WO2019189472A1 - Dispositif de direction - Google Patents

Dispositif de direction Download PDF

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Publication number
WO2019189472A1
WO2019189472A1 PCT/JP2019/013373 JP2019013373W WO2019189472A1 WO 2019189472 A1 WO2019189472 A1 WO 2019189472A1 JP 2019013373 W JP2019013373 W JP 2019013373W WO 2019189472 A1 WO2019189472 A1 WO 2019189472A1
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WO
WIPO (PCT)
Prior art keywords
pair
hole
cam
steering
width direction
Prior art date
Application number
PCT/JP2019/013373
Other languages
English (en)
Japanese (ja)
Inventor
傑 杉下
宏高 清水
勝 大澤
Original Assignee
日本精工株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日本精工株式会社 filed Critical 日本精工株式会社
Publication of WO2019189472A1 publication Critical patent/WO2019189472A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
    • B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
    • B62D1/16—Steering columns
    • B62D1/18—Steering columns yieldable or adjustable, e.g. tiltable
    • B62D1/184—Mechanisms for locking columns at selected positions
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
    • B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
    • B62D1/16—Steering columns
    • B62D1/18—Steering columns yieldable or adjustable, e.g. tiltable
    • B62D1/187—Steering columns yieldable or adjustable, e.g. tiltable with tilt adjustment; with tilt and axial adjustment
    • B62D1/189—Steering columns yieldable or adjustable, e.g. tiltable with tilt adjustment; with tilt and axial adjustment the entire column being tiltable as a unit
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04—Wound springs
    • F16F1/12—Attachments or mountings

Definitions

  • the present invention relates to a steering device including a steering wheel position adjusting device.
  • the steering device transmits the rotation of the steering wheel 1 to the input shaft 3 of the steering gear unit 2, and pushes and pulls the pair of left and right tie rods 4 based on the rotation of the input shaft 3.
  • a steering angle is given to the wheel.
  • the steering device includes a steering shaft 5 that supports the steering wheel 1 at its rear end, and a cylindrical steering column 6 that rotatably supports the steering shaft 5 in an axially inserted state inside the steering shaft 5.
  • the front end portion of the steering shaft 5 is connected to the rear end portion of the intermediate shaft 8 via a universal joint 7, and the front end portion of the intermediate shaft 8 is connected to the input shaft 3 via another universal joint 9.
  • the front-rear direction, the width direction, and the up-down direction mean the front-rear direction, the width direction, and the up-down direction of the vehicle unless otherwise specified.
  • the steering device can include a tilt mechanism for adjusting the vertical position of the steering wheel 1 and a telescopic mechanism for adjusting the front-rear position of the steering wheel 1.
  • the gear housing 10 fixed to the front portion of the steering column 6 is supported with respect to the vehicle body 11 by a tilt shaft 12 arranged in the width direction so as to be able to swing and displace.
  • a displacement bracket 13 is provided below the steering column 6, and a support bracket 14 is disposed at a position sandwiching the displacement bracket 13 from both sides in the width direction.
  • the support bracket 14 has a vertical slot 15 extending in the vertical direction, and the displacement bracket 13 has a longitudinal slot 16 extending in the front-rear direction.
  • the adjustment rod 17 is disposed so as to pass through the vertical slot 15 and the longitudinal slot 16 in the width direction.
  • the steering shaft 5 and the steering column 6 have a telescopic structure.
  • FIG. 25 shows a structure similar to that described in Japanese Patent Laid-Open No. 2015-214291.
  • the steering column 6 includes an outer column 18 disposed on the rear side and an inner column 19 disposed on the front side, and the front portion of the outer column 18 and the rear portion of the inner column 19 are fitted so as to be capable of relative displacement in the axial direction.
  • the total length is configured to be extendable.
  • the outer column 18 includes a slit 20 at the front portion thereof, and the inner diameter of the front portion of the outer column 18 can be elastically expanded and contracted.
  • the outer column 18 includes a pair of sandwiched plate portions 21 a and 21 b that constitute the displacement bracket 13 at a portion that sandwiches the slit 20 from both sides in the width direction.
  • the pair of sandwiched plate portions 21a and 21b has longitudinally long holes 16a and 16b.
  • the support bracket 14 includes a pair of support plate portions 22a and 22b, and the pair of support plate portions 22a and 22b includes vertically elongated holes 15a and 15b.
  • the adjustment rod 17 is disposed so as to pass through the pair of vertical slots 15a and 15b and the pair of longitudinal slots 16a and 16b.
  • the base of the adjusting lever 23 is fixed to one end of the adjusting rod 17 at a portion protruding from the outer surface of one of the pair of supporting plate portions 22a and 22b.
  • a cam device 24 is disposed between the outer surface of one support plate 22 a and the base of the adjustment lever 23.
  • the cam device 24 includes a drive side cam 25 and a driven side cam 26, and the width direction dimension can be enlarged or reduced based on the relative rotation of these cams.
  • the driven cam 26 is provided with an engaging convex portion 27 on its inner surface, and the engaging convex portion 27 is only displaced along the vertical elongated hole 15a into the vertical elongated hole 15a of one support plate portion 22a. Can be engaged.
  • the drive side cam 25 can be rotated together with the adjustment rod 17 by the adjustment lever 23.
  • a nut 28 is screwed into a portion protruding from the outer surface of the other support plate portion 22 b of the pair of support plate portions 22 a and 22 b.
  • a thrust bearing 29 and a pressing plate 30 are disposed between the outer surface of the other support plate portion 22b and the nut 28.
  • the adjustment lever 23 After moving the steering wheel 1 to a desired position, the adjustment lever 23 is swung in the direction opposite to the predetermined direction. Thereby, the drive side cam 25 rotates in the locking direction, the dimension in the width direction of the cam device 24 is enlarged, and the interval between the inner surfaces of the pair of support plate portions 22a and 22b is reduced. As a result, the surface pressure of the contact portion between the inner side surfaces of the support plate portions 22a and 22b and the outer side surfaces of the sandwiched plate portions 21a and 21b increases, and at the same time, the inner diameter of the front portion of the outer column 18 is elastically reduced. The surface pressure of the contact portion between the front inner peripheral surface of the outer column 18 and the rear outer peripheral surface of the inner column 19 increases. In this clamped state, the up / down position and the front / rear position after adjustment of the steering wheel 1 are maintained.
  • the steering device can include a spring 31.
  • One end of the spring 31 is locked to the support bracket 14, and the other end of the spring 31 is in elastic contact with the lower surface of the pressing plate 30.
  • the spring 31 applies an upward force to the other end portion of the adjustment rod 17 via the pressing plate 30 in a direction substantially along the extending direction of the vertical elongated hole 15b. For this reason, when the position of the steering wheel 1 is adjusted, the steering column 6 is prevented from tilting, and the vertical position of the steering wheel 1 can be adjusted with a light force.
  • a tension spring is arranged between a part of a support bracket and a base of an adjustment lever, and the front side surface of the engagement convex portion of the driven cam is connected to the front side of the vertical slot.
  • a structure for pressing against an edge is disclosed. According to this structure, it is possible to prevent the upper and lower end portions of the front and rear side surfaces of the engaging convex portion from colliding with the front and rear side edges of the upper and lower longitudinal holes vigorously, so that the generation of abnormal noise can be suppressed.
  • the end of the tension spring is locked in a circular spring locking hole provided at the base of the adjustment lever.
