JP5293381B2 - Telescopic steering device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To obtain a structure which makes the longitudinal position of a steering wheel adjustable and prevents the steering wheel from being displaced in the forward direction on the secondary collision, and to enable the smooth adjustment of the longitudinal position. <P>SOLUTION: When the longitudinal position is adjusted, an irregular surface 48 for a telescopic lock is separated from an upper surface of an inner column 14b by rocking and displacing an eccentric cam 46 for the telescopic lock by a lock release lever 52 that rotates together with an adjustment lever. This structure prevents the irregular surface 48 for a telescopic lock from rubbing against the upper surface of an inner column 14b. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to an improvement in a telescopic steering device for adjusting the front-rear position of a steering wheel. Specifically, it is easy to protect the driver by preventing inadvertent changes in the front and rear positions of the steering wheel in the event of a secondary collision, and the structure can be adjusted smoothly during normal times. Is realized.

  The steering apparatus for an automobile is configured as shown in FIG. 6, 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, and the steering shaft 5 is rotatably supported by the steering column 6 with the cylindrical steering column 6 inserted in the axial direction. Has been. 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.

  With such a steering device, a tilt mechanism for adjusting the vertical position of the steering wheel 1 and a telescopic mechanism for adjusting the front-rear position according to the physique and driving posture of the driver have been widely known. ing. In order to constitute the tilt mechanism, the steering column 6 is in the width direction with respect to the vehicle body 10 (the width direction is the width direction of the vehicle body and coincides with the left-right direction. Description and claims) The same is applied to the entire range.) The rocking displacement centering on the pivot 11 installed is supported. Further, the displacement bracket fixed to the rear end portion of the steering column 6 with respect to the support bracket 12 supported by the vehicle body 10 is the vertical direction and the front-rear direction (the front-rear direction refers to the front-rear direction of the vehicle body. The same throughout the specification and claims). Among these, in order to constitute a telescopic mechanism that enables displacement in the front-rear direction, the steering column 6 has a structure in which an outer column 13 and an inner column 14 are telescopically combined to expand and contract, and the steering shaft 5 The outer tube 15 and the inner shaft 16 are combined with each other so as to be able to transmit torque and expand and contract by spline engagement or the like. The illustrated example also incorporates an electric power steering device that reduces the force required to operate the steering wheel 1 using the electric motor 17 as an auxiliary power source.

  In the case of a tilt mechanism or a telescopic mechanism, the position of the steering wheel 1 can be adjusted or fixed at the adjusted position based on the operation of the adjustment lever, except for the electric mechanism. For example, in Patent Document 1, as shown in FIGS. 7 to 8, the axial dimension of the cam device 20 is expanded and contracted and the cam member 21 is swung and displaced based on the rotation of the hook-shaped member 19 based on the adjusting lever 18. The structure to be made is described. In the case of this conventional structure, the movable bracket 22 fixed to the outer column 13a is engaged with and disengaged from the support bracket 12a based on the expansion and contraction of the cam device 20. Further, based on the rocking displacement of the cam member 21, whether the inner column 14a is slidable with respect to the outer column 13a is switched.

  In the case of the conventional structure described in Patent Document 1 as described above, the number of friction engagement portions in the case where the front and rear positions of the steering wheel 1 are fixed is increased as compared with the previous structure (prior structure). Thus, the strength and rigidity relating to the front-rear position fixing can be increased. However, there is room for improvement in order to enhance the driver protection so that the position of the steering wheel 1 does not change regardless of the large impact load applied to the steering wheel 1 in the event of a collision. This point will be described below.

  In the event of a collision accident, a so-called secondary collision in which the driver's body collides with the steering wheel occurs following a so-called primary collision in which the automobile collides with another automobile or the like. At the time of this secondary collision, a large impact load is applied to the steering wheel that is directed diagonally forward and upward. On the other hand, in the case of the conventional structure shown in FIGS. 6 to 8, the force for fixing the steering wheel 1 to the adjusted position is obtained only by the frictional force, so that the position is shifted based on the large impact load. there is a possibility. Specifically, the position of the steering wheel 1 may move forward or upward. As a result, the positional relationship between the steering wheel 1 and the driver's body is shifted from the adjusted position (appropriate position). In this state, the airbag opened (inflated) behind the steering wheel 1 cannot effectively receive the driver's body, which is disadvantageous in terms of driver protection.

  Conventionally, the structures described in Patent Documents 2 and 3 are known as structures for preventing the steering wheel from shifting in a secondary collision. Of these, in the case of the conventional structure described in Patent Document 2, a pair of holding arms are arranged on both sides of a plate piece fixed to the outer peripheral surface of the steering column, and these plate pieces are attached to both arm portions at the time of a secondary collision. To prevent the steering column from being displaced forward. In the case of such a conventional structure described in Patent Document 2, unless the accuracy of each component is sufficiently ensured, the force to prevent the steering column from being displaced forward becomes non-uniform. Can be uncertain.

  Further, in Patent Document 3, as shown in FIG. 9, an eccentric cam 23 is provided on a movable bracket 22 fixed to the steering column 6b, and this eccentricity is detected when the steering column 6b tends to be displaced upward. A structure is described in which an uneven portion provided on the outer peripheral edge of the cam 23 bites into a rear end edge of a support bracket 12b provided on the vehicle body side to prevent the steering column 6b from being displaced upward. In the case of the conventional structure described in Patent Document 3, the function of preventing the upward displacement is excellent, but the function of preventing the forward displacement is not provided. Although the structure described in Patent Document 3 may be applied to a structure that prevents the inner column from being displaced forward, when applied as it is, the front and rear positions of the steering wheel can be adjusted smoothly during normal operation. There is a possibility of disappearing.

