JP2017132323A - Position adjustment device for steering wheel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a structure capable of increasing a force to hold a steering wheel at a position after adjustment, and also capable of facilitating position adjustment of the steering wheel.SOLUTION: A tip half part of a swing friction plate 25 is held between an outside surface of one support plate part 20a and one inside surface of one pressing part. A circular hole 30 disposed at a base end part of the swing friction plate 25 is swingably fitted onto a cylindrical part 31 disposed on the outside surface of the one support plate part 20a integrally with the one support plate 20a in the state of projecting outward in the width direction thereof, and an adjustment rod is inserted in a guide long hole 32 disposed at a tip half part of the swing friction plate 25. A leaf spring 35 is held between the outside surface of the one support plate part 20a and one side surface of the swing friction plate 25 around the cylindrical part 31.SELECTED DRAWING: Figure 4

Description

  The present invention relates to an improvement in a position adjustment device for a steering wheel for adjusting the vertical position of the steering wheel in accordance with a driver's physique and driving posture.

  The automobile steering apparatus is configured as shown in FIG. 14, and transmits the rotation of the steering wheel 1 to the input shaft 3 of the steering gear unit 2, and a pair of left and right tie rods 4 in accordance with the rotation of the input shaft 3. 4 is pushed and pulled to give a steering angle to the front wheels. The steering wheel 1 is supported and fixed to the rear end portion of the steering shaft 5. The steering shaft 5 is rotatable inside the steering column 6 with the cylindrical steering column 6 inserted in the axial direction. I support it. Further, 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. Connected to. In the present specification and claims as a whole, the front-rear direction, left-right direction (width direction), and up-down direction refer to the front-rear direction, left-right direction (width direction), and up-down direction of the vehicle unless otherwise specified. .

  A tilt mechanism for adjusting the vertical position of the steering wheel 1 according to the driver's physique and driving posture in the steering device as described above has been widely known. In order to constitute a tilt mechanism, the front end portion of the steering column 6 is supported with respect to the vehicle body 10 so as to be able to swing and swing around a pivot 11 installed in the left-right direction. A displacement bracket 12 fixed to a portion near the rear end of the steering column 6 is supported so as to be able to be displaced with respect to the support bracket 13 supported on the vehicle body 10. In the case of the conventional structure shown in FIG. 14, a telescopic mechanism for adjusting the front-rear position of the steering wheel 1 is also incorporated. In order to constitute a telescopic mechanism, the steering column 6 has a structure in which an outer column 14 and an inner column 15 are telescopically combined, and the steering shaft 5 includes an outer shaft 16 and an inner shaft 17. The structure is such that the torque can be transmitted and can be expanded and contracted by spline engagement or the like. Note that the illustrated example also incorporates an electric power steering apparatus that reduces the force required to operate the steering wheel 1 using the electric motor 18 as an auxiliary power source.

  When the tilt mechanism or telescopic mechanism is a manual structure excluding an electric type, the position of the steering wheel 1 can be adjusted or fixed at the adjusted position based on the operation of the adjustment lever. I can do it. As for the structure of such a manual tilt mechanism and telescopic mechanism, various structures have been widely known and practiced. For example, in the case of the structure shown in FIG. 14, the longitudinal bracket 19 extending in the axial direction of the outer column 14 that is the front-rear position adjustment direction is formed in the displacement bracket 12 fixed to the outer column 14. doing. The support bracket 13 includes a pair of support plate portions 20 that sandwich the displacement bracket 12 from the left and right sides. The support bracket portions 13 extend in the vertical direction at portions where the pair of support plate portions 20 are aligned with each other. A pair of vertical slots 21 are formed. The pair of up-and-down long holes 21 are generally in the shape of a partial arc centered on the pivot 11. An adjustment rod 22 is inserted through the pair of up-and-down direction long holes 21 and the front-rear direction long hole 19. The adjustment rod 22 is provided with a pair of pressing portions in a state where the pair of support plate portions 20 are sandwiched from both sides in the left-right direction. The interval between the pressing parts can be enlarged or reduced.

  When adjusting the vertical position or the front-rear position of the steering wheel 1, the distance between the pair of pressing portions is increased by swinging the adjustment lever in a predetermined direction (generally downward). As a result, the frictional force acting between the inner side surfaces of the pair of support plate portions 20 and the outer side surfaces of the displacement bracket 12 is reduced. In this state, the position of the steering wheel 1 is adjusted within a range in which the adjustment rod 22 can be displaced within the pair of vertical slots 21 and the longitudinal slot 19. After the adjustment, the distance between the pair of pressing portions is reduced by swinging the adjustment lever in a direction opposite to the predetermined direction (generally upward). Accordingly, the frictional force is increased and the steering wheel 1 is held at the adjusted position.

  Further, the above-described steering device is provided with the steering wheel in order to reduce the impact load applied to the driver when a secondary collision occurs in which a driver's body hits the steering wheel 1 in the event of a collision. 1 has a function to allow the forward displacement. For this purpose, specifically, a structure is employed in which the support bracket 13 is supported to the vehicle body 10 so as to be able to be detached forward by an impact during a secondary collision. By the way, in the case of a steering device equipped with a tilt mechanism, if the force for holding the steering wheel 1 in the adjusted position, that is, the holding force of the steering column 6 (outer column 14) with respect to the support bracket 13, is weak. There is a possibility that it is difficult to design an impact absorbing mechanism based on the separation of the support bracket 13 from the vehicle body 10. That is, when a secondary collision occurs when the vertical position of the steering wheel 1 is an intermediate or lower end position, the adjustment rod 22 moves along the pair of vertical elongated holes 21 when the holding force is weak. By displacing upward, the steering wheel 1 may move vigorously to the upper end position of the adjustable range. As a result, the way in which an impact is applied to the support bracket 13 changes, which may make it difficult to design the impact absorbing mechanism.

  On the other hand, in order to increase the holding force of the steering column 6 with respect to the support bracket 13 without increasing the operation amount and operating force of the adjusting lever, the sliding friction parts (which contact each other) are secured. It is preferable to increase the number of portions where the contacting surfaces are frictionally engaged. In view of such circumstances, Patent Document 1 discloses a structure in which the number of the sliding friction portions is increased by overlapping a friction plate supported by a steering column and a friction plate supported by a support bracket in the left-right direction. Is described. However, in the case of such a structure described in Patent Document 1, the number of friction plates required to increase the number of the sliding friction portions increases, and the left and right generated with the increase of the sliding friction portions. The direction dimension, the number of parts, and the increase in weight are each increased.

JP 10-35511 A

  In view of the circumstances as described above, the present invention can increase the force for holding the steering wheel in the adjusted position with a small number of friction plates, and can smoothly adjust the position of the steering wheel. The present invention was invented to realize the structure.

A steering wheel position adjusting device according to the present invention includes a steering column, a displacement bracket, a column side through hole, a support bracket, a pair of vertically elongated holes, an adjusting rod, a pair of pressing portions, and expansion / contraction. Device.
The steering column has a cylindrical shape, and supports a steering shaft having a steering wheel supported and fixed at a rear end portion thereof in a rotatable manner.
The displacement bracket is fixed to a part of the steering column.
The column side through hole is provided in the displacement bracket so as to penetrate the displacement bracket in the width direction.
The support bracket includes a pair of support plate portions that sandwich the displacement bracket from both sides in the width direction, and is supported by the vehicle body.
The pair of up-and-down direction long holes are provided in a state of extending in the up-down direction in portions where the pair of support plate portions are aligned with each other.
The adjusting rod is provided in a state of being inserted in the width direction through the column side through hole and the pair of vertically elongated holes.
The pair of pressing portions are provided at portions projecting from the outer surfaces of the pair of support plate portions at both ends of the adjustment rod.
The expansion / contraction device expands / contracts an interval between the pair of pressing portions.

