JP2006159920A - Steering device with position adjusting function - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To materialize a structure pressing a receiving surface 17a fixed to a steering column 3 by an energizing spring 19 supported to a vehicle body, and capable of decreasing the increasing rate of elastic force of the energizing spring 19 when rocking the steering column downward. <P>SOLUTION: A contact position of the energizing spring 19 to the receiving surface 17a is moved to a rear end side of the steering column 3 by downwardly rocking the steering column 3. The receiving surface 17a is made to be a tilting surface tilting upward at a rate larger than the axis X of the steering column 3, as it goes to the read end side of the steering column 3. In such a structure, the elastic deforming amount of the energizing spring 19 can be suppressed when rocking the steering column 3 downward. Therefore, the above mentioned problem can be solved. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an improvement of a steering device with a position adjusting function that can adjust a height position and the like of a steering wheel for steering an automobile. In particular, the present invention relates to a technique for adjusting the height position with a light force.

  In order to change the height position of a steering wheel according to a driver's physique, a driving posture, etc., a steering device having a position adjusting function has been conventionally used. 8 to 13 show an example of a conventional structure of such a steering apparatus with a position adjusting function. The steering shaft 2 that is rotated by the operation of the steering wheel 1 fixed to the rear end portion (the right end portion of each drawing excluding FIG. 10) is inserted into the steering column 3, and the front end portion of the steering column 3 (see FIG. 10). The left end portion of each figure is supported on the vehicle body so as to be swingable about the horizontal axis 4. On the other hand, the intermediate portion of the steering column 3 supports the vertical position of the pair of fixing brackets 5 and 5 fixed to the vehicle body.

  Each of the fixing brackets 5, 5 is formed by bending a metal plate having sufficient rigidity, and includes a pair of vertical plate portions 6, 6 arranged in parallel to each other. Then, elongated holes 7 and 7 which are arc-shaped around the horizontal axis 4 and which are long in the vertical direction are formed at positions where these vertical plate portions 6 and 6 are aligned with each other. In addition, a substantially U-shaped cross section is formed by bending a metal plate having sufficient rigidity at a portion sandwiched between the pair of vertical plate portions 6 and 6 at an intermediate portion of the steering column 3. The lifting bracket 8 is fixed by welding or the like. The elevating bracket 8 includes a pair of side plate portions 9 and 9 that overlap the vertical plate portions 6 and 6 and are parallel to each other. Further, concentric through holes 10 and 10 are formed in portions of the side plate portions 9 and 9 that are aligned with the long holes 7 and 7, respectively. A tilt bolt 11 is inserted through each of the through holes 10 and 10 and the long holes 7 and 7.

  At the base end portion (left end portion in FIG. 10) of the tilt bolt 11, a head portion 12 for pressing the outer surface of one (left side in FIG. 10) of the vertical plate portion 6 is provided. In the illustrated example, the tilt bolt 11 is prevented from rotating by engaging the engaging portion 13 provided at the end of the head 12 with the elongated hole 7. Further, a tilt nut 14 for pressing the outer surface of the other (right side in FIG. 10) vertical plate 6 is screwed to the tip end (right end in FIG. 10) of the tilt bolt 11, and The base end portion of the tilt lever 15 is coupled and fixed to the tilt nut 14. The tilt nut 14 and the tilt lever 15 and the tilt bolt 11 constitute a switching means.

  The elevating bracket 8 includes a bottom plate portion 16 that connects lower end edges of the side plate portions 9 and 9 to each other. And the width direction (left-right direction of FIG. 10, the up-down direction of FIG. 11) intermediate part of the lower surface of this baseplate part 16 is made into the receiving surface 17 for pressing a part of the urging | biasing spring 19 described below. The receiving surface 17 is a plane perpendicular to the side plate portions 9 and 9 and parallel to the central axis X of the steering column 3 (shown only in FIG. 9). Note that the receiving surface 17 is formed in a plane parallel to the central axis of the steering column 3 in this manner, for example, in various conventional structures in addition to the conventional structure described in Patent Document 1. Further, at both ends in the width direction of the bottom surface of the bottom plate portion 16, recesses 18 and 18 are provided to be recessed upward with respect to the receiving surface 17.