  In other words, in order to smoothly adjust the front / rear position of the steering wheel (without causing excessive resistance or abnormal noise), the eccentricity is performed with the adjustment lever rotated downward for this front / rear position adjustment. It is necessary to reliably separate the uneven portion of the cam and the outer peripheral surface of the inner column. On the other hand, in recent years, in order to protect the driver's knee part in the event of a collision accident, in order to minimize the part protruding downward from the steering column, each component for adjusting the position of the steering wheel is provided above the steering column. It is considered to be installed in With such a structure, when the above-described blocking structure for the inner column by the eccentric cam is implemented, the eccentric lever can be adjusted even when the adjustment lever is rotated downward to adjust the front / rear position adjustment of the steering wheel. The cam is rotated downward by its own weight, and the uneven portion of the eccentric cam and the outer peripheral surface of the inner column are likely to be in contact with each other. In such a state, the vertical position of the steering wheel cannot be adjusted smoothly.

Japanese Patent No. 3783524 US Pat. No. 6,039,350 US Pat. No. 7,021,660

  In view of the circumstances as described above, the present invention relates to a telescopic steering device that can adjust the front / rear position of a steering wheel, and when the front / rear position of the steering wheel is adjusted, the uneven portion of the eccentric cam and the counterpart surface are reliably separated from each other. Thus, the present invention has been invented to realize a structure capable of smoothly adjusting the front-rear position.

The telescopic steering device of the present invention includes an outer column, an inner column, a steering shaft, a pair of support plate portions, a hook-like member, and an adjustment lever, as in the conventionally known telescopic steering device. Prepare.
Of these, the outer column is cylindrical, and at least a part of the inner diameter in the axial direction can be enlarged or reduced.
The inner column has a cylindrical shape and is fitted and supported on the inner diameter side of the outer column so as to be capable of axial displacement.
The steering shaft is rotatably supported on the inner diameter side of the inner column, and fixes a steering wheel to a rear end portion that protrudes rearward from the rear end opening of the inner column. Such a steering shaft is configured to be extendable and contractible by, for example, serration engagement between the outer tube and the inner shaft. However, instead of making the intermediate shaft (a member represented by reference numeral “8” in FIG. 6) extendable and retractable, a structure in which the steering shaft is not expanded and contracted may be employed. In this case, the amount of protrusion of the front end portion of the steering shaft from the front end opening portion of the steering column changes with the adjustment of the front / rear position of the steering wheel.
Further, the both support plate portions are provided in a fixed portion in a state in which a portion of the outer column in which the inner diameter can be expanded and contracted is sandwiched from both sides in the width direction.
The flange-shaped member is arranged in the width direction, and interferes with the inner column at a part of the outer column and a vehicle body side through hole formed at a position where the both support plate portions are aligned with each other. The column side through hole formed in the portion not to be inserted is inserted. Then, with the rotation of the adjustment lever, the distance between the surfaces of the two support plate portions facing each other is enlarged or reduced.
Furthermore, the adjustment lever is provided at the base end portion of the bowl-shaped member, and expands and contracts the space between the mutually opposing surfaces of the both support plate portions as it rotates. In order to increase or decrease the distance, the adjusting lever and the hook-shaped member may be rotated synchronously, or only the adjusting lever may be rotated without rotating the hook-shaped member. May be. In short, by rotating the rotating member and the non-rotating member opposed to the member in the rotating direction, an axial force is generated in the bowl-shaped member to expand or contract the interval.

In particular, the telescopic steering device of the present invention includes a support shaft, a telescopic locking eccentric cam, an elastic member, and a lock release lever.
Of these, the support shaft is supported by a part of the outer column in a state of being disposed in parallel with the bowl-shaped member.
The telescopic lock eccentric cam is supported at an intermediate portion of the support shaft so as to be rotatable with respect to the support shaft. A portion of the telescopic lock eccentric cam that opposes the outer peripheral surface of the inner column or the surface of the member fixed to the inner column increases in distance from the center of the support shaft toward the rear. It has an arc edge. And the telescopic lock uneven part is formed on the convex arc edge of the telescopic lock. The telescopic lock irregularities are serrated or triangular.
The elastic member is provided between the telescopic lock eccentric cam and the outer column or a member fixed to the outer column. It has elasticity in a direction in which a front portion of the telescopic lock uneven portion is brought into contact with the outer peripheral surface of the inner column or the surface of a member fixed to the inner column.
Further, the lock release lever is supported at the base end portion by the intermediate portion of the hook-shaped member, and rotates together with the hook-shaped member to be engaged with and disengaged from the telescopic lock eccentric cam. Then, as the adjustment lever is rotated from the state in which the position of the steering wheel is fixed to the state in which the adjustment is performed, the telescopic lock eccentric cam is moved from the counterpart portion to the front end portion of the telescopic lock uneven portion. The telescopic lock eccentric cam is oscillated and displaced in the direction of separation.

The present invention relates to an improvement of a telescopic steering device for adjusting the front-rear position of the steering wheel, but can also be implemented in combination with a tilt-type steering device for adjusting the vertical position. In this case, as in the invention described in claim 2, the front end portion of the outer column or the inner column is supported so as to be able to swing and swing around a pivot arranged in parallel with the bowl-shaped member. To do.
Further, the vehicle body side through hole is a long hole that is long in the arc direction centering on the pivot, and the rear end edges of the both support plate portions are arc-shaped convex edges centering on the pivot.
Further, a pair of tilt lock eccentric cams are supported at both ends of the support shaft so as to be rotatable about the support shaft.
The portion of the tilt-lock eccentric cam that faces the convex edge is a tilt-lock convex arc edge that increases in distance from the center of the support shaft as it goes upward. Then, an uneven portion for tilt lock is formed. The tilt lock uneven portion also has a sawtooth shape or a triangular wave shape.
Further, in a state where the adjustment lever is rotated to adjust the position of the steering wheel, a connecting member for separating the tilt lock uneven portion and the convex edge portion is displaced together with the adjustment lever. It is provided between the portion and the eccentric cams for both tilt locks.