In particular, in the steering wheel position adjusting device of the present invention, the side surface (inner side surface or outer side surface) of at least one of the pair of support plate portions and the side surface of the one support plate portion. An oscillating friction plate is sandwiched between the opposing side surface of the opposing member (the outer surface of the displacement bracket or the inner surface of one of the pair of pressing portions).
Then, when the adjustment rod is displaced along the adjustment slot, the base end of the oscillating friction plate is a member that is displaced relative to the adjustment rod (when the vertical position of the steering wheel is adjustable). Is one of the support plate portions, and when the front-rear position can be adjusted, the displacement bracket is pivotably supported, and the adjustment rod is attached to the front half portion of the swing friction plate. Only the displacement along this guide long hole is engaged with the provided guide long hole.
Further, a leaf spring capable of elastically expanding and contracting the dimension in the width direction is sandwiched between the side surface of the oscillating friction plate and the side surface of the one support plate portion facing each other. Then, in a state where the substrate portion of the leaf spring is prevented from being displaced by the oscillation of the oscillation friction plate with respect to one of the side surface of the oscillation friction plate and the side surface of the one support plate portion. I support it.

  When the present invention as described above is implemented, preferably, as in the invention described in claim 2, the leaf spring is pivoted to pivotally support the base end portion of the rocking friction plate. Provide around the support shaft.

When the present invention as described above is implemented, specifically, for example, as in the invention described in claim 3, the shape of the plate portion of the leaf spring viewed from the width direction is made non-circular. An engaging recess that is recessed in the width direction is provided on the one side surface. Then, by engaging the base plate portion of the leaf spring with the engagement recess, the base portion of the leaf spring is supported with respect to the one side surface in a state in which displacement caused by the swing of the swing friction plate is prevented. To do.
Alternatively, the leaf spring is bonded to the one side surface, or the side edge portion of the leaf spring substrate portion is engaged with a claw portion provided on the one side surface, thereby the leaf spring. It is also possible to support the substrate portion with respect to the one side surface in a state in which displacement due to the swing of the swing friction plate is prevented.

According to the steering wheel position adjusting device of the present invention configured as described above, even with a small number of friction plates, the force for holding the steering wheel in the adjusted position can be increased (the sliding friction portion can be increased). Moreover, the position of the steering wheel can be adjusted smoothly.
That is, in the case of the present invention, in a state where the distance between the pair of pressing portions is reduced so as to hold the steering wheel in the adjusted position, the oscillating friction plate has at least one side surface (inner surface) of the supporting plate portion. Or the outer side surface) and the side surface of the mating member (the outer side surface of the displacement bracket or the inner side surface of one of the pair of pressing portions) facing the side surface of the one supporting plate portion. It will be in the state of being pinched strongly. If an attempt is made to move the position of the steering wheel from this state, both side surfaces of the oscillating friction plate strongly rub against the side surface of the one support plate portion and the side surface of the mating member. In short, when trying to move the position of the steering wheel from the state where the steering wheel is held at a desired position, it is necessary to swing the swinging friction plate while sliding both side surfaces of the swinging friction plate. . For this reason, the force which hold | maintains the said steering wheel in the position after adjustment can be strengthened. Further, in the case of the present invention, a structure capable of increasing the force for holding the steering wheel in the adjusted position can be obtained without overlapping a plurality of friction plates as in the structure described in Patent Document 1 described above. This can be realized with a small swing friction plate. Accordingly, it is possible to reduce the size and weight of the steering wheel position adjusting device while suppressing an increase in the lateral dimension, the number of parts, and the weight of the steering wheel position adjusting device.

  In the case of the present invention, a leaf spring capable of elastically expanding / contracting the dimension in the width direction is sandwiched between the side surface of the oscillating friction plate and the side surface of the one support plate portion facing each other. For this reason, the side surface of the rocking friction plate and the side surface of the one support plate portion are reliably separated in a state where the distance between the pair of pressing portions is increased and the vertical position of the steering wheel is adjustable. I can do things. Therefore, when adjusting the vertical position of the steering wheel, a frictional force does not act between the side surface of the oscillating friction plate and the side surface of the one support plate portion. Furthermore, in the case of the present invention, the substrate portion of the leaf spring is displaced with respect to one side surface of the side surface of the rocking friction plate and the side surface of the one support plate portion as the rocking friction plate swings. We support in state that we blocked. For this reason, when adjusting the vertical position of the steering wheel, the leaf spring does not slide with respect to the one side surface, and frictional force acts between the leaf spring and the one side surface. Absent. As a result, the vertical position of the steering wheel can be adjusted smoothly.

The side view which shows the 1st example of embodiment of this invention. The figure (A) which shows the expanded aa cross section of FIG. 1 in a clamped state, and the figure (B) shown in an unclamped state. The enlarged bb sectional view (A) of (A) of Drawing 2 and the enlarged cc sectional view (B) of (B). The perspective view (A) shown in the state before supporting a rocking | fluctuation friction board to one support plate part, and the side view (B) which takes out and shows a rocking | fluctuation friction board. The positional relationship of the oscillating friction plate in the state (A) in which the steering wheel is moved to the upper end position of the adjustable range, the state (B) in which the steering wheel is moved to the intermediate position, and the state (C) in which the steering wheel is moved to the lower end position. The side view equivalent to the center part of FIG. 1 which takes out and shows a rocking | fluctuation friction board and a support bracket. In order to explain the effect of the present invention, the engagement state of the adjusting rod, the guide elongated hole and the vertically elongated hole is shown by comparison between the conventional structure (A) and the present invention (B). Pattern diagram. The figure which shows a 2nd example of embodiment of this invention by taking out a support bracket and a rocking | fluctuation friction board, a clamped state (A), and an unclamped state (B). Similarly perspective view. Similarly, the same figure as (A) of FIG. Similarly, the same figure as FIG. The side view which shows the 3rd example of embodiment of this invention. FIG. 12 is an enlarged dd sectional view of FIG. 11. The telescopic rocking friction plate is moved in a state (A) where the steering wheel is moved to the front end position within the adjustable range, a state (B) where the steering wheel is moved to the intermediate position, and a state (C) where the steering wheel is moved to the rear end position. FIG. 12 is a side view corresponding to the central part of FIG. 11, showing the positional relationship by taking out the steering column and the telescopic rocking friction plate. The partial cutting schematic side view which shows an example of the position adjustment apparatus of the steering wheel conventionally known.

[First example of embodiment]
1 to 5 show a first example of an embodiment of the present invention. The steering wheel position adjusting device of this example includes a steering column 6a, a displacement bracket 12a, a longitudinal long hole 19a that is a column side through hole, a steering shaft 5a, a support bracket 13a, and a pair of vehicle body side through holes. A pair of vertically elongated holes 21a and 21a, which are holes, an adjustment rod 22a, a pair of pressing portions 24a and 24b, an adjustment lever 23, and a swing friction plate 25 are provided.
Among these, the steering column 6a is a telescopic steering formed by fitting the rear end portion of the inner column 15a disposed on the front side and the front end portion of the outer column 14a disposed on the rear side so as to allow relative displacement in the axial direction. The column is entirely cylindrical. The displacement bracket 12a is integrally formed with the outer column 14a on the lower surface of the front end portion of the outer column 14a by die-casting a light alloy such as an aluminum alloy. The displacement bracket 12a is capable of elastically expanding and contracting the entire width by a slit 26 formed at the center in the width direction. However, the displacement bracket 12a may be provided on the upper surface of the front end portion of the outer column 14a. The front / rear direction long hole 19a is a part of the displacement bracket 12a, and is provided at a position aligned with the slit 26 so as to penetrate the displacement bracket 12a in the width direction. When the present invention is implemented with a structure that does not include a telescopic mechanism (including only a tilt mechanism), a state in which a circular hole is penetrated in the width direction through the displacement bracket 12a in place of the longitudinal slot 19 is provided. Provided.