  The urging spring 19 is made of a single wire made of spring steel, and is provided with a pair of coil spring portions 20 and 20 arranged concentrically and spaced apart in the axial direction, and the coil springs. The pressing arm portion 21 provided in a state of extending in a tangential direction from the opposite ends of the portions 20 and 20 and the end portions on the opposite sides of the coil spring portions 20 and 20 in the tangential direction, respectively. And a pair of support arm portions 22 and 22 provided in the state of being. That is, each of the coil spring portions 20 and 20 is formed by spirally winding portions near both ends of the wire, and is arranged concentrically and spaced apart in the axial direction. The pressing arm portion 21 is formed by bending an intermediate portion of the wire rod into a U-shape, and a pair of first straight portions 23 and 23 parallel to each other, and tip portions of the first straight portions 23 and 23 (FIG. 9). , 11, 12, and 13) are connected to each other by a second straight line portion 24. And the base end part (left end part of FIG. 9, 11, 12, 13) of each 1st linear part 23 and 23 of these is connected to the edge part of the mutually opposing side of each said coil spring part 20 and 20, respectively. is doing. Each of the support arm portions 22 and 22 has a distal end portion (upper end portions in FIGS. 9, 10, 12, and 13 and a right end portion in FIG. 11) in a crank shape and the remaining portions by the both end portions of the wire. Each is formed in a straight line. And each base end part (The lower end part of FIG. 9, 10, 12, 13 and the left end part of FIG. 11) is connected with the edge part on the opposite side of each said coil spring part 20,20.

  Such an urging spring 19 has notches formed at the front plate portions 25 and 25 constituting the front end portions of the fixing brackets 5 and 5 as support members at the tip ends of the support arm portions 22 and 22. 26 and the through holes 27 are coupled to the respective fixing brackets 5 and 5 in a state where displacement is prevented. At the same time, by twisting the coil spring portions 20 and 20, the second linear portions 24 constituting the pressing arm portion 21 in a state where the elastic force in the twisting direction is generated by the coil spring portions 20 and 20. The receiving surface 17 is slidably contacted. Accordingly, the receiving surface 17 is pressed by the second linear portion 24 based on the elasticity in the twisting direction. Then, this pressing force (force for swinging the steering column 3 upward about the horizontal axis 4) and gravity (force that also swings downward = moment) are balanced. When the height position of the steering wheel 1 to be described below is adjusted, the force necessary for swinging the steering column 3 about the horizontal axis 4 can be reduced. In addition, in the state where the biasing spring 19 is assembled as described above, the pair of first straight portions 23 and 23 constituting the pressing arm portion 21 are respectively connected to the concave portions 18 and 23 with respect to the width direction of the bottom plate portion 16. 18 is arranged in a portion matching with 18.

  When the height position of the steering wheel 1 is adjusted by the steering device configured as described above according to the physique of the driver, the tilt nut 14 is loosened by operating the tilt lever 15, and this tilt The distance between the nut 14 and the head 12 of the tilt bolt 11 is increased. Thus, the frictional force generated between the inner side surfaces of the vertical plate portions 6 and 6 constituting the pair of fixed brackets 5 and 5 and the outer side surface of the pair of side plate portions 9 and 9 constituting the lifting bracket 8 is reduced. Make it smaller. In this state, the steering column 3 is swung around the horizontal axis 4 (the tilt bolt 11 is moved along the long holes 8 and 8 formed in the vertical plates 6 and 6). The steering wheel 1 is moved to a desired height position. In this case, the upper limit position of the height at which the steering wheel 1 can be moved is the position (FIG. 12) where the tilt bolt 11 reaches the upper end of each of the long holes 8 and 8, and the lower limit position is also the same. The tilt bolt 11 is a position (FIG. 13) that reaches the lower end of each of the long holes 8, 8.

Further, when the steering column 3 is swung as described above, the contact position of the second linear portion 24 constituting the pressing arm portion 21 of the biasing spring 19 with respect to the receiving surface 17 provided on the lower surface of the lifting bracket 8. Moves to the rear end side of the steering column 3 as the steering column 3 is swung downward, and also moves to the front end side of the steering column 3 as it is swung upward. Therefore, the distance L from the front edge of each of the fixed brackets 5 and 5 to the contact position is the smallest (L = L _MIN ) in the upper limit position shown in FIG. {L = L _MAX (> L _MIN )} is the largest in the state. Further, when the steering column 3 is swung downward as described above, the pair of first straight portions 23 and 23 constituting the pressing arm portion 21 of the biasing spring 19 are respectively shown in FIG. Since it enters into the inside of the recessed parts 18 and 18 provided in the width direction both ends of the lower surface of the said raising / lowering bracket 8, it does not interfere with this raising / lowering bracket 8. FIG.