  • the inner diameter of the spring locking hole is sufficiently larger than the wire diameter of the tension spring in consideration of the workability of the assembly operation of the steering device. For this reason, when the adjustment lever is swung to adjust the position of the steering wheel, the end of the tension spring moves (slides) along the inner periphery of the spring locking hole, and a slight vibration called stick-slip occurs. May occur. When stick-slip occurs, the vibration propagates to the tension spring, and there is a possibility that abnormal noise such as bounce sound and reverberation sound is generated.
  • the present invention not only prevents the side surface of the engagement convex portion of the driven cam constituting the cam device and the side edge of the vertically elongated hole from colliding with force, but also tension. It is an object of the present invention to provide a steering device that can suppress the occurrence of stick-slip between a spring and an adjustment lever and can secure the workability of assembly work.
  • the steering device of the present invention includes a steering column, a displacement bracket, a support bracket, an adjustment rod, a cam device, an adjustment lever, and a tension spring.
  • the steering column is for rotatably supporting the steering shaft in an axial direction inside thereof, and has a cylindrical shape, is attached to a vehicle body or a member that can be fixed to the vehicle body, and has a width. It is arranged in the direction, and can be oscillated and displaced about a tilt shaft that supports the steering column or a member fixed to the steering column.
  • the steering column can be composed of an inner column and an outer column that is disposed on the rear side of the inner column and is fitted to the inner column so as to be capable of relative displacement in the axial direction.
  • the displacement bracket is provided in a part of the steering column and has a column side through-hole penetrating the displacement bracket in the width direction.
  • the column side through hole can be configured by a longitudinal hole (telescopic adjustment elongated hole) that extends in the longitudinal direction.
  • the steering device of the present invention does not include a telescopic mechanism, it can be configured by a circular hole.
  • the support bracket is provided on a mounting plate portion, a pair of support plate portions connected to the mounting plate portion and disposed on both sides in the width direction of the displacement bracket, and the pair of support plate portions. And a pair of vertically elongated slots (tilt adjusting slots).
  • the cam device includes a driving cam and a driven cam, and a portion of one end of the adjustment rod that protrudes from the outer surface of one of the support plate portions of the pair of support plate portions. Arranged around.
  • the adjustment lever has a base fixed to the driving cam.
  • the tension spring is bridged between the support bracket and the base of the adjustment lever.
  • the base of the adjustment lever has a spring locking hole in which an end of the tension spring is locked.
  • the driven cam is provided with an engaging convex portion on an inner surface thereof, and the engaging convex portion is provided on the one supporting plate portion, and the upper and lower ones of the pair of vertical elongated holes.
  • the front long side of the one of the support plate portions of the one vertical plate is engaged with the longitudinal long hole so that the displacement along the vertical long hole is possible. It is elastically pressed against the front edge.
  • the spring locking hole is configured by a combination of a guide hole portion disposed on the front side and a large-diameter hole portion disposed on the rear side.
  • the guide hole portion has a pair of linear guide sides that are inclined toward each other toward the front side.
  • the large-diameter hole has a size that allows the end of the tension spring to be loosely inserted.
  • the end of the tension spring is elastically pressed between the pair of guide sides and is elastically pressed against the pair of guide sides.
  • the adjusting rod can be rotated in synchronization with the driving cam in response to the swinging operation of the adjusting lever. Alternatively, it is possible to rotate only the drive side cam and not rotate the adjusting rod.
  • the guide hole portion may be constituted by a triangular hole having a substantially triangular opening shape.
  • the guide hole portion may have a substantially trapezoidal opening shape.
  • the large-diameter hole portion may have an inner diameter larger than the wire diameter of the end portion of the tension spring, and may have a substantially semicircular opening shape.
  • the large-diameter hole portion may have a substantially trapezoidal opening shape that is sufficiently larger than the wire diameter of the end portion of the tension spring.
  • the spring locking hole may have a substantially tear-shaped opening shape as a whole, which is a combination of the substantially triangular opening shape of the guide hole portion and the substantially semicircular opening shape of the large-diameter hole portion. .
  • the spring locking hole has a substantially triangular opening shape as a whole, which is a combination of the substantially triangular opening shape of the guide hole portion and the substantially trapezoidal opening shape of the large diameter hole portion.
  • the spring locking hole has a substantially trapezoidal opening shape as a whole, which is a combination of the substantially trapezoidal opening shape of the guide hole portion and the substantially trapezoidal opening shape of the large-diameter hole portion. You can also.
  • the steering device of the present invention not only can the side surface of the engagement convex portion of the driven cam constituting the cam device collide with the side edge of the vertically elongated slot, but also the tension spring and the adjustment can be prevented. Occurrence of stick-slip with the lever can be suppressed, and the workability of the assembly work can be ensured.
  • FIG. 1 is a perspective view of the steering device of the first example of the embodiment as viewed from the adjustment lever side on the rear side and the upper side.
  • FIG. 2 is a perspective view of the steering device of the first example of the embodiment as viewed from the rear side and the upper side from the side opposite to the adjustment lever.
  • FIG. 3 is a perspective view of the steering device of the first example of the embodiment as viewed from the adjustment lever side on the front side and the upper side.
  • FIG. 4 is a perspective view of the steering device of the first example of the embodiment as viewed from the adjustment lever side on the rear side and the lower side.
  • FIG. 5 is a perspective view of the steering device of the first example of the embodiment as viewed from the side opposite to the adjustment lever on the rear side and the lower side.
  • FIG. 1 is a perspective view of the steering device of the first example of the embodiment as viewed from the adjustment lever side on the rear side and the upper side.
  • FIG. 2 is a perspective view of the steering device of the first example of the embodiment as
  • FIG. 6 is a side view of the steering device of the first example of the embodiment as viewed from the adjustment lever side.
  • FIG. 7 is a side view of the steering device of the first example of the embodiment as viewed from the side opposite to the adjustment lever.
  • FIG. 8 is a plan view of the steering device of the first example of the embodiment.
  • FIG. 9 is a bottom view of the steering device of the first example of the embodiment.
  • FIG. 10 is a cross-sectional view taken along the line AA of FIG. 6 showing the steering device of the first example of the embodiment.
  • FIG. 11 is a perspective view of a cam device incorporated in the steering device of the first example of the embodiment.
  • FIG. 12 (A) to 12 (D) schematically show a driving side cam and a driven side cam of a cam device incorporated in the steering device of the first example of the embodiment
  • FIG. 12B is a rear view of the driving cam
  • FIG. 12C is a front view of the driven cam
  • FIG. 12D is a rear view of the driven cam.
  • 13A and 13B show a pressing plate incorporated in the steering device of the first example of the embodiment
  • FIG. 13A is a plan view of the pressing plate
  • FIG. FIG. 3 is a front view of the pressing plate.
  • 14 is a cross-sectional view taken along the line BB in FIG. FIG. 15A and FIG.
  • FIG. 15B are explanatory diagrams of the relationship between the swinging position of the adjustment lever and the engagement state of the cam device with respect to the steering device of the first example of the embodiment.
  • A) shows (a) the swinging position of the adjusting lever in the locked state, and (b) the engaged state of the driving cam and the driven cam in the locked state.
  • A) The swinging position of the adjusting lever in the unlocked state, and (b) the engaged state of the driving side cam and the driven side cam in the unlocked state.
  • FIG. 16 is a partially omitted view showing a state in which the tension spring is locked to the base portion of the adjustment lever at the swinging position of the adjustment lever in the unlocked state with respect to the steering device of the first example of the embodiment. .
  • FIG. 17 is a partially omitted view showing a state in which the tension spring is locked to the base of the adjusting lever at the swinging position of the adjusting lever in the unlocked state with respect to the steering device of the second example of the embodiment.