  Further, the steering shaft 5a can transmit torque by spline engagement between the front end portion of the outer shaft 16a disposed on the rear side and the rear end portion of the inner shaft 17a disposed on the front side, and can expand and contract. Combining possible combinations. Such a steering shaft 5a has an intermediate portion rear end portion of the outer shaft 16a at the rear end portion of the outer column 14a, and an intermediate portion front end portion of the inner shaft 17a at the front end portion of the inner column 15a. Each of them is rotatably supported by a rolling bearing capable of supporting a radial load and a thrust load like a single row deep groove type ball bearing. Therefore, the steering shaft 5a expands and contracts with the expansion and contraction of the steering column 6a. A steering wheel 1 (see FIG. 14) is supported and fixed to a portion of the rear end portion of the outer shaft 16a that protrudes rearward from the rear end opening of the outer column 14a.

  The support bracket 13a is formed by bending a metal plate, such as a steel plate, that can ensure the required strength and rigidity. The support plate 13a is supported by the vehicle body, and the bottom surface of the attachment plate portion 27. And a pair of support plate portions 20a and 20b that are parallel to each other. The distance between the inner surfaces of the pair of support plate portions 20a and 20b substantially matches the width dimension of the displacement bracket 12a. The pair of vertically elongated holes 21a and 21a are formed in the matching portions of the pair of support plate portions 20a and 20b, and support the front end portion of the steering column 6a so as to be able to swing and displace. It is a partial arc shape centering on the pivot 11a. However, the pair of vertically elongated holes 21a, 21a can be linearly inclined in the upward direction as going backward. The support bracket 13a having such a configuration allows the vehicle body 10 (see FIG. 14) to drop forward due to an impact load applied during a secondary collision. However, the steering column 6a has sufficient rigidity in normal times. Is supported in a state that can be secured. That is, the locking notches 28, 28 are formed at two positions in the width direction of the mounting plate portion 27 so as to open at the rear edge of the mounting plate portion 27, and the pair of locking notches 28, 28 is locked to the locking capsules 29, 29 fixed to the vehicle body 10 (see FIG. 14) so as to be able to be detached forward when a strong impact directed forward is applied. The thickness of the metal plate constituting such a support bracket 13a is, for example, about 2.8 to 4.5 mm, preferably 3.2 to 4.0 mm.

  Further, the adjusting rod 22a is provided in a state of being inserted in the width direction through the longitudinal slot 19a and the pair of vertical slots 21a, 21a. Then, at the both ends of the adjusting rod 22a, the pair of pressing portions 24a and 24b are provided at the portions protruding from the outer surfaces of the pair of supporting plate portions 20a and 20b. The interval between the pair of pressing portions 24a and 24b can be enlarged or reduced. The structure of the expansion / contraction device for expanding / contracting the distance between the pair of pressing portions 24a, 24b by the adjusting lever 23 is not particularly limited. For example, it is possible to employ a cam device in which the axial dimension can be expanded or contracted by engagement between the cam surfaces of a pair of cam members, or a structure in which a nut is screwed into a male thread portion provided at the tip of the adjustment rod 22a. . Regardless of which structure is employed, the adjusting lever 23 is provided at one end of the adjusting rod 22a. Then, by swinging the adjustment lever 23, the distance between the pair of pressing portions 24a, 24b can be enlarged or reduced.

  The oscillating friction plate 25 is formed in a substantially sector shape by a metal plate such as a steel plate, a stainless steel plate or an aluminum alloy that can ensure the required strength and rigidity. The thickness of this metal plate is, for example, about 0.5 to 1.5 mm, preferably 0.8 to 1.2 mm. Such a oscillating friction plate 25 has a front half portion (wide portion) of the oscillating friction plate 25 as an outer surface of the one support plate portion 20a and one of the pair of pressing portions 24a, 24b ( In a state of being sandwiched between the inner surface of the pressing portion 24a (left side in FIG. 2), the one supporting plate portion 20a is supported so as to be swingable and displaceable along with the vertical position adjustment of the steering wheel 1. Yes. For this purpose, of the one support plate portion 20a, an extension line of the center line α {see FIG. 5A) of the vertically elongated hole 21a provided in the one support plate portion 20a (the pivot shaft 11a). Above the vertical slot 21a (including the vicinity thereof as long as the angle θ described below can be made substantially constant regardless of the vertical position of the adjusting rod 22a). By subjecting the portion to surface pressing, an engagement recess 34 that is recessed inward in the width direction and has a rectangular shape when viewed from the width direction is provided on the outer surface of the one support plate portion 20a. Then, by applying a burring process to the central portion of the engagement recess 34, the cylindrical portion 31 that is a swing support shaft protrudes outward in the width direction (toward the one pressing portion 24a). Is provided. A circular hole 30 provided in the base end portion (a portion corresponding to the main part of the fan) of the swing friction plate 25 is externally fitted to such a cylindrical portion 31 with a gap fit. In a state where the cylindrical portion 31 is inserted into the circular hole 30 of the swing friction plate 25, a portion of the cylindrical portion 31 that protrudes from the other side surface (the left side surface in FIG. 2) of the swing friction plate 25 is radially outside. By restraining plastic deformation (caulking and expanding), a restraining portion (caulking portion) 33 is formed in the portion. The restraining portion 33 prevents the oscillating friction plate 25 from falling off the cylindrical portion 31 (the circular hole 30 coming out of the cylindrical portion 31). However, the holding portion 33 is in a state in which the gap between the pair of pressing portions 24a and 24b is widened so that the position of the steering wheel 1 can be adjusted without holding down the rocking friction plate 25. Thus, the swing friction plate 25 can be smoothly swung. The adjusting rod 22a is inserted through a guide long hole 32 provided in the front half of the swing friction plate 25. The guide slot 32 extends from a rear end (one end in the clockwise direction in FIGS. 1 and 4) that is one end in the swing direction to a front end (the front in the clockwise direction in FIG. 1) that is the other end in the swing direction. A small curve until the distance between the circular hole 30, that is, the cylindrical portion 31, which is the swing center of the swing friction plate 25, increases gradually. Forming. More specifically, the guide long hole 32 is in a state {the state shown in FIG. 5B) where the adjustment rod 22a is located in the center of the vertical long hole 21a, and is more than the center line α. It has a partial arc shape centered on a point located forward and above the cylindrical portion 31. The distance L between the adjustment rod 22a and the cylindrical portion 31 is set as a radius around the tangent of the portion of the partial arc where the adjustment rod 22a is engaged and the central axis of the cylindrical portion 31. The angle θ formed by the tangent line of the virtual arc (the swinging direction of the swinging friction plate 25) is set to be substantially constant regardless of the vertical position of the adjusting rod 22a. Such an angle θ is preferably 10 degrees to 35 degrees, and more preferably 20 degrees to 30 degrees. When the adjusting rod 22a is positioned at the upper end of the movable range within the up and down direction long hole 21a, the adjusting rod 22a and the rear end of the guide long hole 32 are engaged. When the adjusting rod 22a is positioned at the lower end of the movable range in the vertical direction long hole 21a, the adjusting rod 22a and the front end of the guide long hole 32 are engaged with each other. The circular hole 30 of the oscillating friction plate 25 is externally supported by the cylindrical part 31 so as to be able to oscillate around the cylindrical part 31.