  In any case, if the steering wheel 1 is moved to a desired height position as described above, the tilt nut 14 is tightened by operating the tilt lever 15 as it is, and the head 12 And the distance between the tilt nut 14 is reduced. As a result, the inner side surfaces of the pair of vertical plate portions 6 and 6 are strongly pressed against the outer side surfaces of the side plate portions 9 and 9, and the frictional force generated between these both sides is increased. As a result, the steering wheel 1 can be fixed at the adjusted height position.

  By the way, in the case of the steering device with a position adjusting function as described above, the supporting arm portions 22 and 22 and the pressing arm portions constituting the biasing spring 19 are generated as the steering column 3 is swung downward. The opening angle θ with respect to 21, that is, the elasticity in the torsional direction generated by each of the coil spring portions 20, 20 constituting the biasing spring 19 is increased. When the elasticity in the torsional direction increases as described above, the operation force necessary for lowering the height position of the steering wheel 1 increases accordingly. Therefore, in order to reduce the operating force, it is desirable to reduce the rate of increase in the elasticity when the steering column 3 is swung downward.

  In this case, as a method of reducing the rate of increase in elasticity, a method of reducing the spring coefficient of each of the coil spring portions 20 and 20 can be considered. For this purpose, specifically, a method of increasing the number of windings of the wire constituting each of the coil spring portions 20, 20 and a method of reducing the diameter of the wire are conceivable. However, if the method of increasing the number of turns of the wire is adopted, the axial dimensions of the coil spring portions 20 and 20 are increased, which may not be installed in a narrow space, which is not preferable. Further, if the method of reducing the diameter of the wire rod is adopted, the durability of the coil spring portions 20 and 20 is lowered, which is not preferable.

JP 2004-9796 A

  In view of the circumstances as described above, the steering device with a position adjusting function according to the present invention can increase the rate of increase in elasticity of the urging spring when the steering column is swung downward without causing an increase in size or a decrease in durability. It was invented to realize a structure that can be made smaller.

A steering apparatus with a position adjusting function according to the present invention includes a steering column having a steering shaft for fixing a steering wheel inserted in a rear end portion thereof, a front end portion of which is pivotally supported by a horizontal axis, a fixing bracket fixed to the vehicle body, And a switching means capable of switching between a state in which the middle or rear end of the steering column is fixed to the fixing bracket and a state in which the steering column is not fixed, and an urging spring.
The urging springs of these are in a state of extending radially outward from the virtual cylindrical surface including the outer peripheral surface of the coil spring part from both ends of the coil spring part and the wire constituting the coil spring part. A pair of provided arm portions. Then, by twisting the coil spring portion, the support member (for example, one arm portion of the pair of arm portions fixed to the vehicle body with the coil spring portion generating elasticity in the torsion direction) The other arm is connected to the receiving surface provided on the lower surface of the steering column or a member fixed to the steering column (directly or via a coating or mounting part made of a low friction material) ), Which are in contact with the receiving surface so as to be displaceable in the front-rear direction. As a result, the receiving surface is pressed upward based on the elasticity in the torsional direction, and the contact position of the other arm with respect to the receiving surface swings downward about the horizontal axis. Accordingly, the steering column is moved to one axial end side of the steering column, and is also moved to the other axial end side of the steering column by swinging upward.
In particular, in the steering device with a position adjusting function of the present invention, the swing of the steering column is increased at a rate larger than the central axis of the steering column as the receiving surface is directed to one end side in the axial direction of the steering column. The inclined surface is inclined in the direction toward the upper side of the moving direction.