  • . 18 (A) and 18 (B) show a pressing plate incorporated in the steering device of the third example of the embodiment, and FIG. 18 (A) is a plan view of the pressing plate, FIG. 18 (B).
  • FIG. 3 is a front view of the pressing plate.
  • FIG. 19 is a partially omitted enlarged view of a portion corresponding to the left and right intermediate portion of FIG. 6 showing a fourth example of the embodiment.
  • 20 is a partial cross-sectional enlarged view of a portion corresponding to the left and right intermediate portion of FIG.
  • FIG. 21 is a sectional view taken along the line DD of FIG. 22 (A) and 22 (B) show a tension spring incorporated in the steering device of the fifth example of the embodiment
  • FIG. 22 (A) is a perspective view of the tension spring
  • FIG. 22 (B) is an end view of a tension spring.
  • FIG. 23 is a schematic diagram of an example of a conventional steering apparatus to which the present invention can be applied.
  • FIG. 24 is a partial side view of an example of a conventional steering wheel position adjusting device to which the present invention can be applied.
  • 25 is a cross-sectional view taken along the line CC of FIG.
  • FIGS. 1 to 10 and FIG. 15 (A) show a state where the adjustment lever 23a is swung to a locked position where the position of the steering wheel 1 (see FIG. 23) is held.
  • FIG. 15B shows a state where the adjusting lever 23a is swung to an unlock position where the position of the steering wheel 1 can be adjusted.
  • the steering device of this example is supported by a steering shaft 5a that supports the steering wheel 1 at its rear end, and a vehicle body 11 (see FIG. 23), and a plurality of steering shafts 5a are inserted in the axial direction inside the steering shaft 5a. And a cylindrical steering column 6a that is rotatably supported via a rolling bearing.
  • a gear housing 10a constituting an electric assist device is fixed to the front end of the steering column 6a.
  • the gear housing 10a is supported by the lower bracket 32 that can be fixed to the vehicle body 11 so as to be capable of swinging and shifting around the tilt shaft 12a disposed in the width direction.
  • An electric motor (not shown) is supported on the gear housing 10a, and the output torque of the electric motor is applied to the steering shaft 5a via a speed reduction mechanism disposed inside the gear housing 10a. As a result, the force required to operate the steering wheel 1 can be reduced.
  • the steering device of this example includes a telescopic mechanism for adjusting the front-rear position of the steering wheel 1 and a tilt mechanism for adjusting the vertical position of the steering wheel 1 according to the physique and driving posture of the driver.
  • the steering column 6a is fitted to the rear part of the inner column 19a arranged on the front side (lower side) and the front part of the outer column 18a arranged on the rear side (upper side) so as to allow relative displacement in the axial direction.
  • the outer column 18a is supported so as to be movable in the front-rear direction with respect to the support bracket 14a.
  • the steering shaft 5a has a structure in which an inner shaft 33 and an outer shaft 34 are combined so that torque can be transmitted and expanded and contracted by spline engagement or the like.
  • Such a structure constitutes a telescopic mechanism.
  • the steering column can be configured by a single cylindrical member.
  • the steering column 6a and the gear housing 10a are supported so as to be able to swing and displace around the tilt shaft 12a with respect to the vehicle body 11, and the outer column 18a is supported so as to be movable in the vertical direction with respect to the support bracket 14a.
  • a tilt mechanism is configured.
  • the outer column 18a is made of a light alloy such as an aluminum-based alloy or a magnesium-based alloy, and is a sandwiched portion 35 disposed in the front half, and is made of an iron-based alloy such as carbon steel, and is disposed in the latter half. And a cylindrical portion 36 coupled to the shaft 35 in the axial direction.
  • the sandwiched portion 35 is supported so as to be movable in the front-rear direction and the up-down direction with respect to the support bracket 14a.
  • the sandwiched portion 35 of the outer column 18a includes a column fitting portion 37 in its upper half and a displacement bracket 13a in its lower half. As shown in FIG.
  • the column fitting portion 37 includes a slit 20a that is fitted on the rear portion of the inner column 19a and extends in the axial direction at the lower end portion thereof.
  • the displacement bracket 13a includes a pair of sandwiched plate portions 21c and 21d disposed on both sides in the width direction of the slit 20a below the column fitting portion 37. The lower ends of the pair of sandwiched plate portions 21c and 21d are connected in the width direction.
  • the front half of the outer column 18a corresponds to a part of the steering column 6a.
  • the pair of sandwiched plate portions 21c, 21d includes column-side through holes penetrating in the width direction, and includes longitudinal long holes (telescopic adjustment long holes) 16c, 16d extending in the front-rear direction.
  • the longitudinal holes 16c and 16d are mounted on the inner sides of the lower holes 38a and 38b formed in the sandwiched plate portions 21c and 21d and the outer half in the width direction of the lower holes 38a and 38b.
  • the sleeves 39a and 39b are made of synthetic resin and are formed of inner surfaces.
  • the sleeves 39a and 39b are made of a synthetic resin excellent in slidability such as a polyamide resin, a polyacetal resin, and a polytetrafluoroethylene resin.
  • the column-side through hole can be configured by a simple circular hole.
  • the support bracket 14a is made of a metal plate having sufficient rigidity, such as steel or an aluminum alloy, and is connected to the mounting plate portion 40 and the mounting plate portion 40, and is disposed on both sides in the width direction of the displacement bracket 13a.
  • the support plate portions 22c and 22d and the pair of support plate portions 22c and 22d have a pair of vertical long holes (tilt adjustment long holes) 15c and 15d extending in the vertical direction.
  • the mounting plate part 40 is locked to the locking capsule 41 supported and fixed to the vehicle body so as to be able to be detached forward.
  • the mounting plate portion 40 is normally supported with respect to the vehicle body 11 via the locking capsule 41, but in the event of a collision accident, the mounting plate portion 40 is detached forward from the locking capsule 41 based on the impact of the secondary collision, A forward displacement of the outer column 18a is allowed.
  • the mounting plate portion 40 includes a bridge portion 42 disposed in the center portion in the width direction and a pair of side plate portions 43a and 43b disposed on both sides in the width direction.
  • the bridge portion 42 has an inverted U-shaped cross section and is disposed above the sandwiched portion 35 of the outer column 18a.
  • the bridge portion 42 includes a plurality of (three in the illustrated example) ribs 44 arranged in a state of being separated in the front-rear direction, and the rigidity of the bridge portion 42 is ensured.
  • Each of the pair of side plate portions 43a and 43b has a flat plate shape and is provided with a locking notch for opening the locking capsule 41 and opening at the rear end edge thereof.
  • Each of the pair of side plate portions 43a and 43b includes substantially L-shaped locking arm portions 45a and 45b at the width direction inner end portion of the front end portion thereof.
  • the locking arm portions 45a and 45b are bent at a substantially right angle downward from the widthwise inner ends of the front end portions of the pair of side plate portions 43a and 43b and project forward from the lower end portions thereof.
  • Have The shape of the locking arm portions 45a and 45b and the formation position thereof are preferably symmetrical with respect to the width direction.
  • the upper ends of the pair of support plate portions 22c and 22d are fixed to both ends in the width direction of the lower surface of the bridge portion 42 by welding.
  • the pair of support plate portions 22c and 22d are disposed substantially parallel to each other on both sides in the width direction of the sandwiched portion 35 of the outer column 18a.
  • the pair of support plate portions 22c and 22d includes a pair of vertical elongated holes 15c and 15d extending in the vertical direction in a partial arc shape with the tilt shaft 12a as the center.