  Further, in the case of this example, a width between the outer surface of the one support plate portion 20a and one side surface (right side surface in FIG. 2) of the one support plate portion 20a around the cylindrical portion 31. A plate spring 35 capable of expanding and contracting in the direction is sandwiched. The leaf spring 35 includes a substrate portion 36 and a pair of elastic deformation portions 37 and 37. Of these, the substrate portion 36 is T-shaped when viewed from the width direction, and has a circular hole 42 through which the cylindrical portion 31 is inserted at the center. The pair of elastic deformation portions 37, 37 are provided in a state of being bent outward in the width direction from the rear end edges of both end portions in the vertical direction of the substrate portion 36 and extending rearward. Such a pair of elastically deforming portions 37, 37 is substantially V-shaped having bent portions near the tip, and the outer surfaces of both bent portions are elastic pressing portions 38, 38. Such a leaf spring 35 engages the base plate portion 36 with the engaging recess 34 and makes the pair of elastic pressing portions 38, 38 abut against one side surface of the oscillating friction plate 25. , And is sandwiched between the outer side surface of the one support plate portion 20a and one side surface of the oscillating friction plate 25.

  In the case of this example, when the vertical position or the front / rear position of the steering wheel 1 is adjusted, the adjustment lever 23 is swung in a predetermined direction (usually downward), whereby the pair of pressing portions 24a, 24b. Increase the distance between each other. As a result, based on the presence of the slit 26 of the displacement bracket 12a, the inner diameter of the front end portion of the outer column 14a expands elastically, and the inner peripheral surface of the front end portion of the outer column 14a and the outer periphery of the rear end portion of the inner column 15a. The surface pressure of the fitting portion with the surface is reduced or lost. At the same time, the surface pressure of the contact portion between the both side surfaces of the oscillating friction plate 25, the outer surface of the one support plate portion 20a and the inner surface of the one pressing portion 24a, and the pair of support plate portions Contact pressure between the inner side surfaces of 20a and 20b and both side surfaces of the displacement bracket 12a, and contact pressure between the outer surface of the other support plate portion 20b and the inner surface of the other pressing portion 24b. However, they are reduced or lost. Particularly in the case of this example, the leaf spring 35 is sandwiched between the outer side surface of the one support plate portion 20 a and one side surface of the swing friction plate 25. For this reason, when the distance between the pair of pressing portions 24a, 24b is increased, the dimension in the width direction of the leaf spring 35 is elastically expanded (based on the elasticity of the pair of elastic deformation portions 37, 37, A pair of elastic pressing portions 38 and 38 elastically press one side surface of the swing friction plate 25 outward in the width direction), the outer surface of the one support plate portion 20a, and the swing friction plate. Thus, the surface pressure of the contact portion between the outer surface of one of the support plate portions 20a and the one side surface of the oscillating friction plate 25 can be completely lost. In this way, the adjustment rod 22a can be displaced within the front / rear direction long hole 19a and the pair of vertical direction long holes 21a, 21a in a state where the distance between the pair of pressing portions 24a, 24b is widened. Then, the position of the steering wheel 1 is adjusted.

  In this example as described above, the movement of the oscillating friction plate 25 when the steering wheel 1 (steering column 6a) is displaced in the vertical direction to adjust the vertical position of the steering wheel 1 is performed. And will be described next. FIG. 5A shows a state in which the steering wheel 1 is moved to an adjustable upper end position. In this state, the adjustment rod 22a is engaged with the upper end portion of the up-down direction long hole 21a and the rear end portion of the guide long hole 32. When the steering wheel 1 is displaced downward from this state and the adjusting rod 22a is lowered, the distance L between the adjusting rod 22a and the central axis of the cylindrical portion 31 becomes longer. ) → (B) → (C), the swinging friction plate 25 swings around the cylindrical portion 31 in the counterclockwise direction of FIG. In the state where the steering wheel 1 is moved to the adjustable lower end position, as shown in FIG. 5C, the adjustment rod 22a is connected to the lower end portion of the vertical elongated hole 21a and the guide length. The front end of the hole 32 is engaged. On the other hand, when the steering wheel 1 is displaced upward from the lower end position to the upper end position, conversely to the downward displacement described above, (C) → (B) → (A) in FIG. The oscillating friction plate 25 oscillates in this order.

  According to the steering wheel position adjusting device of this example configured as described above, the force for holding the steering wheel 1 (see FIG. 14) in the adjusted position can be increased, and the vertical position of the steering wheel 1 can be increased. Can be adjusted smoothly. That is, in the case of this example, the swinging friction plate 25 is configured to support the one support member in a state where the distance between the pair of pressing portions 24a and 24b is shortened so as to hold the steering wheel 1 in the adjusted position. It will be in the state pinched strongly between the outer surface of the board part 20a, and the inner surface of said one press part 24a. When the vertical position of the steering wheel 1 is moved from this state, both side surfaces of the oscillating friction plate 25 strongly rub against the outer surface of the one support plate portion 20a and the inner surface of the one pressing portion 24a. It will be a thing. In short, when trying to move the steering wheel 1 from a state where the steering wheel 1 is held at a desired position, both sides of the oscillating friction plate 25 are connected to the outer surface of the one support plate portion 20a and the one of the ones. The rocking friction plate 25 needs to be swung while sliding with respect to the inner surface of the pressing portion 24a. For this reason, the force which hold | maintains the said steering wheel 1 in the position after adjustment can be strengthened. As a result, at the time of a secondary collision, the adjustment rod 22a is inserted into the vertical elongated holes 21a and 21a provided in the pair of support plate portions 20a and 20b based on a forward impact load applied to the steering wheel 1. By displacing along the upper side, it is possible to prevent the steering wheel 1 from rising, and to enhance the protection of the driver's body. In the state where the distance between the pair of pressing portions 24a and 24b is reduced, the leaf spring 35 is disposed between the outer side surface of the one support plate portion 20a and one side surface of the swing friction plate 25. It is crushed elastically and fits inside the engaging recess 34.

  In the case of this example, a structure capable of increasing the force for holding the steering wheel 1 in the adjusted position is formed by overlapping a plurality of friction plates like the structure described in Patent Document 1 described above. However, this can be realized with only one rocking friction plate 25. Accordingly, it is possible to suppress the lateral dimension, the number of parts, and the weight of the steering wheel position adjusting device from increasing as in the structure described in Patent Document 1, and the steering wheel position adjusting device can be reduced in size. Weight reduction can be achieved.

  Furthermore, in the case of this example, by externally fitting the circular hole 30 provided at the base end portion of the rocking friction plate 25 to the cylindrical portion 31 provided integrally with the one support plate portion 20a, The rocking friction plate 25 is supported so as to be rockable with respect to the one support plate portion 20a. Therefore, it is possible to prevent the number of parts from increasing with the provision of the oscillating friction plate 25. Specifically, for example, a columnar member provided separately from the one support plate portion is supported and fixed on the side surface of one support plate portion by welding or the like, so that the base end portion of the rocking friction plate is attached. There is no need to provide a swinging support shaft for swingably supporting the provided circular hole. For this reason, it is possible to suppress an increase in manufacturing cost due to the provision of the oscillating friction plate 25. In particular, as in this example, if the cylindrical portion 31 is formed by burring the metal plate constituting the one support plate portion 20a, the steering wheel position adjusting device is industrially efficient. Can be produced.

  In the case of assembling the steering wheel position adjusting device of this example, it is preferable that the plate spring 35 and the circular hole 30 provided in the base end portion of the swing friction plate 25 are connected to the one support plate portion 20a. The cylindrical part 31 formed on the cylindrical part 31 is swingably fitted, and further, the holding part 33 is formed to prevent the swinging friction plate 25 from falling off the cylindrical part 31. The support plate portion 20 a is supported and fixed to the lower surface of the mounting plate portion 27. Thereby, the assembly work of the steering wheel position adjusting device can be facilitated.

