN100476241C (zh) | 2003-06-25 | 2009-04-08 | 日本精工株式会社 | 蜗轮减速器及电动式动力转向装置 |
US7156628B2 (en) * | 2004-06-03 | 2007-01-02 | White Drive Products, Inc. | Wobblestick with helix |
JPWO2009028482A1 (ja) * | 2007-08-31 | 2010-12-02 | Thk株式会社 | 運動装置及び移動装置 |
JP5263281B2 (ja) | 2010-12-20 | 2013-08-14 | 日本精工株式会社 | 電動パワーステアリング装置 |
JP6179197B2 (ja) * | 2013-05-31 | 2017-08-16 | 株式会社リコー | 駆動伝達装置、及び画像形成装置 |
-
2016
- 2016-04-15 US US15/564,473 patent/US10408271B2/en active Active
- 2016-04-15 EP EP16783113.0A patent/EP3267062A4/en not_active Withdrawn
- 2016-04-15 JP JP2017514104A patent/JP6597774B2/ja active Active
- 2016-04-15 WO PCT/JP2016/062179 patent/WO2016171092A1/ja active Application Filing
- 2016-04-15 CN CN201680020926.4A patent/CN107407337B/zh active Active
-
2019
- 2019-07-29 JP JP2019139139A patent/JP6911892B2/ja active Active
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2114807A (en) * | 1937-11-04 | 1938-04-19 | Mccavitt John | Universal joint |
JPS487288U (ja) * | 1971-06-05 | 1973-01-26 | ||
GB2040397A (en) * | 1979-01-22 | 1980-08-28 | Costamasnaga Spa | Universal joints |
JPH0861450A (ja) * | 1994-08-23 | 1996-03-08 | Nippon Sharyo Seizo Kaisha Ltd | 遊星ローラ式変速機構を用いた動力伝達装置 |
JP2001003946A (ja) * | 1999-06-22 | 2001-01-09 | Koyo Seiko Co Ltd | 筒 軸 |
JP2003072563A (ja) * | 2001-06-20 | 2003-03-12 | Koyo Seiko Co Ltd | 電動式動力舵取装置 |
JP2011038600A (ja) * | 2009-08-12 | 2011-02-24 | Nakamura Jiko Co Ltd | 自在継手部品の製造方法 |
Non-Patent Citations (1)
Title |
---|
See also references of EP3267062A4 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN109563884A (zh) * | 2017-06-29 | 2019-04-02 | 川崎重工业株式会社 | 铁道车辆用齿轮形挠曲联轴节及具备该齿轮形挠曲联轴节的铁道车辆用转向架 |
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CN107407337B (zh) | 2019-12-20 |
JP6911892B2 (ja) | 2021-07-28 |
EP3267062A4 (en) | 2018-08-01 |
US20180080502A1 (en) | 2018-03-22 |
US10408271B2 (en) | 2019-09-10 |
CN107407337A (zh) | 2017-11-28 |
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