  • the pair of support plate portions 22c and 22d includes reinforcing protrusions 46a and 46b extending in the vertical direction at the front end portions thereof.
  • the upper end portions of the reinforcing protrusions 46 a and 46 b are not continuous with the bridge portion 42.
  • the tension springs 73a and 73b are arranged on both outer sides in the width direction of the pair of support plate portions 22c and 22d, reinforcement is performed in order to suppress the protruding amount to the outer side in the width direction while securing the section modulus.
  • the ridges 46a, 46b have a circular arc shape in which the front end portion is folded inward in the width direction.
  • the pair of support plate portions 22c and 22d includes bending plate portions 47a and 47b that extend in the vertical direction and bend substantially perpendicularly toward the outer side in the width direction at the rear end portions.
  • the reinforcing protrusions 46a and 46 and the bent plate portions 47a and 47b are provided to increase the bending rigidity (torsional strength) of the support plate portions 22c and 22d.
  • the shape of the vertically elongated hole is not limited to the partial arc shape with the tilt axis as the center, and alternatively, a linear shape that extends in the backward direction as it goes upward can be adopted.
  • the adjusting rod 17a is disposed so as to pass through the pair of longitudinal elongated holes 16c, 16d and the pair of vertically elongated holes 15c, 15d in the width direction.
  • the adjustment rod 17a includes a head portion 48 at one end portion and a male screw portion 49 at the other end portion.
  • a disc spring 50, an adjusting lever 23a, and a cam device 24a are arranged between the outer side surfaces in order from the outside in the width direction.
  • a nut 28a and a thrust bearing 29a are sequentially arranged from the outer side in the width direction around a portion protruding from the outer surface of the other support plate portion 22d of the pair of support plate portions 22c and 22d.
  • a pressing plate 30a is arranged.
  • the nut 28a is screwed into a male screw portion 49 at the other end of the adjustment rod 17a.
  • the heads 48 and nuts 28a arranged at both ends of the adjusting rod 17a cannot be displaced relative to each other in the axial direction of the adjusting rod 17a. It functions as a displacement restricting portion that prevents displacement outward in the direction.
  • the adjusting lever 23a and the cam device 24a constitute an expansion / contraction mechanism.
  • the distance between the driven cam 26a and the pressing plate 30a constituting the pair of pressing portions and the pair of support plate portions 22c. , 22d can be expanded and contracted.
  • the magnitude of the clamping force with which the support bracket 14a clamps the displacement bracket 13a from both sides in the width direction can be adjusted.
  • the adjusting lever 23a is a member for swinging when the driver adjusts the position of the steering wheel 1.
  • the adjustment lever 23a is made of a metal plate such as a steel plate or a stainless steel plate, and has a long shape bent in a substantially crank shape.
  • the adjustment lever 23a is disposed so as to extend rearward (driver's seat side) and downward as it goes toward the distal end side.
  • the adjustment lever 23a includes a flat plate-like base portion 51 at a front end side portion (upper end side portion) thereof.
  • the base 51 includes a substantially rectangular mounting hole 52 that penetrates in the plate thickness direction.
  • the base 51 is provided with a spring locking hole 53 in a substantially trapezoidal portion located in front of the attachment hole 52.
  • the adjustment lever 23a is fixed to the driving cam 25a so as not to be relatively rotatable by using the mounting hole 52. For this reason, the driving cam 25a can rotate relative to the driven cam 26a by the swinging operation of the adjusting lever 23a.
  • the cam device 24a in the state shown in FIGS. 15A and 15A in which the adjustment lever 23a is swung upward, the cam device 24a is in a locked state, and the adjustment lever 23a is swung downward in FIG. 15B. In the state shown in (a), the cam device 24a is unlocked.
  • the spring locking hole 53 is not a simple circular hole as shown in FIG. 16, but has a substantially triangular opening shape (which is a triangular hole) disposed on the front side (left side in FIG. 16). It has a substantially tear-shaped opening shape in which the portion 79 and a large-diameter hole portion 80 having a substantially semicircular opening shape disposed on the rear side (right side in FIG. 16) are combined.
  • the guide hole 79 has a pair of linear guide sides 81a and 81b that are inclined toward each other toward the front side, and a partially arcuate connection portion that connects the front ends of the pair of guide sides 81a and 81b. 82.
  • the pair of guide sides 81 a and 81 b are line symmetric with respect to an imaginary straight line N that is orthogonal to the central axis O 17 of the adjustment rod 17 a and passes through the central portion in the circumferential direction of the connecting portion 82.
  • the center O 80 of the large-diameter hole 80 is located on the virtual straight line N.
  • the inner diameter d 80 of the large diameter hole portion 80 is sufficiently larger than the diameter D 74 of the hook portion 74b of the tension spring 73a (d 80> D 74) .
  • the curvature radius of the connecting portion 82 is smaller than one half of the wire diameter D 74 of the hook portion 74b.
  • the size of the included angle ⁇ 3 between the pair of guide sides 81a and 81b is determined in consideration of the wire diameter D 74 of the hook portion 74b, the shape of the base portion 51, and the like, for example, in the range of 30 degrees to 90 degrees.
  • the angle is preferably set in the range of 45 to 75 degrees. In the illustrated example, the included angle ⁇ 3 is 60 degrees.
  • the spring locking hole 53 has a substantially tear-like shape as a whole, which is a combination of the substantially triangular opening shape of the guide hole portion 79 and the substantially semicircular opening shape of the large-diameter hole portion 80. It has an opening shape.
  • the shape of the spring locking hole is not limited to this shape, and the following shapes can also be adopted. That is, the guide hole portion can have a substantially trapezoidal opening shape instead of the substantially triangular opening shape.
  • the large-diameter hole portion can have a substantially trapezoidal opening shape that is sufficiently larger than the wire diameter D 74 of the hook portion 74b of the tension spring 73a.
  • the spring locking hole may have a substantially triangular opening shape as a whole, which is a combination of the substantially triangular opening shape of the guide hole portion and the substantially trapezoidal opening shape of the large diameter hole portion.
  • the spring locking hole may have a substantially trapezoidal opening shape as a whole, which is a combination of a substantially trapezoidal opening shape of the guide hole portion and a substantially trapezoidal opening shape of the large diameter hole portion.
  • the cam device 24a is composed of a combination of a driving side cam 25a and a driven side cam 26a.
  • the driving side cam 25a is arranged on the outer side in the width direction
  • the driven side cam 26a is arranged on the inner side in the width direction.
  • the driving side cam 25a may be disposed on the inner side in the width direction
  • the driven side cam may be disposed on the outer side in the width direction.
  • the drive cam 25a constitutes an expansion / contraction mechanism. In this case, the direction of the width direction in the following description is reversed.
  • the drive side cam 25a is made of sintered metal, has an annular plate shape as a whole, and includes a center hole 54 through which the adjustment rod 17a is inserted.
  • the driving cam 25a has an inner surface that is one side surface in the width direction and an outer surface that is the other side surface in the width direction.
  • the drive-side cam 25a includes a drive-side cam surface 55 that is an uneven surface in the circumferential direction on the inner surface.
  • the driving cam 25a is provided with a substantially rectangular fitting convex portion 56 in front view for fitting and fixing the base portion 51 of the adjusting lever 23a on the outer surface.
  • the drive-side cam surface 55 has a flat-side drive-side base surface 57 and a plurality of circumferentially equidistant positions (four locations in the illustrated example) on the drive-side base surface 57 within the width direction corresponding to one side in the width direction. And a drive-side convex portion 58 having a substantially trapezoidal cross section.