  The structure for pivotally supporting the base end portion of the swing friction plate 25 so as to be swingable with respect to the one support plate portion 21a is not limited to the above-described structure. At the end, a cylindrical part formed by burring the metal plate constituting the rocking friction plate is inserted into a circular hole formed in one support plate part, and one of the cylindrical parts is inserted. A base end portion of the oscillating friction plate can be pivotably supported by plastically deforming a portion protruding from the side surface of the support plate portion radially outward to form a restraining portion. Alternatively, the base end portion of the cylindrical or columnar swing support shaft is supported and fixed to one support plate portion or the swing friction plate by welding or press-fitting into a through hole formed in the one support plate portion. A circular hole formed in the dynamic friction plate or one of the support plate portions may be fitted on the tip end portion of the swing support shaft so as to be swingable.

  Further, in the case of this example, the circular hole 30 provided at the base end portion of the rocking friction plate 25 is arranged on the upper and lower sides formed on the one support plate portion 20a out of the outer surface of the one support plate portion 20a. On the extended line of the center line α of the direction long hole 21a, it is fitted on the cylindrical portion 31 provided above the vertical direction long hole 21a so as to be swingable. For this reason, when adjusting the vertical position of the steering wheel 1, the adjustment rod 22 a is engaged with the vertical slot 21 a and the guide slot 32 provided in the front half of the rocking friction plate 25. The frictional force acting on the part can be reduced. The reason for this will be described with reference to FIG.

In FIG. 6A, a cylindrical portion 31z for swingably supporting the circular hole 30 provided at the base end portion of the swing friction plate 25z is provided at the rear (or front) of the vertical slot 21a. The structure is shown. Also in the case of the structure of the comparative example shown in FIG. 6A, the longitudinal direction of the guide long hole 32z provided in the front half of the rocking friction plate 25z in the engaging portion with the adjusting rod 22a. (A tangential direction of the guide elongated hole 32z) and a tangential line of a virtual arc whose radius is _a distance La between the adjustment rod 22a and the cylindrical portion 31z (the swing direction of the swing friction plate 25z). angle theta _a, regardless of the vertical position of the adjusting rod 22a, substantially constant (preferably 10 degrees to 35 degrees, more preferably 20 degrees to 30 degrees) in the manner becomes. In the case of the structure of such a comparative example, the length direction of the up / down direction long hole 21a (tangential direction of the up / down direction long hole 21a) at the engaging portion with the adjusting rod 22a, the adjusting rod 22a, the angle phi _a formed between the longitudinal direction of at the guide slot 32z with the engaging portion of the (tangential direction of the elongated guide holes 32z), regardless of the vertical position of the steering wheel 1, a relatively small (20 Degrees to about 30 degrees). Therefore, when the vertical position of the steering wheel 1 is adjusted, the engaging portion (sliding contact portion) between the outer peripheral surface of the adjusting rod 22a and the inner peripheral edge of the vertical elongated hole 21a and the inner peripheral edge of the guide long hole 32z. ) Has a wedge effect, and the frictional force acting on the engaging portion increases. In other words, when the force applied to the adjusting rod 22a is F based on the displacement of the steering wheel 1 upward, the engagement between the outer peripheral surface of the adjusting rod 22a and the inner peripheral edge of the vertically elongated hole 21a. The pressing force (normal force) Fc _1a applied to the portion and the pressing force Fc _2a applied to the engaging portion between the outer peripheral surface of the adjusting rod 22a and the inner peripheral edge of the guide elongated hole 32z are equal to each other. ) Expression.

従って、前記比較例の構造に於いて、前記調節ロッド２２ａが前記上下方向長孔２１ａ内を上方に変位する事に対する摩擦抵抗（前記摩擦力Ｆｓ_１ａと、前記摩擦力Ｆｓ_２ａのうち上下方向長孔２１ａの長さ方向成分との和）Ｆｓ_ａは、次の（３）式により算出できる。

When the friction coefficient of the engaging portion between the outer peripheral surface of the adjusting rod 22a and the inner peripheral edge of the vertical elongated hole 21a and the inner peripheral edge of the guide long hole 32z is μ, the outer peripheral surface of the adjusting rod 22a. And a friction force Fs _1a acting on an engagement portion between the upper and lower elongated holes 21a and an engagement portion between the outer peripheral surface of the adjusting rod 22a and the inner periphery of the guide elongated hole 32z. Fs _2a is equal to each other and is expressed by the following equation (2).

Therefore, in the structure of the comparative example, the frictional resistance (the frictional force Fs _1a for that the adjusting rod 22a is displaced to the vertical long hole 21a upward in the vertical direction length of the frictional force Fs _2a The sum of the length direction component of the hole 21a) Fs _a can be calculated by the following equation (3).

On the other hand, in the case of the steering wheel position adjusting device of the present example, as shown in FIG. 6B, the cylindrical portion 31 is placed on the extension line of the center line α of the vertical direction long hole 21a. It is provided above the vertical hole 21a. For this reason, the length direction of the up-and-down direction long hole 21a in the engaging portion with the adjusting rod 22a (the tangential direction of the up-and-down direction long hole 21a) and the engaging portion with the adjusting rod 22a. The angle φ (= 90 ° −θ) formed with the length direction of the guide slot 32 (the tangential direction of the guide slot 32) is similar to the structure of the comparative example. Compared with the case where it is provided behind (or forward) 21a, it can be increased. For this reason, when the vertical position of the steering wheel 1 is adjusted, there is a wedge effect on the engaging portion between the outer peripheral surface of the adjusting rod 22a and the inner peripheral edge of the vertical elongated hole 21a and the inner peripheral edge of the guide long hole 32. It can be suppressed from occurring. As a result, when the force applied to the adjusting rod 22a is F based on the displacement of the steering wheel 1 upward, the relationship between the outer peripheral surface of the adjusting rod 22a and the inner peripheral edge of the vertical elongated hole 21a. The pressing force (normal force) Fc ₁ applied to the joint portion and the pressing force Fc ₂ applied to the engaging portion with the inner peripheral edge of the guide elongated hole 32 are respectively expressed by the following equations (4) to (5). become.

従って、本例のステアリングホイールの位置調節装置に於いて、前記調節ロッド２２ａが前記上下方向長孔２１ａ内を上方に変位する事に対する摩擦抵抗Ｆｓは、次の（８）式により算出できる。

Further, if the friction coefficient of the engaging portion between the outer peripheral surface of the adjusting rod 22a and the inner peripheral edge of the vertical elongated hole 21a and the inner peripheral edge of the guide long hole 32 is μ, the outer peripheral surface of the adjusting rod 22a Friction force Fs ₁ acting on the engaging portion with the inner peripheral edge of the vertical elongated hole 21a and friction force acting on the engaging portion between the outer peripheral surface of the adjusting rod 22a and the inner peripheral edge of the guide long hole 32 fs ₂ are each represented by the following (6) to (7).

Therefore, in the steering wheel position adjusting device of this example, the frictional resistance Fs against the displacement of the adjusting rod 22a in the up-and-down direction long hole 21a can be calculated by the following equation (8).

Here, in the case of the structure of the present example, the angle φ formed by the length direction of the vertical slot 21a and the length direction of the guide slot 32 is 55 degrees to 80 degrees. , the angle phi _a formed between the longitudinal direction of the vertical long hole 21a in the longitudinal direction and the guide long hole 32z is 20 to 30 degrees. Accordingly, as is clear from the equations (3) and (8), the frictional resistance Fs of the structure of this example against the displacement of the adjusting rod 22a upward in the vertical elongated hole 21a is also shown in FIG. The frictional resistance Fs _a of the structure of the comparative example shown in (A) of (A) is suppressed to be smaller (Fs <Fs _a ). That is, in this example, when the friction coefficient μ is 0.15 and the angle φ is 65 degrees (θ is 25 degrees), the frictional resistance Fs is 0. It becomes about 1F. In contrast, in the case of the comparative example, when the angle phi _a and 25 degrees, the frictional resistance Fs _a from the expression (3), is about 0.7F.
In short, according to the steering wheel position adjusting device of this example, when the vertical position of the steering wheel 1 is adjusted, the frictional resistance Fs against the displacement of the adjusting rod 22a in the vertical direction is the case of the structure of the comparative example. Therefore, the adjustment operation of the vertical position of the steering wheel 1 can be performed smoothly. However, the cylindrical portion 31 is formed on the side surface of the one support plate portion 20a on the extension line of the center line α of the vertical direction long hole 21a provided on the one support plate portion 20a. It can also be provided below 21a.