  When carrying out the invention described in claim 2, more specifically, as in the invention described in claim 3, the elastic member is externally fitted to the intermediate portion of the support shaft. The torsion coil spring is engaged with one end portion of the lock release lever and the other end portion of the outer column. Further, the connecting member is a torsion coil spring having a coil portion at an intermediate portion, one end portion being locked to a tilt lock eccentric cam, and a portion rotating together with the hook-shaped member.

The present invention configured as described above acts as follows to suppress the movement of the position of the steering wheel at the time of a secondary collision.
First, when adjusting the position of the steering wheel, the interval between the mutually opposing surfaces of the pair of support plate portions constituting the support bracket is expanded by rotating the adjustment lever in a predetermined direction. In this state, the front / rear position of the steering wheel is adjusted while sliding the inner column relative to the outer column.

  When the adjusting lever is rotated in a predetermined direction as described above, a lock release lever that rotates together with the hook-shaped member engages with the telescopic locking eccentric cam, and this telescopic locking eccentric cam is used for the telescopic locking. The front end portion of the concavo-convex portion is oscillated and displaced in a direction away from the outer peripheral surface of the inner column or the surface of a member fixed to the inner column. As a result, the uneven portion for telescopic locking and the mating surface do not rub against each other, and the front-rear position of the steering wheel can be adjusted smoothly. Such a smooth adjustment operation can be surely realized even with a structure in which the support shaft, the telescopic lock eccentric cam, and the like are installed above the outer column.

In the case of the invention described in claims 2 to 3, the telescopic lock convex arc edge is separated from the mating surface as the adjusting lever is rotated. In addition to this, the convex arc edge for tilt lock is separated from the curved edge portion provided at the rear end edge of both support plate portions. Therefore, the vertical position of the steering wheel can be adjusted while the outer column is displaced in the vertical direction with respect to the pair of support plate portions.
After adjusting the steering wheel to a desired position (front-rear position and vertical position if necessary), the adjustment lever is rotated in a direction opposite to the predetermined direction.

As a result of the rotation in the opposite direction, the distance between the opposing surfaces of the two support plate portions is reduced, and these two support plate portions strongly hold the outer column from both sides in the width direction. As a result, the inner diameter of the outer column is reduced, the inner peripheral surface of the outer column is strongly pressed against the outer peripheral surface of the inner column, and the inner column is prevented from being displaced with respect to the outer column. The front-rear position of the steering wheel is fixed.
In the second to third aspects of the invention, at the same time, the outer column is prevented from moving with respect to the both support plate portions, and the vertical position of the steering wheel is also fixed.

In this manner, in the state where the adjustment lever is rotated until the front-rear position of the steering wheel is fixed (in the case of the invention described in claims 2 to 3, the vertical position is also the vertical position). The support shaft is rotated in the direction opposite to the predetermined direction by the connecting member, and the portion of the convex arc edge for telescopic locking that has the smallest distance from the center of the support shaft is the outer peripheral surface of the inner column or this It contacts the surface of the member fixed to the inner column.
In the case of the inventions described in claims 2 to 3, in accordance with this, the portion of the convex arc edge for tilt lock whose distance from the center of the support shaft is the smallest is the both support plate portions. It abuts on the curved edge provided on the rear edge.

From this state, when a forward impact load is applied to the inner column and the outer column in accordance with a secondary collision, the telescopic locking concave and convex portions provided on the convex arc edge of the telescopic locking are formed on the inner column. It bites into the outer peripheral surface or the surface of a member fixed to the inner column. As a result, a large force is applied to prevent the steering wheel from moving forward, and the position of the steering wheel can be effectively prevented from moving forward. At this time, the force required to cause the telescopic lock irregularities to bite into the outer peripheral surface of the inner column or the surface of the member fixed to the inner column is small in the initial stage and gradually increases. Such characteristics are preferable in terms of protecting the driver by absorbing impact energy transmitted from the steering wheel to the inner column and the outer column.
In the case of the invention described in claims 2 to 3, the position of the steering wheel is prevented from moving forward as described above, and at the same time, the tilt lock is provided on the convex arc edge for tilt lock. The uneven portion bites into the curved edge portion, thereby preventing the position of the steering wheel from shifting upward.

The perspective view which shows one example of embodiment of this invention. Similarly disassembled perspective view. The disassembled perspective view which takes out and shows a part of components. XX sectional drawing of FIG. The YY sectional view of Drawing 4 showing the state (A) which fixed the position of a steering wheel, and the state (B) which performs position adjustment. The partial cutting side view which shows an example of the steering device for motor vehicles incorporating the telescopic steering device. The longitudinal section side view which shows an example of the telescopic steering apparatus known conventionally. The expanded ZZ sectional drawing of FIG. The partial side view which shows one example of the position shift prevention structure of a steering wheel known conventionally.