  • a drive-side stopper surface 59 is provided on the front side in the unlocking direction, which is the rotation direction of the drive-side cam 25a when switching to the unlocked state, on both sides in the circumferential direction of the drive-side convex portion 58, and the rear side thereof.
  • a driving side guide slope 60 is provided on the side.
  • the drive-side guide slope 60 and the drive-side stopper face 59 have opposite inclination directions with respect to the circumferential direction, and the drive-side stopper face 59 has a greater inclination angle with respect to the drive-side base face 57. Greater than 60. In this example, the drive side stopper surface 59 is not practically used.
  • the drive side cam 25a is fixed to the base 51 of the adjustment lever 23a and adjusted.
  • the adjustment lever 23a and the adjustment rod 17a engage with each other so as not to rotate relative to each other by, for example, an uneven fitting (not shown), so that the drive cam 25a can rotate in synchronization with the adjustment rod 17a.
  • the drive side cam is fitted on the adjustment rod so as to be able to rotate relative to the adjustment rod. In this case, the drive cam rotates by the swing operation of the adjustment lever, but the adjustment rod does not rotate.
  • the driven cam 26a is made of sintered metal, has an annular plate shape as a whole, and is provided with a central hole 61 through which the adjusting rod 17a is inserted, like the driving cam 25a.
  • the driven cam 26a has an inner surface that is one side surface in the width direction and an outer surface that is the other side surface in the width direction.
  • the driven cam 26a includes a driven cam surface 62 that is an uneven surface in the circumferential direction on the outer surface.
  • the driven cam 26a is provided with a substantially rectangular plate-like engagement convex portion 27a protruding inward in the width direction on the inner side surface.
  • the driven-side cam surface 62 is directed to a widthwise outer side corresponding to the other side in the width direction from a plurality of equally spaced circumferential positions of the driven-side base bottom surface 63 and the driven-side base bottom surface 63. It has a substantially trapezoidal cross section and has the same number of driven side convex portions 64 as the driving side convex portions 58.
  • a driven side guide slope 65 is provided on the front side in the unlocking direction of both sides in the circumferential direction of the driven side convex portion 64, and a driven side stopper surface 66 is provided on the rear side thereof. Yes.
  • the driven-side guide slope 65 and the driven-side stopper surface 66 are opposite in the inclination direction with respect to the circumferential direction, and the inclination angle with respect to the driven-side base surface 63 is larger in the driven-side stopper surface 66. It is larger than the driven side guide slope 65. In this example, the driven-side stopper surface 66 is not substantially used.
  • the driven cam 26a is fitted on the adjusting rod 17a so as to be capable of relative rotation with respect to the adjusting rod 17a and relative displacement in the axial direction of the adjusting rod 17a.
  • the engaging convex part 27a engages with the up-down direction long hole 15c of one support plate part 22c so that only the displacement along the up-down direction long hole 15c is possible. For this reason, the driven cam 26a can be moved up and down along the up-and-down direction long hole 15c, but exists between the front-and-rear side edge of the up-and-down direction long hole 15c and the front-and-rear side surface of the engaging convex part 27a. Except for a slight rotation caused by the gap, it does not rotate greatly.
  • the adjustment lever 23a When adjusting the position of the steering wheel 1, the adjustment lever 23a is swung downward from the lock position shown in FIGS. 15A and 15A to the unlock position shown in FIGS. Accordingly, as shown in FIGS. 15A and 15B, the driving side cam 25a rotates in the unlocking direction, and as shown in FIGS. 15B and 15B, the driving side convex portion 58 and the driven side are driven. It will be in the unlocking state by which the side convex part 64 was alternately arrange
  • the surface pressure of the contact portion between the inner surface of the support plate portions 22c and 22d and the outer surface of the sandwiched plate portions 21c and 21d is reduced or lost, and at the same time, the inner diameter of the column fitting portion 37 of the outer column 18a is reduced. It expands elastically, and the surface pressure of the contact portion between the inner peripheral surface of the column fitting portion 37 and the rear outer peripheral surface of the inner column 19a decreases.
  • the vertical position and the front / rear position of the steering wheel 1 can be adjusted within a range in which the adjustment rod 17a can move inside the pair of vertical slots 15c, 15d and the pair of longitudinal slots 16c, 16d. It becomes possible.
  • the adjustment lever 23a is swung upward from the state shown in FIGS. Rotate 25a in the locking direction.
  • the cam device that constitutes the expansion / contraction device in a state (locked state) where the tip surface of the drive-side convex portion 58 and the tip surface of the driven-side convex portion 64 abut each other The dimension in the width direction of 24a is increased, and the distance between the driven cam 26a constituting the pair of pressing portions and the pressing plate 30a (the interval between the inner surfaces of the pair of support plate portions 22c and 22d) is reduced.
  • the disc spring 50 is made of a metal such as carbon steel, carbon tool steel, or spring steel, has an annular shape, is externally fitted to a portion near one end of the adjustment rod 17a, and is an inner surface of the head 48 of the adjustment rod 17a. And the outer surface of the base 51 of the adjusting lever 23a.
  • the disc spring 50 imparts elasticity in a direction away from each other to the inner surface of the head 48 and the outer surface of the base 51. For this reason, even when the clamping force is released in order to adjust the position of the steering wheel 1, the cam device 24a has a width direction between the inner surface of the head 48 and the outer surface of the one support plate portion 22c.
  • the occurrence of rattling can be suppressed, and the occurrence of rattling in the width direction between the inner surface of the nut 28a and the outer surface of the other support plate portion 22d can be suppressed in the thrust bearing 29a and the pressing plate 30a. it can.
  • the disc spring 50 can be omitted because the cam device 24a and the thrust bearing 29a can be prevented from wobbling in the width direction by using the moment acting on the pressing plate 30a.
  • the pressing plate 30a is made of a metal plate such as a cold rolled steel plate (SPCC) or a hot rolled steel plate (SPHC), and has a crank shape as a whole.
  • the pressing plate 30a is fitted on a portion closer to the other end of the adjusting rod 17a so as to be capable of relative rotation with respect to the adjusting rod 17a and relative displacement in the axial direction of the adjusting rod 17a.
  • the pressing plate 30a has an insertion hole 67 through which the adjustment rod 17a is inserted, and is attached to the adjustment rod 17a at one place in the circumferential direction of the annular plate body 68 and the outer peripheral edge of the plate body 68. Arranged and provided with a substantially L-shaped locking plate portion 69.
  • the base half portion 70 of the locking plate portion 69 has a flat plate shape and extends from the outer peripheral edge of the plate body 68 toward the outside in the width direction (the axial direction of the plate body 68).
  • the front half 71 of the locking plate 69 has a flat plate shape and extends from the outer end (tip) in the width direction of the base half 70 toward the side opposite to the plate body 68 so as to be bent at a substantially right angle.
  • the plate body 68 is disposed between the outer surface of the other support plate portion 22d and the inner surface of the thrust bearing 29a.
  • the front half 71 of the locking plate 69 includes a spring locking hole 72 having a circular opening shape.
  • the distance from the rotation center (center axis) of the adjustment rod 17a to the spring engagement hole 72 is the distance from the rotation center of the adjustment rod 17a to the spring engagement hole 53 provided in the base 51 of the adjustment lever 23a.
  • the plate main body 68 and the front half 71 of the locking plate portion 69 are arranged in parallel to each other, and the base half 70 of the locking plate 69 is in relation to the plate main body 68 and the front half 71 of the locking plate 69. Arranged at right angles.