  In the case of this example, the leaf spring 35 is sandwiched between the outer side surface (the seat surface portion 36) of the one support plate portion 20 a and one side surface of the oscillating friction plate 25. For this reason, in a state where the distance between the pair of pressing portions 24a and 24b is increased and the vertical position of the steering wheel 1 is adjustable, the one side surface of the oscillating friction plate 25 and the one supporting plate portion 21a The outer surface can be reliably separated. Therefore, when adjusting the vertical position of the steering wheel 1, no frictional force acts between one side surface of the oscillating friction plate 25 and the outer side surface of the one support plate portion 21a. As a result, the vertical position of the steering wheel 1 can be adjusted smoothly. Particularly in the case of this example, by engaging the base plate portion 36 of the leaf spring 35 with an engagement recess 34 provided in a state of being recessed inward in the width direction on the outer surface of the one support plate portion 21a, The leaf spring 35 is supported with respect to the one support plate portion 21a in a state in which rotation about the cylindrical portion 31 is prevented regardless of the oscillation of the oscillation friction plate 25. For this reason, when the vertical position of the steering wheel 1 is adjusted, the leaf spring 35 does not slide with respect to the outer surface of the one support plate portion 21a. A frictional force does not act between the outer surface of 21a. Also from this aspect, the vertical position of the steering wheel 1 can be adjusted smoothly. Further, in a state where the distance between the pair of pressing portions 24 a and 24 b is reduced, the leaf spring 35 is disposed between the outer side surface of the one support plate portion 20 a and one side surface of the swing friction plate 25. It is crushed elastically and is in a state of being accommodated inside the engaging recess 34. Therefore, in a state where the distance between the pair of pressing portions 24a and 24b is reduced, both side surfaces of the oscillating friction plate 25, the outer surface of the one supporting plate portion 20a, and the inner side of the one pressing portion 24a The side surfaces are brought into contact with each other (without elastically deforming the rocking friction plate 25 in the width direction).

  The engaging recess 34 may be provided by performing a cutting process such as a counterbore process on the outer surface of the one support plate part 20a. Alternatively, the engagement recess 34 for engaging the base plate portion 36 of the leaf spring 35 can be provided on one side surface of the oscillating friction plate 25 while being recessed outward in the width direction, or can be omitted. it can. When the engagement recess is omitted, the substrate portion of the leaf spring is adhered to the outer side surface of the support plate portion or one side surface of the swing friction plate, or the side edge portion of the substrate portion of the leaf spring is attached to this side portion. By engaging with an outer surface of one support plate or a claw provided on one side surface of this oscillating friction plate, the outer surface of this one support plate portion or one side surface of this oscillating friction plate It supports in the state which prevented the displacement accompanying the rocking | fluctuation of a rocking | fluctuation friction board. Further, when the engagement concave portion is omitted, the front half of the swinging friction plate is elastically deformed inward in the width direction with respect to the base half in a state where the distance between the pair of pressing portions is reduced. (Offset) state.

  Further, in the case of this example, the plate spring 35 as described above is provided around the cylindrical portion 31. Accordingly, when the vertical position of the steering wheel 1 is adjusted by increasing the distance between the pair of pressing portions 24a, 24b, one side surface of the pair of elastic pressing portions 38, 38 and the rocking friction plate 25 is provided. The frictional force (friction moment) acting between the two can be kept small. Further, in the case of this example, the outer surface of the bent portion provided at the tip end portion of the pair of elastic deformation portions 37, 37 is elastic with one side surface of the oscillating friction plate 25 facing outward in the width direction. It is set as a pair of elastic press parts 38 and 38 pressed against. Therefore, the contact area (sliding contact area) between the pair of elastic pressing portions 38 and 38 and one side surface of the oscillating friction plate 25 is kept small (the pair of elastic pressing portions 38 and 38 and the rocking contact surface). The contact state of the contact portion with one side surface of the dynamic friction plate 25 can be line-contacted). From these surfaces, the vertical position of the steering wheel 1 can be adjusted smoothly. However, a leaf spring for reliably separating the side surface of the support plate portion and the side surface of the swing friction plate in a state where the distance between the pair of pressing portions is widened is provided between the support plate portion and the swing friction plate. It can also be provided in other parts such as around the adjusting rod.

  In order to suppress the frictional force acting between the pair of elastic pressing portions 38 and 38 and one side surface of the oscillating friction plate 25 when adjusting the vertical position of the steering wheel 1, For example, a low friction layer such as molybdenum or polytetrafluoroethylene (PTFE) may be provided on the surface of the leaf spring 35, or the leaf spring 35 may be made of a synthetic resin having self-lubricating properties. Alternatively, thrust bearings may be provided on both side portions of the leaf spring 35.

  In this example, the oscillating friction plate 25 has a substantially fan shape, but may have an arbitrary shape such as a rectangle or a circle. However, it is preferable to have a substantially sector shape from the surface that suppresses the protruding amount from the front and rear side edges of the one support plate portion 20a while ensuring the contact area with the outer surface of the one support plate portion 20a. . That is, the portion surrounding the guide slot 32 provided in the front half portion of the swing friction plate 25 (the portion around the guide slot 32 having a width sufficient to ensure the strength of the guide slot 32). When both ends in the moving direction and a portion surrounding the circular hole 30 provided at the base end portion of the swing friction plate 25 are connected by a substantially straight line (including a straight line), the swing friction plate 25 as a whole has a substantially sector shape. It becomes.

[Second Example of Embodiment]
7 to 10 show a second example of the embodiment of the present invention. In the steering wheel position adjusting device of this example, the pair of oscillating friction plates 25a and 25b are overlapped with each other, and the first half of the pair of oscillating friction plates 25a and 25b is One of the pair of support plate portions 20a and 20b constituting the support bracket 13a (the left side in FIG. 7) of the support plate portion 20a and the pair of pressing portions 24a and 24b (see FIG. 2). It is sandwiched between the inner surface of one of the pressing portions 24a. Further, in this example, a pair of leaf springs 35a is provided between one side surface (the right side surface in FIG. 7) of the pair of swing friction plates 25a and 25b and the outer side surface of the one support plate portion 20a. , 35b. For this purpose, on the extended line of the center line α {see FIG. 10 (A)} of the up-and-down direction long hole 21a provided in the one support plate portion 20a out of the outer surface of the one support plate portion 20a, By applying a surface pressing process to the upper part and the lower part of the vertically long hole 21a, the outer surface of the one support plate part 20a is recessed inward in the width direction, and the shape seen from the width direction is formed. Rectangular engagement recesses 34a and 34b are provided, and further, burring is performed on the central portions of both engagement recesses 34a and 34b, so that the corresponding portions are outward in the width direction (toward the one pressing portion 24a). B) projecting cylindrical portions 31a and 31b. Then, by fitting the circular holes 30a, 30b provided in the base end portions of the pair of swing friction plates 25a, 25b to the cylindrical portions 31a, 31b with a gap fit, the pair of swing friction plates The plates 25a and 25b are supported so as to be able to swing around both the cylindrical portions 31a and 31b. Further, the pair of leaf springs 35a and 35b are engaged with the respective base plate portions 36a and 36b with the engaging recesses 34a and 34b, and the pair of elastic pressing portions 38a and 38b are engaged with the pair of swinging portions. While being in contact with one side surface of the dynamic friction plates 25a and 25b, the dynamic friction plates 25a and 25b are sandwiched between the outer side surface of the one support plate portion 20a and one side surface of the pair of swing friction plates 25a and 25b. In addition, the free state of the pair of elastic deformation portions 37b and 37b constituting the lower leaf spring 35b of the pair of leaf springs 35a and 35b (the outer surface of the one supporting plate portion 20a and the lower side The amount of protrusion outward in the width direction in a state before being sandwiched between one side surface of the rocking friction plate 25b is determined by the upper plate spring 35a in the free state of the pair of elastic deformation portions 37a and 37a (see above). The upper oscillating friction plate 25a is larger than the protruding amount outward in the width direction in the state before being sandwiched between the outer side surface of one support plate portion 20a and one side surface of the upper oscillating friction plate 25a. It is larger than the thickness.