  1 to 5 show an example of an embodiment of the present invention. The telescopic steering device of this example includes a tilt mechanism for adjusting the vertical position in addition to the telescopic mechanism for adjusting the front-rear position of the steering wheel 1 (see FIG. 6). In the case of the present example in order to constitute the telescopic mechanism, the rear half of the inner column 14b that can be expanded and contracted is provided in the axial direction on the inner diameter side of the outer column 13b that is generally referred to as a housing portion. A displacement in the (oblique direction) is possible. This inner column 14b is telescopically fitted so that the rear end portion of the first half element 25 having a cylindrical shape and a relatively small diameter and the front end portion of the second half element 26 having a cylindrical shape and a relatively large diameter can be displaced in the axial direction. By combining, it is possible to expand and contract. A pivot bracket 24 is fixed to the front end portion of the inner column 14b, and the pivot bracket 24 swings around the pivot 11 (see FIGS. 6 to 7) disposed in the width direction with respect to the vehicle body. The displacement is supported as possible. Based on this swing displacement, the height position of a steering wheel 1 described later can be adjusted. That is, in the case of this example, a telescopic mechanism and a so-called hip swing type tilt mechanism that swings around the front end portion of the entire steering column are combined.

  In order to constitute the telescopic mechanism, in addition to making the inner column 14b extendable, the steering shaft 5a supported rotatably inside the inner column 14b is made extendable so that the steering wheel 1 The front-rear position can be adjusted. As shown in FIG. 4, the steering shaft 5a is formed by combining an outer tube 15a and an inner shaft 16a so as to be capable of torque transmission and expansion and contraction, and has an inner diameter of the inner column 14b. On the side, only rotation is supported by a combination of a single row deep groove type ball bearing and a needle bearing. In this state, the steering wheel 1 can be fixed to a portion protruding from the rear end opening of the inner column 14b at the rear end portion of the steering shaft 5a (the outer tube 15a constituting the steering shaft 5a).

  On the other hand, the outer column 13b is manufactured by casting a light metal such as an aluminum alloy, and includes a main part 27, a sandwiched part 28, and a pair of left and right locking arm parts 29 and 29. Of these, the main portion 27 is formed with a slit-like discontinuous portion 30 at the upper end portion extending from the rear end portion to the intermediate portion with respect to the axial direction so that the portion excluding the front end portion is formed in a cylindrical shape. Yes. Therefore, the inner diameter of at least the rear end portion of the main portion 27 can be elastically expanded / contracted. The sandwiched portion 28 is provided on the upper surface of the intermediate portion of the main portion 27 in a state of sandwiching the discontinuous portion 30 from both the left and right sides and projecting upward. The left and right outer surfaces are substantially parallel to each other. Thus, the distance between these two outer surfaces is larger than the outer diameter of the main portion 27. Further, the both locking arm portions 29, 29 are provided for locking the lower end portions of the tension springs 31, 31 which are spanned between the support bracket 12c described below.

  The outer column 13b as described above is supported so as to be movable up and down with respect to the support bracket 12c supported on the vehicle body. The support bracket 12c is made of a metal plate having sufficient strength and rigidity, such as a steel plate, and includes a pair of left and right mounting plate portions 32, 32 and support plate portions 33, 33. The support bracket 12c can be detached forward based on a large impact load applied during a secondary collision, with the mounting plate portions 32 and 32 of the support bracket 12c being attached to the vehicle body by sliding plates 34 and 34 and bolts (not shown), respectively. To support. The support plate portions 33, 33 are bent at a right angle downward from the mounting plate portions 32, 32, are parallel to each other, and pivotally support the pivot bracket 24 at a position where they are aligned with each other. Long holes 35, 35 that are long in the arc direction (oblique vertical direction) centered on the pivot axis are provided. Both the long holes 35 correspond to the vehicle body side through holes described in the claims. In the example shown in the figure, the connecting plate 36 is welded and fixed to the upper end portions of the both supporting plate portions 33 and 33, and the mounting plate portions 32 and 32 and the supporting plate portions 33 and 33 are connected and fixed in pairs. doing.

  The outer column 13b is supported so as to be movable up and down between the support plate portions 33, 33 constituting the support bracket 12c as described above. For this purpose, both the long holes 35 and 35 are provided in a state of penetrating the sandwiched portion 28 in the left-right direction with the sandwiched portion 28 disposed between the support plate portions 33 and 33. Further, the hook-shaped member 19a is inserted through the through hole 37 corresponding to the column side through hole described in the claims. This flange-shaped member 19a is for expanding and contracting the space between the opposing surfaces of the two support plate portions 33, 33 as it rotates, and both ends thereof are arranged outside the support plate portions 33, 33. It protrudes from the side. The base portion of the adjusting lever 18a is coupled and fixed to the base end portion (the left end portion in FIGS. 1 to 3) of the hook-shaped member 19a, and the hook-shaped member 19a is connected to the tip portion (the right end portion in FIGS. 1 to 3). The outer surface of the base portion of the holding plate 38 that is externally fitted in a state in which the rotation of the holding plate 38 is prevented is held down by a nut 39 to prevent the holding plate 38 from coming off.

  Further, a cam device 20a is provided between the inner side surface of the base end portion of the adjustment lever 18a and the outer side surface of one (left side in FIGS. 1 to 3) of the support plate 33, and as the adjustment lever 18a rotates. Thus, the interval between the both side surfaces can be enlarged or reduced. When adjusting the position of the steering wheel 1, the adjustment lever 18 a is rotated downward (clockwise in FIGS. 1 to 5) to support the inner surface of the base end portion of the adjustment lever 18 a and the one support. The space | interval with the outer surface of the board part 33 is shortened. Then, the interval between the inner side surfaces of the pair of support plate portions 33, 33 is elastically expanded, and the inner side surface of both the support plate portions 33, 33 and the outer side surface of the sandwiched portion 28 of the outer column 13b. The surface pressure of the contact portion is reduced or lost. At the same time, the inner diameter of the outer column 13b is elastically expanded, and the contact pressure between the inner peripheral surface of the outer column 13b and the outer peripheral surface of the rear half element 26 of the inner column 14b is reduced. Displaceable in the front-rear direction. As a result, the front / rear position and the vertical position of the steering wheel 1 can be adjusted.