  • the pressing plate 30a corresponds to a locked member.
  • the thrust bearing 29a has a pair of ring-shaped race rings and a plurality of needles arranged radially between the pair of race rings.
  • the thrust bearing 29a supports a thrust load acting on the pressing plate 30a from the nut 28a, and enables the nut 28a to reciprocate.
  • a pair of tension springs 73a and 73b are disposed on both outer sides in the width direction of the pair of support plate portions 22c and 22d of the support bracket 14a.
  • the pair of tension springs 73a and 73b are made of spring steel such as stainless steel and piano wire, have the same spring constant, and have the same length in the free state. Consists of. As shown in FIG.
  • the center axes O a and O b of the pair of tension springs 73a and 73b are directed outward in the width direction toward the front with respect to the center axis O 6 of the steering column 6a. It is arranged with a slight inclination in the direction of (separating) several degrees (for example, 1 degree to 5 degrees) or arranged in parallel. As shown in FIGS. 6 and 7, the central axes O a and O b of the pair of tension springs 73a and 73b are several tens of degrees in the upward direction toward the front (for example, 30 to 50 degrees). It is inclined to some extent. In this example, the inclination angle inclined in the width direction with respect to the central axis O 6 of the steering column 6a is substantially the same in the one tension spring 73a and the other tension spring 73b.
  • One tension spring 73a of the pair of tension springs 73a and 73b includes a U-shaped hook portion 74a disposed at one end, a U-shaped hook portion 74b disposed at the other end, and an intermediate And a coil part 77a arranged in the part.
  • the hook portion 74a is locked to the locking arm portion 45a of the one side plate portion 43a from the outside in the width direction.
  • the hook portion 74b is locked from the inner side in the width direction to the spring locking hole 53 of the base 51 of the adjustment lever 23a.
  • one tension spring 73a is arrange
  • One tension spring 73a applies a force F1 directed obliquely upward to the base 51 of the adjusting lever 23a.
  • the front side surface of the engaging convex portion 27a of the driven cam 26a is ,
  • One of the support plate portions 22c is elastically pressed against the front edge of the up-down direction long hole 15c.
  • the hook portion 74b in a state where the hook portion 74b is locked in the spring locking hole 53, the hook portion 74b is in a direction approaching the connecting portion 82 by the elastic restoring force exerted by the coil portion 77a.
  • the pair of guide sides 81a and 81b are pulled in a direction in which the interval is reduced.
  • the hook portion 74b is elastically pressed between the pair of guide sides 81a and 81b (bite like a wedge) and is elastically pressed against the pair of guide sides 81a and 81b.
  • the hook portion 74b comes into contact only with the pair of guide sides 81a and 81b.
  • the inner diameter d 80 of the large diameter hole portion 80 since sufficiently larger than the wire diameter D 74 of the hook portion 74b, the hook portion 74b is loosely insertable to the large diameter portion 80.
  • the other tension spring 73b of the pair of tension springs 73a and 73b includes a U-shaped hook portion 75a disposed at one end, a U-shaped hook portion 75b disposed at the other end, And a coil part 77b arranged in the part.
  • the hook portion 75a is locked to the locking arm portion 45b of the other side plate portion 43b from the outside in the width direction.
  • the hook portion 75b is locked from the inner side in the width direction to the spring locking hole 72 of the front half portion 71 of the locking plate portion 69 of the pressing plate 30a.
  • the other tension spring 73b is arranged so as to be bridged between the other side plate portion 43b and the pressing plate 30a.
  • the other tension spring 73b applies a force F2 that is directed obliquely upward to the pressing plate 30a.
  • a pair of tension springs 73a and 73b disposed on both outer sides in the width direction of the support bracket 14a are applied to the both ends of the adjustment rod 17a in an obliquely upward direction. . Therefore, an upward force is applied to the outer column 18a, so that the steering column 6a can be prevented from tilting when the position of the steering wheel 1 is adjusted (unclamped). Adjustment can be performed with a light force.
  • the adjustment lever 23a is swung in a direction to reduce the width direction dimension of the cam device 24a, and the adjustment lever 23a is moved to the unlock position, that is, the adjustment lever 23a is rotated downward.
  • the total length L1 of the inclination angle ⁇ 1 and one tension spring 73a with respect to the center axis O 6 of the steering column 6a of one of the tension springs 73a shown in FIG.
  • the pressing plate 30a is pressed against the outer surface of the other support plate portion 22c and the inner surface of the thrust bearing 29a based on the pulling force of the other tension spring 73a. Therefore, when the adjustment rod 17a is moved in the vertical direction. However, the rotational phase hardly changes. For this reason, when the adjusting lever 23a is moved to the unlocked position regardless of the vertical position of the adjusting rod 17a, the inclination angle with respect to the steering column 6a and the total length thereof are changed between the one tension spring 73a and the other tension spring 73b. Are the same as each other.
  • the direction of action of the force of the pair of tension springs 73a and 73b is the tilt shaft 12a and the adjustment rod 17a. It faces upward by a predetermined angle (for example, about 10 to 30 degrees) from the direction of the virtual straight line M (see FIG. 7) orthogonal to the direction.
  • a predetermined angle for example, about 10 to 30 degrees
  • the angle between the direction of action of the central axis O 6 and the tension spring 73a, 73b of the force of the steering column 6a is greater than the angle between the center axis O 6 of the steering column 6a and the virtual straight line M.
  • a pair of tension springs are located relative to the center axis of the steering column with respect to the base of the adjustment lever and the locked member.
  • the structure, shape, and length (attachment of both ends) are not limited to the above-mentioned preferred examples as long as the same magnitude of force can be applied in the direction of action directed diagonally forward and upward by the same angle. It is also possible to adopt a configuration in which the position) differs between one tension spring and the other tension spring.
  • the force applied from one tension spring 73a to the base 51 of the adjusting lever 23a acts as a drag (brake) that suppresses the rotation of the drive cam 25a.
  • a gap 76a is formed between the distal end surface of the driving-side convex portion 58 and the driven-side base surface 63, and the driven side A gap 76 b is formed between the distal end surface of the side convex portion 64 and the driving side base surface 57, and a gap 76 c is formed between the driving side stopper surface 59 and the driven side stopper surface 66.
  • the steering device of the present example when the adjustment lever 23a is swung downward from the clamp position, the leading end surface of the driving-side convex portion 58, the driven-side base surface 63, and the leading end surface of the driven-side convex portion 64 It is possible to prevent the generation of abnormal noise (metal contact sound) due to the violent collision between the driving side base surface 57 and the driving side stopper surface 59 and the driven side stopper surface 66. Further, as shown in FIGS. 15B and 15B, the clearance 76a between the front end surface of the driving side convex portion 58 and the driven side base surface 63, and the front end surface of the driven side convex portion 64 and driving.
  • abnormal noise metal contact sound
  • the width direction dimension of the cam device 24a in the unlocked state can be increased by the gap 76b between the side base bottom surface 57 and the side base bottom surface 57. For this reason, it is possible to prevent the cam device 24a from rattling in the width direction between the inner surface of the head 48 and the outer surface of the one support plate portion 22c, and the inner surface of the nut 28a and the other support are supported. It is possible to suppress the occurrence of rattling in the width direction between the thrust bearing 29a and the pressing plate 30a with the outer surface of the plate portion 22d. Further, since the rotation of the drive cam 25a is braked by the one tension spring 73a, the adjustment lever 23a is vibrated vigorously, and a part of the adjustment lever 23a is prevented from colliding with the finger of the passenger.