  In the case of the steering device with a position adjusting function of the present invention configured as described above, the contact position of the other arm portion with respect to the receiving surface causes the steering column to swing downward as in the case of the conventional structure described above. Accordingly, the steering column moves to one end side in the axial direction (in the case of the conventional structure, the rear end side). However, in the case of the conventional structure, the receiving surface is a plane parallel to the central axis of the steering column, whereas in the present invention, the receiving surface is closer to one end side in the axial direction of the steering column. The inclined surface is inclined in a direction upward in the swing direction of the steering column at a rate larger than the central axis of the steering column. For this reason, in the case of the present invention, when the steering column is swung downward, the downward displacement rate of the contact position (the increase rate of the opening angle of the pair of arm portions), that is, the coil spring portion The rate of increase in elasticity in the torsional direction generated in (1) can be reduced as compared with the conventional structure. Therefore, in the case of the present invention, when the height position of the steering wheel is adjusted, the operating force required to swing the steering column downward can be reduced. In the case of the present invention, it is not necessary to increase the number of windings of the wire constituting the coil spring portion, so that the size is not increased, and further, the diameter of the wire constituting the coil spring portion needs to be reduced. Because there is no, durability does not decrease.

  According to the second aspect of the present invention, one end side in the axial direction of the steering column is the rear end side, and the other end side in the axial direction is also the front end side. The structure in which the length of the steering column can be expanded and contracted with reference to the position of the horizontal axis in a state where the intermediate part or the rear end part of the steering wheel is not fixed (the front and rear position of the steering wheel can be changed) (Structure). In this case, preferably, as described in claim 2, as the contact position of the other arm portion with respect to the receiving surface increases the length of the steering column on the basis of the position of the horizontal axis, As the length of the steering column is shortened on the front end side of the column with reference to the position of the horizontal axis, the column is moved to the rear end side of the steering column.

  In the case of adopting such a configuration, when the length of the steering column is extended with reference to the position of the horizontal axis, the action of gravity tries to swing the steering column downward about the horizontal axis. growing. However, at the same time, since the contact position of the other arm portion with respect to the receiving surface moves to the front end side, the contact position is displaced downward, and the elasticity in the torsional direction generated by the coil spring portion is increased. Therefore, even when the length of the steering column is increased, the force by which the biasing spring presses the receiving surface and the gravity can be kept in balance (or the balance deviation can be suppressed to a slight extent). Further, when the length of the steering column is shortened with reference to the position of the horizontal axis, the action of gravity, which tries to swing the steering column downward about the horizontal axis, is reduced. However, at the same time, since the contact position of the other arm portion with respect to the receiving surface moves to the rear end side, the contact position is displaced upward, and the elasticity in the torsional direction generated by the coil spring portion is reduced. . Therefore, even when the length of the steering column is shortened, the force by which the urging spring presses the receiving surface and the gravity can be kept in balance (or balance deviation can be suppressed to a small extent).

  The present invention can also be applied to a structure in which an auxiliary power device for an electric power steering device is supported on a portion of the steering column closer to the rear side than the horizontal axis, as described in claim 3. .

  1 to 3 show a first embodiment of the present invention corresponding to claim 1. The feature of this embodiment is that the shape of the receiving surface 17a provided on the lower surface of the lifting bracket 8a is devised. The structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. For this reason, the same parts are denoted by the same reference numerals, overlapping illustrations and descriptions are omitted or simplified, and the following description will focus on the characteristic parts of the present embodiment.

  In the case of this embodiment, the distance from the central axis X (shown only in FIG. 1) of the steering column 3 toward the rear end side of the steering column 3 (right side in FIGS. 1 to 3) is increased. At a large rate, the steering column 3 is inclined so as to incline in a direction toward the upper side of the swinging direction (a direction in FIG. 1).

Also in the case of the steering apparatus with a position adjusting function of the present embodiment configured as described above, the contact position of the second linear portion 24 of the biasing spring 19 with respect to the receiving surface 17a is the same as in the case of the conventional structure described above. As the steering column 3 is swung downward (in the direction B in FIG. 1), the steering column 3 moves to the rear end side. Therefore, also in this embodiment, the distance L from the front end edge of each fixed bracket 5 to the contact position is the smallest when the steering column 3 is swung to the upper limit position as shown in FIG. = L _MIN ), and becomes the largest {L = L _MAX (> L _MIN )} when the steering column 3 is swung to the lower limit position as shown in FIG.