  In this state, the entire weight of the portion where the two tension springs 31, 31 are lifted or lowered together with the steering wheel 1 spanned between the support bracket 12 c and the both locking arm portions 29, 29, or Support some. Therefore, there is little need to support this weight by hand when adjusting the vertical position of the steering wheel 1, and this adjustment work can be performed easily. After the position adjustment, if the adjustment lever 18a is rotated upward (counterclockwise in FIGS. 1 to 3 and 5), the inner side surface of the base end portion of the adjustment lever 18a and the outer side surface of the one mounting plate portion 33 The space between the inner surfaces of the support plate portions 33, 33 is reduced instead of the interval between the support plate portions 33, 33, and the surface of the contact portion between the inner surface of the support plate portions 33, 33 and the outer surface of the sandwiched portion 28 As the pressure increases, the steering wheel 1 is supported at the adjusted position. In order to increase or decrease the distance, it is sufficient that the pair of cam members constituting the cam device 20a are relatively displaced in the rotational direction. The hook-shaped member 19a may rotate together with the adjusting lever 18a, but does not necessarily rotate (it may be displaced only in the axial direction without rotating).

  Further, in the case of the structure of the present example, the rear column of the outer column 13b also protrudes upward from the support plate portions 33 and 33 in the same manner as the sandwiched portion 28. The protruding portion 40 is provided. The protruding portion 40 is also provided in a state of sandwiching the discontinuous portion 30 from both the left and right sides, like the sandwiched portion 28. Also, the width dimension of the protruding portion 40 is slightly smaller than the width dimension of the sandwiched portion 28, and between the projecting portion 40 and the sandwiched portion 28, as shown in FIG. The stepped surfaces 41 are provided on the left and right side surfaces of the outer column 13b.

  The support shaft 43 is inserted through a through hole 42 formed in a state of penetrating the protruding portion 40 as described above in the width direction. The support shaft 43 is disposed in parallel with the flange-shaped member 19a, and is provided with a head portion 44 at a base end portion (left end portion in FIGS. 1 to 3) and a distal end portion (right end portion in FIGS. 1 to 3). The nut 45 is screwed onto the male thread portion provided in (). A telescopic locking eccentric cam 46 is provided at the center of the portion between the head 44 and the nut 45, and tilt locking eccentric cams 47 and 47 are provided at both ends, respectively. It fits in the state.

  Among the eccentric cams 46, 47, 47, the telescopic locking eccentric cam 46 provided in the center portion enters the discontinuous portion 30 of the outer column 13b and faces the upper surface of the inner column 14b. Of the outer peripheral edge portion of the telescopic lock eccentric cam 46, the portion facing the outer peripheral surface of the inner column 14b is inclined in a direction in which the distance from the center of the support shaft 43 increases toward the rear. A convex arc edge for telescopic locking. And the telescopic lock concavo-convex portion 48 is formed on the convex arc edge of the telescopic lock. Further, in the case of the structure of the present example, a portion of the outer peripheral edge portion of the telescopic lock eccentric cam 46 that is rearward from the large-diameter side end portion of the telescopic lock uneven portion 48 is subjected to a collision. The over-rotation preventing stopper 49 is provided so as to protrude sufficiently rearward from the portion. Such an eccentric cam 46 for telescopic lock is a metal harder than a metal material such as medium carbon steel, high carbon steel, carburized steel, bearing steel, etc., which constitutes the inner column 14b, such as low carbon steel or aluminum alloy. Made of materials.

  A telescopic lock biasing spring 50, which is an elastic member, is provided between the telescopic locking eccentric cam 46 and the outer column 13b as described above. This telescopic lock urging spring 50 is a torsion coil spring formed by bending a spring steel wire, and one end (the upper end in FIG. 5) of the telescopic lock 50 is fitted to the support shaft 43. The other end of the eccentric cam 46 is engaged with a locking recess 51 formed in the outer column 13b. In this state, the telescopic locking eccentric cam 46 is given elasticity in the direction in which the telescopic locking concave and convex portion 48 abuts against the upper surface of the inner column 14b (clockwise in FIG. 5).

  A lock release lever 52 is provided at the central portion of the hook-shaped member 19a in a state of rotating in synchronization with the hook-shaped member 19a while facing the telescopic locking eccentric cam 46. That is, the mounting hole 53 having a non-circular cross section (in the illustrated example, an oval shape) formed in the base end portion of the unlocking lever 52 and the non-cylindrical portion formed in the central portion of the flange-shaped member 19a are rattled. (Preferably with an interference fit). The tip 54 of the lock release lever 52 is opposed to a receiving step surface 55 provided on the outer peripheral surface of the base of the telescopic locking eccentric cam 46 so as to face upward.

  Then, in order to enable the position adjustment of the steering wheel 1, the tip end 54 is rotated in a state where the adjusting lever 18 a is rotated downward and the hook-shaped member 19 a is rotated clockwise in FIG. 5. By pressing the receiving step surface 55 downward, the telescopic lock eccentric cam 46 resists the elasticity of the telescopic lock urging spring 50 {as shown in FIG. 5 (A) → (B). To counterclockwise. In the case of this example, by providing such a lock release lever 52, the position of the steering wheel 1 is adjusted regardless of the structure in which the telescopic locking eccentric cam 46 is disposed above the outer column 13b. The telescopic lock concavo-convex portion 48 and the upper surface of the inner column 14b are reliably separated as shown in FIG. 5B so that the front-rear position of the steering wheel 1 can be adjusted smoothly. .