  • the width direction dimension of the cam device 24a in the unlocked state can be increased by the gap 76b between the side base bottom surface 57 and the side base bottom surface 57. For this reason, it is possible to prevent the cam device 24
  • the force applied from the other tension spring 73b to the pressing plate 30a causes a moment to act on the pressing plate 30a.
  • the hook portion 75b of the other tension spring 73b is the first half of the locking plate portion 69 disposed at a position that is disengaged (offset) in the width direction with respect to the plate body 68 that is externally fitted to the adjustment rod 17a. Locked to the portion 71.
  • the pressing plate 30a is provided with a bent portion between the plate main body 68 and the base half portion 70 of the locking plate portion 69 based on the force F2 acting from the other tension spring 73b. And a moment in the direction of the arrow ⁇ acts around an imaginary straight line Z extending in the extending direction of the bent portion.
  • the plate main body 68 applies forces in directions away from each other to the outer surface of the other support plate portion 22d and the inner surface of the thrust bearing 29a. Therefore, similarly to the disc spring 50, even when the clamping force is released, the cam device 24a has a width between the inner surface of the head 48 that is the displacement restricting portion and the outer surface of the one support plate portion 22c. It is possible to suppress the occurrence of rattling in the direction, and it is possible to suppress the occurrence of rattling in the width direction of the thrust bearing 29a between the inner surface of the nut 28a serving as a displacement restricting portion and the outer surface of the plate body 68. .
  • the hook portion 74b is paired with a pair of guide sides by the elastic restoring force exerted by the coil portion 77a in a state where the hook portion 74b of the tension spring 73a is locked in the spring locking hole 53 of the adjustment lever 23a. It is elastically pressed between 81a and 81b, and is elastically pressed against a pair of guide sides 81a and 81b. For this reason, even when the vertical position of the steering wheel 1 is adjusted or when the adjustment lever 23a is swung, the movement of the hook portion 74b is restricted by the pair of guide sides 81a and 81b, and the hook portion 74b becomes a spring locking hole. It can prevent moving (sliding) along the inner periphery of 53.
  • the inner diameter d 80 of the large diameter hole portion 80, and sufficiently larger than the diameter D 74 of the hook portion 74b, a hook portion 74b, is loosely insertable to the large diameter portion 80. Therefore, since the hook portion 74b can be easily inserted into the spring locking hole 53, the workability of the assembly operation of the steering device can be ensured.
  • a pair of tension springs 73a and 73b are disposed on both outer sides in the width direction of the pair of support plate portions 22c and 22d of the support bracket 14a, and the base 51 of the adjustment lever 23a disposed at both ends of the adjustment rod 17a. And the force which faced the diagonally front upper direction is respectively provided with respect to the press plate 30a.
  • the direction in which the force is applied by the pair of tension springs 73a and 73b is not upward along the extension direction of the pair of vertical elongated holes 15c and 15d, but is directed toward the diagonally upper front.
  • the component force is kept small.
  • the direction of action of the force of the pair of tension springs 73a and 73b is The push-up force is prevented from becoming too low by facing upward by a predetermined angle from the direction of the virtual straight line M perpendicular to the center axis of the tilt shaft 12a and the center axis of the adjustment rod 17a.
  • the pair of tension springs 73a and 73b causes the base 51 of the adjustment lever 23a and the pressing plate 30a to face each other in the same direction. That power is given. For this reason, when the position of the steering wheel 1 is adjusted, the posture of the adjustment rod 17a can be stabilized, and the adjustment rod 17a can be prevented from being tilted up and down.
  • the direction of the force applied by the pair of tension springs 73a and 73b is not the upper direction along the extension direction of the pair of vertical elongated holes 15c and 15d, but the direction facing diagonally forward and upward.
  • the upward component force can be kept small, and a frictional force can be generated between the front side surface of the engaging convex portion 27a and the front side edge of the vertically elongated hole 15c. For this reason, when the clamping force is released, the position of the steering wheel 1 can be kept at the position where the clamping force is released. Therefore, it is possible to realize a structure that does not cause a sudden jump or a sudden drop in the steering wheel 1 when the clamping force that has been conventionally required for the steering device is released.
  • component forces directed outward in the width direction can be applied to the base 51 of the adjustment lever 23a and the pressing plate 30a. Also from this surface, it is possible to prevent the cam device 24a and the thrust bearing 29a from rattling in the width direction when the clamping force is released.
  • the drive cam 25a tends to rotate vigorously.
  • the driven cam 26a also tends to rotate around the adjustment rod 17a based on the concave and convex engagement between the driving cam surface 55 and the driven cam surface 62.
  • the front side surface of the engagement convex portion 27a of the driven cam 26a is elastically pressed against the front edge of the vertical slot 15c by the elasticity of the tension spring 73a. It is possible to effectively prevent the cam 26a from rotating. For this reason, it is possible to prevent abnormal noise (metal contact sound) from being generated when the front and rear side surfaces of the engaging convex portion 27a and the front and rear side edges of the vertical elongated holes 15c collide with force.
  • the steering wheel 1 When adjusting the front-rear position of the steering wheel 1, the steering wheel 1 is moved forward as much as possible, and the adjustment rod 17a is moved to the pair of front and rear direction long holes 16c, 16d and the pair of up and down direction long holes 15c. Also, when sandwiched between the front side edge of 15d, the front side surface of the engagement convex portion 27a is in contact with the front side edge of the vertical elongated hole 15c in advance, so that the front side surface of the engagement convex portion 27a is It is also possible to prevent a collision sound from being generated due to a violent collision with the front side edge of the directional elongated hole 15c.
  • the present invention is applied to a steering apparatus including both a tilt mechanism and a telescopic mechanism, but the present invention can also be applied to a steering apparatus including only a tilt mechanism.
  • a combination of a cam device and an adjustment lever is adopted as the expansion / contraction device, and a combination of a driven cam and a pressure plate constituting the cam device is adopted as a pair of pressing portions.
  • the known configuration can also be employed.
  • a base having a head at the base and a male screw at the tip is formed, and a nut having a female screw that can be screwed onto the male screw is attached to the tip of the bolt.
  • the structure which rotates the said nut with an adjustment lever is also employable.
  • the adjusting lever and the bolt head or the nut constitute an expansion / contraction device, and the inner side surface of the bolt head and the inner side surface of the nut constitute a pair of pressing portions.
  • the base 51 of the adjusting lever 23a and the pressing plate 30a function as a locked member.
  • the locked member can also be disposed independently of these members.
  • it can also be comprised by any one press part of the other one pair of press parts, or its part, or an expansion / contraction mechanism or its part.
  • a member such as a cam device or a washer, or an adjustment rod disposed on a portion of the adjustment rod 17a that protrudes from the outer surface of one of the support plate portions 22c and 22d.
  • It can also be configured by a member such as a bearing ring of a thrust bearing, which is disposed in a portion protruding from the outer surface of the other support plate portion 22d of the pair of support plate portions 22c and 22d.
  • the shape of the base 51a of the adjustment lever 23b is changed from the structure of the first example of the embodiment.
  • the front portion of the base portion 51a has a tapered generally triangular shape, perpendicular to the central axis O 17 of the adjusting rod 17a, and a virtual straight line N passing through the circumferential center portion of the connecting portion 82 is , Passing through the top of the base 51a.
  • the hook portion 74b of the tension spring 73a is elastically pushed between the pair of guide sides 81a and 81b constituting the guide hole portion 79 having a substantially triangular opening shape. For this reason, it can prevent that the hook part 74b moves along the inner periphery of the spring latching hole 53, and can suppress that a stick slip generate
  • Other configurations and operational effects of the second example of the embodiment are the same as those of the first example of the embodiment.