However, in the case of the conventional structure, the receiving surface 17 (see FIG. 9) is a plane parallel to the central axis X of the steering column 3, whereas in the present embodiment, the receiving surface 17a is The inclined surface is inclined in a direction toward the upper side of the swinging direction of the steering column 3 at a rate larger than the central axis X toward the rear end side of the steering column 3. For this reason, in the case of the present embodiment, the rate of displacement of the contact position downward when the steering column 3 is swung downward, that is, the support arm portions 22 constituting the biasing spring 19. , 22 and the pressing arm portion 21 can be increased by a smaller increase rate than the conventional structure. For example, the opening angle θ in the state in which the steering column 3 is swung to the upper limit position (the state of FIG. 2 in the present embodiment and the state of FIG. 12 in the conventional structure) is the case of the present embodiment (θ = α ) And the conventional structure (θ = α) even when they are equal to each other, the steering column 3 is swung to the lower limit position (the state shown in FIG. 3 in the present embodiment, and the conventional structure shown in FIG. 13). The opening angle θ in the state) is smaller (β ₂ <β ₁ ) in the case of the present embodiment (θ = β ₂ ) than in the conventional structure (θ = β ₁ ).

  In any case, in the case of the present embodiment, the increase rate of the opening angle θ when the steering column 3 is swung downward can be reduced as compared with the conventional structure. The rate of increase in elasticity in the torsional direction generated by the coil spring portions 20 and 20 constituting the spring 19 can also be reduced. Therefore, in the case of the present embodiment, when adjusting the height position of the steering wheel 1 (see FIG. 8), the operation force required to swing the steering column 3 downward can be reduced. In the case of the present embodiment, since it is not necessary to increase the number of windings of the wire constituting each coil spring part 20, 20, the coil spring part 20, 20 is not increased in size. Since there is no need to reduce the diameter of the constituent wire, the durability does not decrease.

  When the structure of this embodiment as described above is implemented, the inclination angle γ of the receiving surface 17a with respect to the central axis X of the steering column 3 is determined by each member constituting the steering device (for example, the horizontal shaft 4, According to the relative position of the lifting bracket 8 and the biasing spring 19 and the like, it is determined as appropriate (in the range of 0 ° <γ <90 °, more preferably in the range of 10 to 20 °). So that the effect of can be obtained accurately.

  Next, FIG. 4 shows Embodiment 2 of the present invention, which also corresponds to claim 1. In the case of the first embodiment described above, the urging spring 19 is supported on the front end portion of each fixing bracket 5, whereas in the case of this embodiment, the urging spring 19 is attached to the rear of each fixing bracket 5. It is supported at the end. In the present embodiment in which the support position of the urging spring 19 with respect to each fixed bracket 5 is changed in this way, the second linear portion 24 of the urging spring 19 with respect to the receiving surface 17a is the same as in the case of the first embodiment described above. Is moved to the rear end side of the steering column 3 as the steering column 3 is swung downward. Accordingly, in the present embodiment also, in order to swing the steering column 3 downward when adjusting the height position of the steering wheel 1 (see FIG. 8) on the same principle as in the first embodiment described above. Necessary operating force can be reduced. Since the structure and operation of the other parts are the same as those in the case of the above-described first embodiment, the same parts are denoted by the same reference numerals, and redundant description is omitted.

  Next, FIGS. 5-6 has shown Example 3 of this invention corresponding to Claims 1-3. In the case of the present embodiment, the steering shaft 2 and the steering column 3 can be expanded and contracted in the axial direction with reference to the position of the horizontal axis 4. For this purpose, the steering shaft 2 has a front end side inner shaft 28 and a rear end side outer shaft 29, and the steering column 3 has a front end side inner column 30 and a rear end side outer column 31 respectively. It is configured by combining in scope form. Further, in the pair of left and right side plate portions 6 constituting the lifting bracket 8b fixed to the intermediate portion of the outer column 31, second elongated holes 32 that are long in the axial direction of the steering column 3 are respectively aligned with the mutually aligned portions. Is forming. Then, the flange portion of the tilt bolt 11 is inserted into each of the second long holes 32.

  By adopting such a configuration, in the case of the present embodiment, not only the height position of the steering wheel 1 but also the front-rear position can be adjusted according to the physique of the driver. That is, in the case of the present embodiment, as in the case of adjusting the height position, the steering shaft 2 and the steering shaft 2 and the brackets 8b with the lift bracket 8b fixed to the pair of fixed brackets 5 by the tilt lever 15 are released. The front-rear position can be adjusted by extending or retracting the steering column 3 (moving the tilt bolt 11 along the second elongated holes 32). When the steering column 3 is expanded and contracted as described above, the elevating bracket 8b fixed to the outer column 31 moves in the axial direction of the steering column 3 with respect to the urging spring 19 supported by the fixed bracket 5. (Rearward when stretched, forward when contracted). As a result, the contact position of the second linear portion 24 constituting the biasing spring 19 with respect to the receiving surface 17a provided on the lower surface of the elevating bracket 8b is contracted forward as the steering column is extended. Each move backwards as things happen.