  On the other hand, both the tilt-lock eccentric cams 47, 47 are opposed to or abutted against the rear end edges of the both support plate portions 33, 33 provided on the support bracket 12c (phases in the width direction coincide). The rear end edges of these support plate portions 33 and 33 are convex arc-shaped curved edges 56 centered on the pivot 11 that pivotally supports the pivot bracket 24. Therefore, even when the support shaft 43 is moved up and down with respect to the support bracket 12c as the vertical position of the steering wheel 1 is adjusted, the distance between the support shaft 43 and the curved edges 56 does not change. . Of the outer peripheral edge portions of the tilt-lock eccentric cams 47, 47, the portion facing both the curved edge portions 56 is the upper portion (referred to as a positional relationship in a state where the position of the steering wheel 1 is fixed). The same is applied to the entire specification and claims.) Tilt tilted in a direction in which the distance from the center of the support shaft 43 increases toward the center (the center is biased forward and upward from the center of the support shaft 43). Convex arc edge for locking. The tilt lock uneven portion 57 is formed on the tilt lock convex arc edge. Further, of the two tilt lock eccentric cams 47, 47, the portion opposite to the convex arc edge for tilt lock is extended radially outward across the support shaft 43 to form a driven arm portion 58. Yes.

  Furthermore, in the case of the structure of this example, a stopper 59 for preventing excessive rotation at the time of collision is provided on the upper portion of the tilt lock concavo-convex portion 57 in the outer peripheral edge portions of the tilt lock eccentric cams 47, 47. Provided. The top part of the stopper 59 for preventing excessive rotation at the time of collision exists substantially at the tangential position of the outer diameter side end part of the convex arc edge for tilt lock. The two tilt lock eccentric cams 47, 47 each having such a configuration are low carbon steels that constitute the support bracket 12c, such as medium carbon steel, high carbon steel, carburized steel, bearing steel and the like. And made of a metal material harder than a metal material such as an aluminum alloy.

  Furthermore, tilt lock engagement / disengagement springs 60, 60, each of which is a connecting member, are provided between the adjustment lever 18a and the holding plate 38 and the eccentric cams 47, 47 for both tilt locks. The movement of the hook-shaped member 19a that rotates together with 18a can be transmitted to the eccentric cams 47, 47 for both tilt locks. In the case of this example, the springs 60 and 60 for engaging and disengaging both tilt locks are formed by bending a spring steel wire, and one end portion is the base end of the adjusting lever 18a or the restraining member. The other end is locked to the tip of the plate 38 and the tip of the driven arm 58 of the tilt lock eccentric cam 47, 47, respectively. Moreover, the coil part 61 for ensuring the bending amount is provided in the intermediate part. The coil portion 61 is provided to give appropriate elasticity to the eccentric cams 47 and 47 for both tilt locks regardless of some manufacturing errors.

  By constructing as described above, the tilt lever eccentric cams 47 and 47 are moved as shown in FIGS. 1 to 3 as the adjusting lever 18a is rotated upward to fix the position of the steering wheel 1. It is designed to rotate counterclockwise. Then, along with this rotation, the lower end portion or the intermediate portion of the tilt lock uneven portion 57 of both the tilt lock eccentric cams 47, 47 is brought into contact with the curved edge portion 56 on the support bracket 12c side. Yes. In this state, the shape and size of each component are regulated so that the front end portion of the telescopic locking concavo-convex portion 48 of the telescopic locking eccentric cam 46 abuts against the upper surface of the inner column 14b.

The telescopic steering device of the present example configured as described above operates as follows to make it possible to adjust the front-rear position and the vertical position of the steering wheel 1, and the position of the steering wheel 1 at the time of a secondary collision. By suppressing the movement forward and upward, the driver who collides with the steering wheel 1 is enhanced in protection.
First, when adjusting the position of the steering wheel 1, the adjusting lever 18a is rotated downward. As a result, as described above, due to the action of the cam device, the surface pressure of the contact portion between the inner surface of the mounting plate portions 33, 33 and the outer surface of the sandwiched portion 28 of the outer column 13b is reduced or lost. To do.

  In this state, the front-rear position of the steering wheel 1 can be adjusted. In the case of this example, the front / rear position can be adjusted by sliding the latter half element 26 of the inner column 14b with respect to the outer column 13b. At this time, the inner column 14b expands and contracts. At the time of such an adjustment operation of the front / rear position, the upper surface of the inner column 14b and the telescopic lock eccentric cam 46 are completely separated from each other as shown in FIG. Can be done. Furthermore, in the case of this example, in addition to this, the vertical position of the steering wheel 1 can be adjusted as follows. That is, when the adjusting lever 18a is rotated downward, as described above, the surface of the contact portion between the inner side surfaces of the support plate portions 33 and 33 and the outer side surface of the sandwiched portion 28 of the outer column 13b. Pressure is reduced or lost. Further, both the tilt lock eccentric cams 47, 47 are rotated in the clockwise direction in FIGS. 1 to 3, and the tilt lock uneven portions 57 of the both tilt lock eccentric cams 47, 47 are the both curved edge portions 56. Separate from. In this state, the vertical position of the steering wheel 1 can be adjusted by moving the hook-shaped member 19a along the long holes 35, 35 of the support plate portions 33, 33.

  After adjusting the steering wheel 1 to a desired position as described above, the adjusting lever 18a is moved in the direction opposite to the predetermined direction (counterclockwise in FIGS. 1 to 3), and the adjusting lever 18a is moved to the outer column 13b. And turn upward until it is substantially parallel to the inner column 14b. As a result of the rotation in the opposite direction, the support plate portions 33, 33 strongly hold the outer column 13b from both sides in the width direction by the operation of the cam device as described above, and the vertical position of the steering wheel 1 is increased. Is fixed. At the same time, as the width dimension of the discontinuous portion 30 is reduced, the inner diameter of the outer column 13b is reduced, and the inner peripheral surface of the outer column 13b is strongly pressed against the outer peripheral surface of the inner column 14b. , 14b is prevented from relative displacement in the axial direction, and the front-rear position of the steering wheel 1 is fixed.