  Further, the pair of swing friction plates 25a and 25b are inserted through the guide rod holes 32a and 32b provided in the front half portions of the pair of swing friction plates 25a and 25b through the adjusting rod 22a (see FIG. 2). ing. Among these, one guide slot 32a formed in the one rocking friction plate 25a is in a state in which the adjustment rod 22a is located at the center in the vertical slot 21a (shown in FIG. 10B). In the state}, a partial arc shape centered on a point located in front of the center line α and above the cylindrical portion 31a. When the adjustment rod 22a is positioned at the upper end of the movable range within the vertically elongated hole 21a {state shown in FIG. 10A}, the adjustment rod 22a and the one guide When the rear end portion of the long hole 32a is engaged, and the adjustment rod 22a is located at the lower end portion of the movable range within the vertical direction long hole 21a {the state shown in FIG. } The circular hole 30a of the one oscillating friction plate 25a is slidably mounted on the upper cylindrical portion 31a so that the adjusting rod 22a and the front end of the one guide long hole 32a are engaged. It is fitted. On the other hand, the other guide long hole 32b formed in the other swing friction plate 25b is in a state in which the adjustment rod 22a is located at the center in the vertical direction long hole 21a (in FIG. 10B). In the state shown}, a partial arc shape centered on a point located in front of the center line α and below the lower cylindrical portion 31b. When the adjustment rod 22a is located at the upper end of the movable range within the up-and-down direction long hole 21a {state shown in FIG. 10A}, the adjustment rod 22a and the other guide When the front end portion of the long hole 32b is engaged and the adjusting rod 22a is located at the lower end portion of the movable range in the vertical direction long hole 21a {state shown in FIG. 10C} The circular hole 30b of the other rocking friction plate 25b can be swung to the lower cylindrical portion 31b so that the adjusting rod 22a and the rear end portion of the other guide long hole 32b are engaged with each other. It is fitted.

  In the case of this example as described above, as the vertical position of the steering wheel 1 (see FIG. 14) is adjusted, the one oscillating friction plate 25a oscillates around the upper cylindrical portion 31a, and the other The swing friction plate 25b swings around the lower cylindrical portion 31b. That is, in the state where the steering wheel 1 is moved to the adjustable upper end position, the adjustment rod 22a has an upper end portion of the up / down direction long hole 21a as well as the one of the ones as shown in FIG. It engages with the rear end portion of the guide long hole 32a and the front end portion of the other guide long hole 32b. When the steering wheel 1 is displaced downward from this state, as shown in FIGS. 10 (A) → (B) → (C), the one oscillating friction plate 25a is centered on the upper cylindrical portion 31a. 10 oscillates counterclockwise in FIG. 10, and the other oscillating friction plate 25b oscillates counterclockwise in FIG. 10 about the lower cylindrical portion 31b. And in the state which moved the steering wheel 1 to the adjustable lower end position, as shown in FIG.10 (C), the said adjustment rod 22a has the lower end part of the said up-down direction long hole 21a, and said one side. The front end of the guide slot 32a and the rear end of the other guide slot 32b are engaged. On the other hand, when the steering wheel 1 is displaced upward from the lower end position to the upper end position, contrary to the above-described downward displacement, (C) → (B) → (A) in FIG. In this order, the pair of swing friction plates 25a and 25b swings.

  According to this example, the number of sliding friction portions that contribute to holding the steering wheel 1 in the adjusted position between the one support plate portion 20a and one side surface of the displacement bracket 12a. Can be further increased as compared with the structure of the first example of the embodiment described above. Specifically, the number of the sliding friction portions is two in the structure of the first example of this embodiment, whereas the number of the sliding friction portions can be three in the present example. As a result, the force for holding the steering wheel 1 in the adjusted position can be further increased.

A pair of leaf springs 35a and 35b are sandwiched between one side surface of the pair of swing friction plates 25a and 25b and the outer side surface of the one support plate portion 20a. For this reason, in a state where the distance between the pair of pressing portions 24a and 24b is widened, one side surface of the one swing friction plate 25a is moved from the outer surface of the one support plate portion 20a to the other swing friction plate. One side surface of 25b can be reliably separated from the other side surface of the one oscillating friction plate 25a. Therefore, the vertical position of the steering wheel 1 can be adjusted smoothly.
The structure and operation of the other parts are the same as in the first example of the above embodiment.

[Third example of embodiment]
11 to 13 show a third example of the embodiment of the present invention. As in the case of the second example of the above-described embodiment, the steering wheel position adjusting device of this example has a pair of oscillating friction plates 25a and 25b in a state where the front half portions are overlapped with each other. The front half of the pair of swing friction plates 25a and 25b is connected to the outer surface of one of the pair of support plate portions 20a and 20b constituting the support bracket 13a (left side in FIG. 12). It is clamped between the inner surface of one of the pair of pressing portions 24a and 24b (left side in FIG. 12). Accordingly, when the steering wheel 1 (see FIG. 14) is displaced downward from the upper end position to the lower end position, the lower end position is similarly changed to the upper end position in the order of (A) → (B) → (C) in FIG. In the case of the upward displacement, the pair of swinging friction plates 25a and 25b swing in the order of (C) → (B) → (A) in FIG. A pair of leaf springs 35a and 35b is sandwiched between one side surface (the right side surface in FIG. 12) of the pair of swing friction plates 25a and 25b and the outer side surface of the one support plate portion 20a. ing.

Furthermore, in the case of this example, the front-rear position of the steering wheel 1 is between the inner side surface of one of the support plate portions 20a and 20b and the one side surface of the displacement bracket 12a. A telescopic rocking friction plate 39 that rocks and displaces with adjustment is sandwiched. This telescopic rocking friction plate 39 can ensure the required strength and rigidity, such as a steel plate and a stainless steel plate, and is the other side of the inner side surface of the one support plate portion 20a and the one piece of the displacement bracket 12a. The metal plate which can increase the friction coefficient of the engaging portion with the side surface is formed in a substantially sector shape. In order to support the base end of the telescopic rocking friction plate 39 (portion corresponding to the main part of the fan) so as to be rockable, the telescopic position of the steering wheel 1 is relatively displaced with respect to the adjusting rod 22a. A telescopic rocking support shaft 40 is provided in parallel with the adjustment rod 22a on one side surface (left side surface in FIG. 12) of the displacement bracket 12a, which is a portion. The telescopic rocking support shaft 40 passes through a central position in the front-rear direction of the front-rear direction long hole 19a provided in the displacement bracket 12a on one side surface of the displacement bracket 12a, and extends in the axial direction of the steering column 6a. On the imaginary straight line β in the direction orthogonal to the longitudinal direction long hole 19a), the longitudinal long hole 19a is disposed above the longitudinal direction long hole 19a. However, the telescopic rocking support shaft 40 can be installed below the longitudinal slot 19a on the one side surface of the displacement bracket 12a as long as it is on the virtual straight line β. In any case, by setting the telescopic rocking support shaft 40 on the virtual straight line β, the center axis of the telescopic rocking support shaft 40 and the steering wheel 1 are set to the front end position. and the distance L _F between the center axis of the adjustment rod 22a to kick, the distance L _B between the center axis of the in the case where the steering wheel 1 and the rear end position the adjusting rod 22a, the same as each other (L _F = L _B ).