  • the pressing plate 30b used in the present example has an insertion hole 67a for inserting the adjustment rod 17a, and an annular plate body 68a that is externally fitted to the adjustment rod 17a, and a circumference of the outer peripheral edge of the plate body 68a.
  • a flat plate-like locking plate portion 69a disposed in one direction is provided.
  • the locking plate portion 69a extends obliquely in the direction toward the front side (the radially outer side of the plate body 68) from the outer peripheral edge of the plate body 68a toward the outer side in the width direction (the axial direction of the plate body 68).
  • the locking plate portion 69a includes a spring locking hole 72a for locking the end portion of the other tension spring 73b at a position deviated (offset) from the plate body 68a in the width direction.
  • a moment can be applied to the pressing plate 30b based on the force applied to the pressing plate 30b from the other tension spring 73b. That is, the end portion of the other tension spring 73b is in the spring locking hole 72a disposed at a position out of the locking plate portion 69a in the width direction with respect to the plate body 68a externally fitted to the adjustment rod 17a. Locked.
  • the bending portion between the plate main body 68a and the base end portion of the locking plate portion 69a serves as a fulcrum, and the extending direction of the bending portion A moment in the direction of the arrow ⁇ acts around an imaginary straight line Z extending in the direction of.
  • the plate body 68a can apply forces in directions away from each other to the outer surface of the other support plate portion 22d and the inner surface of the thrust bearing 29a.
  • Other configurations and operational effects of the third example of the embodiment are the same as those of the first example or the second example of the embodiment.
  • a pair of tension springs 73a is used to prevent noise from being generated from the pair of tension springs 73a and 73b when the vertical position of the steering wheel 1 is adjusted or when the adjustment lever 23a is swung.
  • 73b includes a damper member 78 disposed inside the coil portions 77a and 77b.
  • the damper member 78 is made of an elastic material such as rubber or synthetic resin, and has an annular shape and a substantially rectangular cross-sectional shape as a whole in a free state.
  • the damper member 78 is disposed inside the coil portions 77a and 77b in a state where the damper member 78 is deformed. Specifically, in a state where the portions of the damper member 78 located on the opposite sides in the diametrical direction are crushed so as to be close to each other (folded), and the entire damper member 78 is deformed into a linear shape (plate shape), The damper member 78 is inserted so as to be pushed into the coil portions 77a and 77b. In a state where the damper member 78 is disposed inside the coil portions 77a and 77b, the outer peripheral surface of the damper member 78 elastically contacts the inner peripheral surfaces of the coil portions 77a and 77b.
  • the damper member 78 moves in the axial direction of the coil portions 77a and 77b.
  • the length (folded diameter) of the damper member 78 in the coil portions 77a and 77b is regulated so as not to fall off from the inside of 77b.
  • the upper end portion of the damper member 78 is in contact with the lower surfaces of the locking arm portions 45a and 45b.
  • the length (engagement allowance) of the damper member 78 existing inside the coil portions 77a and 77b is sufficiently larger than, for example, the distance from the upper end surface of the coil portions 77a and 77b to the lower surfaces of the locking arm portions 45a and 45b. Secured to be longer.
  • the lower end portion of the damper member 78 is the base 51 of the adjusting lever 23a and the locking plate portion 69 of the pressing plate 30a (FIGS. 7 and 7).
  • the damper member 78 is disposed so that the damper member 78 disposed inside the coil portions 77a and 77b is not damaged by the attachment jig of the tension springs 73a and 73b during the attaching operation of the tension springs 73a and 73b. Length, in particular, the amount of protrusion from the coil portions 77a and 77b is restricted.
  • the hook portion 75b (see FIG. 7) of the tension spring 73b is connected to the spring locking hole 72 of the pressing plate 30a.
  • the amount of movement along the inner periphery of the is small.
  • the damper member 78 may be arranged only inside the coil part 77a constituting one tension spring 73a and not arranged inside the coil part 77b constituting the other tension spring 73b.
  • Other configurations and operational effects of the fourth example of the embodiment are the same as those of the first to third examples of the embodiment.
  • a damper member 78a is disposed outside the coil portions 77a and 77b constituting the tension springs 73a and 73b.
  • the damper member 78a is made of an elastic material such as rubber or synthetic resin, and has a cylindrical shape having an inner diameter slightly smaller than the outer diameter of the coil portions 77a and 77b in a free state.
  • the damper member 78a is fitted on the outside of the coil portions 77a and 77b in a state where the inner diameter is slightly expanded elastically. In a state where the damper member 78a is disposed outside the coil portions 77a and 77b, the inner peripheral surface of the damper member 78a elastically contacts the outer peripheral surface of the coil portions 77a and 77b.
  • the damper member 78a since the damper member 78a can be visually recognized from the outside, forgetting to attach the damper member 78a can be prevented.
  • the damper member 78a is externally fitted to the coil portions 77a and 77b, and the hook portions 74a, 74b, 75a, and 75b existing on both sides of the coil portions 77a and 77b are the locking arm portions 45a and 45b, the adjustment lever 23a, and Since it is each latched by the press plate 30a, it can prevent effectively that the damper member 78a falls off.
  • Other configurations and operational effects of the fifth example of the embodiment are the same as those of the first to third examples of the embodiment.

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

Abstract

L'invention concerne un dispositif de direction dans lequel la collision brutale d'une saillie de mise en prise d'une came côté entraîné et d'un trou long vertical peut être empêchée et l'apparition d'un glissement de direction entre un ressort de traction et un levier de réglage peut être supprimée, et avec lequel la maniabilité d'un travail d'assemblage peut être assurée. Un ressort de traction (73a) est ponté entre un palier de support (14a) et une section de base (51) d'un levier de réglage (23a). Un trou de verrouillage de ressort (53) est constitué par la combinaison : d'une section de trou de guidage (79) présentant une forme d'ouverture triangulaire disposée sur son côté avant ; et d'une section de grand diamètre (80) présentant une forme d'ouverture semi-circulaire disposée sur son côté arrière. La section de crochet (74b) du ressort de traction (73a) est élastiquement insérée entre une paire de côtés de guidage (81a, 81b) de la section de trou de guidage (79) et est poussée élastiquement contre la paire de côtés de guidage (81a, 81b).
PCT/JP2019/013373 2018-03-27 2019-03-27 Dispositif de direction WO2019189472A1 (fr)

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
JP2018059631 2018-03-27
JP2018-059631 2018-03-27
JP2018074164 2018-04-06
JP2018-074164 2018-04-06
JP2018-075911 2018-04-11
JP2018075911 2018-04-11
JP2018-156901 2018-08-24
JP2018156901 2018-08-24
JP2018-174386 2018-09-19
JP2018174386 2018-09-19

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WO2019189472A1 true WO2019189472A1 (fr) 2019-10-03

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50138967A (fr) * 1974-04-25 1975-11-06
JPS5746143U (fr) * 1980-09-01 1982-03-13
JPS57184335U (fr) * 1981-05-19 1982-11-22
JP2014083906A (ja) * 2012-10-22 2014-05-12 Nsk Ltd チルト式ステアリング装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50138967A (fr) * 1974-04-25 1975-11-06
JPS5746143U (fr) * 1980-09-01 1982-03-13
JPS57184335U (fr) * 1981-05-19 1982-11-22
JP2014083906A (ja) * 2012-10-22 2014-05-12 Nsk Ltd チルト式ステアリング装置

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