  In this manner, when the adjustment lever 18a is rotated upward until the position of the steering wheel 1 is fixed, the distal end portion 54 of the lock release lever 52 is received by the telescopic lock eccentric cam 46. Separated from the step surface 55. As a result, the telescopic lock eccentric cam 46 is rotated in the clockwise direction in FIG. 5 by the elastic force of the telescopic lock biasing spring 50, and as shown in FIG. The telescopic lock concavo-convex portion 48 has a small-diameter side end or intermediate portion that abuts on the upper surface of the inner column 14b. Further, both the tilt lock eccentric cams 47, 47 are pulled by the tilt lock engaging / disengaging springs 60, 60 so as to approach the curved edges 56, 56. Of the tilt lock uneven portions 57 of both the tilt lock eccentric cams 47, 47, the lower end portion having the smallest distance from the center of the support shaft 43 is the rear of the support plate portions 33, 33. It abuts on the curved edge portion 56 provided at the end edge.

  With the steering wheel 1 fixed in this manner, when an impact load directed forward and upward is applied to the inner column 14b and the outer column 13b due to a secondary collision, the following is performed. The position of the steering wheel 1 is prevented from shifting. First, as the inner column 14b tends to be displaced forward, a portion of the telescopic lock concavo-convex portion 48 that meshes with the upper surface of the inner column 14b is formed on the telescopic concavo-convex portion 48. It tends to move backward, that is, to a portion where the distance from the center of the support shaft portion 41 is large. As a result, the biting depth of the telescopic lock concavo-convex portion 48 with respect to the upper surface of the inner column 14b gradually increases. Since a large resistance acts on the increase of the biting depth in this way, it is possible to suppress the steering wheel 1 from being displaced forward. When the impact load associated with the secondary collision is large and the amount of rotation of the telescopic lock eccentric cam 46 is increased, the excessive rotation prevention stopper 49 at the time of collision strikes the upper surface of the inner column 14b and the telescopic lock eccentric cam. 46 no longer rotates (clockwise in FIGS. 1 to 3 and 5). In this state, the force for suppressing the forward displacement of the steering wheel 1 is sufficiently large, and the steering wheel 1 is not displaced further forward. The telescopic locking eccentric cam 46 is made of a material harder than the inner column 14b, so that the biting is surely performed.

  Further, the upward movement of the steering wheel 1 is caused by the tilt lock uneven portion 57 provided on the tilt lock convex arc edges of the tilt lock eccentric cams 47, 47 being bent by the support plate portions 33. This is achieved by biting into the edge 56. That is, when the outer column 13b tends to be displaced upward with respect to the support plate portions 33 and 33 (the support bracket 12c provided with the support plate portions 33 and 33) at the time of a secondary collision, both the curved edge portions 56 and 56 and the both tilts are formed. The tilt lock eccentric cams 47 and 47 tend to rotate counterclockwise in FIGS. 1 to 3 about the support shaft 43 based on the engagement with the locking uneven portion 57.

  For this reason, a portion of the tilt lock uneven portion 57 that meshes with the curved edge portions 56, 56 is located above the tilt lock uneven portion 57, that is, a distance from the center of the support shaft 43. Tends to move to larger parts. As a result, the biting depth of the tilt lock concavo-convex portion 57 with respect to the two curved edge portions 56, 56 gradually increases. Since a large resistance acts on the increase of the biting depth in this way, it is possible to suppress the steering wheel 1 from being displaced upward. When the impact load accompanying the secondary collision is large and the rotation amount of the tilt lock eccentric cams 47, 47 increases, the over-rotation prevention stopper 59 at the time of collision hits both the curved edges 56, 56, and the tilt The locking eccentric cams 47, 47 will not rotate any further. In this state, the force for suppressing the upward displacement of the steering wheel 1 is sufficiently large, and the steering wheel 1 is not displaced further upward. The tilt lock eccentric cams 47, 47 are harder than the support bracket 12c, so that the biting is surely performed.

  As a result, a large force is applied to prevent the steering wheel 1 from being displaced forward and upward, and the position of the steering wheel 1 can be effectively prevented from shifting. At this time, in order to cause the tilt lock uneven portion 57 of the convex arc edge for tilt lock to bite into the two curved edge portions 56, 56, the telescopic lock uneven portion 48 of the telescopic lock convex arc edge is moved to the inner column. The force required to bite into the upper surface of 14b is small in the initial stage and gradually increases. Such characteristics are preferable in terms of protecting the driver by absorbing impact energy transmitted from the steering wheel 1 to the inner column 14b and the outer column 13b. In other words, the impact applied to the driver's body at the moment of the occurrence of a secondary collision can be kept low, and the force to support the driver's body can be gradually increased to ensure the freedom of tuning to enhance the driver's protection. This is advantageous from the viewpoint of performance.

In the illustrated example, the hook-shaped member and the support shaft are disposed above the outer column, and the telescopic lock concave / convex portion is engaged with the upper surface of the inner column. However, the present invention can also be implemented with respect to a structure in which a position adjusting mechanism is installed below the steering column. In the case of a structure in which the position adjustment mechanism is installed below the steering column, the telescopic lock concave and convex portions and the inner column are placed with the adjustment lever displaced downward so that the position of the steering wheel can be adjusted. It is easy to separate from the mating surface such as the lower surface. However, this separation can be more reliably applied by applying the present invention.
In the case of this example, a structure in which a telescopic mechanism and a hip swing type tilt mechanism are combined is shown. However, when the present invention is implemented, a telescopic mechanism, an outer column, and an inner column are continuously connected. A so-called oscillating tilt mechanism that adjusts the height position of the steering wheel based on the rocking displacement centered on the portion can also be combined.
Regardless of whether it is a hip swing type tilt mechanism or a swing type tilt mechanism, a structure in which a tilt center, that is, a pivot axis for swinging displacement, is provided at the front end of the outer column is adopted. You can also.
Furthermore, the present invention can be carried out with a structure of a telescopic mechanism alone without a tilt mechanism.