  In the telescopic rocking friction plate 39, a circular hole provided in a portion near the upper end, which is the base end portion of the telescopic rocking friction plate 39, is formed in the telescopic rocking support shaft 40 and the telescopic rocking friction shaft 38. The adjustment rod 22a is inserted into the telescopic guide long hole 41 provided in the front half (lower half) of the telescopic rocking friction plate 39. . The telescopic guide long holes 41 are formed so as to form a smooth curve in a direction in which the distance from the telescopic rocking support shaft 40 is increased from the front end portion to the rear end portion little by little. Yes. Specifically, the telescopic guide long hole 41 is in a state {the state shown in FIG. 13B} in which the adjustment rod 22a is located at the center in the front / rear direction long hole 19a. Further, it has a partial arc shape centering on a point located further forward than the telescopic rocking support shaft 40. The telescopic guide long hole 41 is centered on the tangent of the portion with which the adjusting rod 22a is engaged and the central axis of the telescopic rocking support shaft 40, and the adjusting rod 22a and the telescopic rocking shaft 40 are centered. An angle ψ formed by a tangent line of a virtual arc whose radius is the distance from the dynamic support shaft 40 (the swing direction of the telescopic swing friction plate 39) is constant regardless of the longitudinal position of the adjustment rod 22a. It ’s like that. Such an angle ψ is preferably 10 to 35 degrees. When the front / rear position of the steering wheel 1 is set to the middle position of the adjustable range, the adjustment rod 22a and the front end portion of the telescopic guide long hole 41 are engaged, and the front / rear position of the steering wheel 1 is set. When the rear end position and the front end position of the adjustable range are set, the adjustment rod 22a and the rear end portion of the telescopic guide long hole 41 are engaged with each other. That is, in the case of this example, the adjustment rod 22a and the telescopic swing are moved in the process in which the adjustment rod 22a is displaced along the telescopic guide long hole 41 as the position of the steering wheel 1 in the longitudinal direction is adjusted. The direction in which the distance to the support shaft 40 changes (whether the direction extends or shortens) is opposite to each other with the center position in the front-rear direction within the adjustable range of the steering wheel 1 as a boundary.

  In the present example as described above, the movement of the telescopic rocking friction plate 39 when the steering wheel 1 is displaced in the front-rear direction in order to adjust the front-rear position of the steering wheel 1 is as follows. explain. FIG. 13A shows a state where the steering wheel 1 is moved to an adjustable front end position. In this state, the adjusting rod 22a is engaged with the rear end portion of the longitudinal slot 19a and the rear end portion of the telescopic guide slot 41. Accordingly, by displacing the steering wheel 1 backward from this state, when the adjustment rod 22a is displaced forward in the longitudinal direction long hole 19a, the adjustment rod 22a and the telescopic rocking support shaft 40 13A and 13B, the telescopic rocking friction plate 39 is centered on the telescopic rocking support shaft 40 as shown in FIG. Swings counterclockwise. In the neutral position state shown in FIG. 13B, the adjustment rod 22a is engaged with the front-rear direction center portion of the front-rear direction long hole 19a and the front end portion of the telescopic guide long hole 41. For this reason, when the steering wheel 1 is further displaced rearward from the state shown in FIG. 13B to the rear end position, the adjustment rod 22a and the telescopic swing support shaft 40 The distance between the central axes becomes longer, and the telescopic rocking friction plate 39 is centered on the telescopic rocking support shaft 40 as shown in FIGS. Swing in the direction. On the other hand, when the steering wheel 1 is displaced forward from the rear end position to the front end position, conversely to the forward displacement described above, (C) → (B) → (A The telescopic rocking friction plate 39 is swung in the order of).

According to the steering wheel position adjusting apparatus of the present example as described above, in addition to the force for holding the vertical position of the steering wheel 1, the force for holding the adjusted position in the front-rear direction can be increased.
Since the configuration and operation of the other parts are the same as those of the second example of the above-described embodiment, redundant description is omitted.

DESCRIPTION OF SYMBOLS 1 Steering wheel 2 Steering gear unit 3 Input shaft 4 Tie rod 5, 5a Steering shaft 6, 6a Steering column 7 Universal joint 8 Intermediate shaft 9 Universal joint 10 Car body 11 Axis 12, 12a Displacement bracket 13, 13a Support bracket 14, 14a Outer column 15, 15a Inner column 16, 16a Outer shaft 17, 17a Inner shaft 18 Electric motor 19, 19a Longitudinal holes 20, 20a, 20b Support plate portions 21, 21a Vertical holes 22, 22a Adjusting rod 23 Adjusting lever 24a, 24b Pressing part 25, 25a, 25b, 25z Oscillating friction plate 26 Slit 27 Mounting plate part 28 Locking notch 29 Locking capsule 30, 30a, 30b Circular hole 31, 31a, 31b Cylindrical part 32, 32 , 32b, 32z Guide long hole 33 Holding portion 34, 34a, 34b Engaging recess 35, 35a, 35b Leaf spring 36, 36a, 36b Substrate portion 37, 37a, 37b Elastic deformation portion 38, 38a, 38b Elastic pressing portion 39 Telescopic Rocking friction plate 40 Telescopic rocking support shaft Telescopic guide slot 42 Circular hole

Claims (3)

A cylindrical steering column that supports a steering shaft with a steering wheel supported and fixed at the rear end portion, and rotatably supports the inner side;
A displacement bracket fixed to a part of the steering column;
A column side through hole provided in the displacement bracket in a state of penetrating the displacement bracket in the width direction;
A pair of support plate portions sandwiching the displacement bracket from both sides in the width direction, and a support bracket supported by the vehicle body;
A pair of vertically elongated holes provided in a state of extending in the up-down direction on the mutually matching portions of the pair of support plate parts;
An adjustment rod provided in a state of passing through the column side through hole and the up-down direction long hole in the width direction;
A pair of pressing portions provided at portions projecting from the outer surfaces of the pair of support plate portions at both ends of the adjustment rod;
In a steering wheel position adjusting device, comprising: an expansion / contraction device that expands / contracts an interval between the pair of pressing portions;
A swinging friction plate is sandwiched between a side surface of at least one support plate portion of the pair of support plate portions and a side surface of a counterpart member facing the side surface of the one support plate portion,
The base end portion of the rocking friction plate is pivotally supported with respect to a member that displaces relative to the adjusting rod when the adjusting rod is displaced along the vertically elongated hole. , Engaged with the guide slot provided in the front half of the oscillating friction plate so that only displacement along the guide slot is possible,
A leaf spring capable of elastically expanding and contracting dimensions in the width direction is sandwiched between a side surface of the oscillating friction plate and a side surface of the one support plate portion facing each other.
The substrate portion of the leaf spring is supported with respect to one of the side surface of the oscillating friction plate and the side surface of the one supporting plate portion in a state in which displacement due to oscillation of the oscillating friction plate is prevented. A steering wheel position adjustment device characterized by The leaf spring is provided around a swing support shaft for pivotally supporting a base end portion of the swing friction plate;
The steering wheel position adjusting device according to claim 1. The shape of the substrate portion of the leaf spring viewed from the width direction is non-circular, and an engagement recess recessed in the width direction is provided on the one side surface, and the substrate recess of the leaf spring is provided with the engagement recess. Engaged with the
The position adjustment apparatus of the steering wheel described in any one of Claims 1-2.

Images