DESCRIPTION OF SYMBOLS 1 Steering wheel 2 Steering gear unit 3 Input shaft 4 Tie rod 5, 5a Steering shaft 6, 6a, 6b Steering column 7 Universal joint 8 Intermediate shaft 9 Universal joint 10 Car body 11 Axis 12, 12a, 12b, 12c Support bracket 13, 13a, 13b Outer column 14, 14a, 14b Inner column 15 Outer tube 16 Inner shaft 17 Electric motor 18, 18a Adjusting lever 19, 19a Hook member 20, 20a Cam device 21 Cam member 22 Movable side bracket 23 Eccentric cam 24 Pivoting bracket 25 First half element 26 Second half element 27 Main portion 28 Clamped portion 29 Locking arm portion 30 Discontinuous portion 31 Tension spring 32 Mounting plate portion 33 Support plate portion 34 Sliding plate 35 Long hole 36 Connection plate 37 Through hole 38 Holding plate 39 Nuts 40 Protruding portion 41 Stepped surface 42 Through hole 43 Support shaft 44 Head 45 Nut 46 Telescopic lock eccentric cam 47 Tilt lock eccentric cam 48 Telescopic lock uneven portion 49 Stopper for preventing excessive rotation at the time of collision 50 Telescopic lock biasing Spring 51 Locking concave part 52 Lock release lever 53 Mounting hole 54 Tip part 55 Receiving step surface 56 Curved edge part 57 Tilt lock uneven part 58 Driven arm part 59 Stopper over-rotation preventing stopper 60 Tilt lock engagement / disengagement spring 61 Coil part

Claims (4)

A cylindrical outer column capable of expanding and contracting at least a part of the inner diameter in the axial direction, a cylindrical inner column fitted and supported on the inner diameter side of the outer column so as to be axially displaceable, and the inner column A steering shaft that is rotatably supported on the inner diameter side and that fixes a steering wheel to a rear end protruding rearward from the rear end opening of the inner column, and the inner diameter of the outer column can be enlarged or reduced. A pair of support plate portions provided on the fixed portion with the portion sandwiched from both sides in the width direction, a vehicle body side through hole formed at a position where these support plate portions are aligned with each other, and a part of the outer column In the state where the column side through-hole formed in the portion not interfering with the inner column is inserted in the width direction, the hook-shaped portion for expanding and reducing the interval between the opposing surfaces of the both support plate portions When, in the telescopic steering apparatus having an adjustment lever for scaling this interval with rotation provided at the proximal end of the rod-shaped member,
A support shaft, a telescopic locking eccentric cam, an elastic member, and a lock release lever;
Of these, the support shaft is supported by a part of the outer column in a state of being arranged in parallel with the bowl-shaped member,
The telescopic lock eccentric cam is supported at an intermediate portion of the support shaft so as to be rotatable with respect to the support shaft. Of the telescopic lock eccentric cam, the outer peripheral surface of the inner column or the inner column. The portion facing the surface of the member fixed to the telescopic lock convex arc edge whose distance from the center of the support shaft increases toward the rear, and the telescopic lock convex and concave portions Part is formed,
The elastic member is provided between the telescopic lock eccentric cam and the outer column or a member fixed to the outer column, and the telescopic lock is arranged with respect to the telescopic lock eccentric cam. And has a resilience in a direction in which a front portion of the concave and convex portion is in contact with an outer peripheral surface of the inner column or a surface of a member fixed to the inner column, and the unlocking lever is an intermediate portion of the bowl-shaped member The base end of the steering wheel is supported and rotated together with the hook-shaped member so as to be engaged with and disengaged from the telescopic locking eccentric cam, and the adjustment lever is adjusted from a state in which the position of the steering wheel is fixed. As the telescopic lock eccentric cam is rotated to the state, the front end portion of the telescopic lock uneven portion is separated from the mating portion. Telescopic steering device characterized in that it swings and displaces in the direction.   The front end of the outer column or inner column is supported so as to be able to swing and swing around a pivot arranged parallel to the bowl-shaped member, and the vehicle body side through hole is long in the arc direction around the pivot It is a long hole, the rear end edges of both support plate portions are arc-shaped convex edges centered on this pivot, and a pair of tilt lock eccentric cams at both ends of the support shaft is centered on this support shaft. The tilt lock convex arc in which the distance from the center of the support shaft increases as the portion of the tilt lock eccentric cam facing the convex edge portion moves upward. The tilt lock uneven portion is formed on the convex arc edge for tilt lock, and the tilt lock uneven portion is rotated in a state where the adjustment lever is rotated to adjust the position of the steering wheel. And the convex edge Connecting members are provided in order to, telescopic steering apparatus according to claim 1.   The elastic member is a torsion coil spring in which the coil portion is externally fitted to the intermediate portion of the support shaft, one end portion is locked to the unlocking lever, and the other end portion is locked to the outer column, and the connecting member is the intermediate portion. The telescopic steering device according to claim 2, wherein the torsion coil spring includes a coil portion, and one end portion is engaged with a tilt-lock eccentric cam and the other end portion is engaged with a portion that rotates together with the hook-shaped member.   The telescopic steering device according to any one of claims 1 to 3, wherein a support shaft, a telescopic locking eccentric cam, an elastic member, and a lock release lever are provided above the outer column.

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