  In this embodiment, when the steering shaft 2 and the steering column 3 are extended as described above (the distance from the horizontal shaft 4 to the steering wheel 1 is increased), the steering column 3 is moved to the horizontal shaft 4. The action (moment) of gravity that attempts to swing downward about the center increases. However, at the same time, since the contact position of the second linear portion 24 with respect to the receiving surface 17a moves to the front end side, the contact position is displaced downward, and the coil spring portion 20 constituting the biasing spring 19 is formed. , 20 increases the elasticity in the torsional direction. Therefore, even when the steering shaft 2 and the steering column 3 are extended, the force by which the urging spring 19 presses the receiving surface 17a and the gravity are kept in balance (or the deviation of the balance is slightly reduced). Can be suppressed). Further, when the steering shaft 2 and the steering column 3 are contracted (the distance from the horizontal shaft 4 to the steering wheel 1 is shortened), the steering column 3 is swung downward about the horizontal shaft 4. The action (moment) of gravity becomes smaller. However, at the same time, the contact position of the second linear portion 24 with respect to the receiving surface 17a moves to the rear end side, so that the contact position is displaced upward and is generated by the coil spring portions 20, 20. The elasticity in the torsional direction is reduced. Therefore, even when the steering shaft 2 and the steering column 3 are contracted, the force by which the urging spring 19 presses the receiving surface 17a and the gravity can be kept in balance (or a slight deviation in balance). Can be suppressed).

  In the case of this embodiment, the auxiliary power device 33 of the electric power steering device is supported at the front end portion of the steering column 3 on the rear end side of the horizontal axis. Therefore, in the case of the present embodiment, the steering column 3 is lowered about the horizontal axis 4 as much as the auxiliary power device 33 is supported as compared with the structure in which the auxiliary power device 33 is not supported. The action (moment) of gravity that attempts to swing is increased. Accordingly, in the case of this embodiment, the balance between these two forces can be maintained by increasing the initial set value of the elasticity of the biasing spring 19 by the amount of the action of gravity. ing. In the case of this embodiment as well, the support position of the urging spring 19 with respect to each of the fixed brackets 5 can be the rear end portion instead of the illustrated front end portion. The structure and operation of the other parts are the same as those in the first embodiment shown in FIGS.

  In each of the above-described embodiments, a configuration is adopted in which the other arm portion that constitutes the biasing spring that is the metal member is brought into direct contact with the receiving surface that is the metal surface. However, when carrying out the present invention, in order to reduce the sliding resistance of the contact portion between the receiving surface and the other arm portion, at least one of the receiving surface and the surface of the other arm portion is provided. The low friction material can be coated, or the other arm can be brought into contact with the receiving surface via a sliding part or a rolling part such as a synthetic resin attached to the other arm.

  Moreover, in each Example mentioned above, the single inclined surface was employ | adopted as a receiving surface. However, when the present invention is implemented, for example, a receiving surface 17b whose inclination angle changes in multiple steps as shown in FIG. 7A or a curved surface receiving device as shown in FIG. The surface 17c can also be adopted.

  In each of the above-described embodiments, the lower surface of a member (the bottom plate portion 16 constituting the lifting brackets 8a and 8b) provided below the steering column is used as a receiving surface. However, when the present invention is implemented, the lower surface of a member provided on the side or upper side of the steering column can be used as a receiving surface. The receiving surface can also be provided directly on the lower surface of the steering column. In this case, for example, the receiving surface is formed by bulging a portion of the steering column where the receiving surface is to be formed by hydroforming.

FIG. 9 is an enlarged view corresponding to a portion B in FIG. 8, showing the first embodiment of the present invention in a state where the swing angle of the steering column is adjusted to the intermediate position. FIG. 2 is a view similar to FIG. 1, showing a state in which the swing angle of the steering column is adjusted to the upper limit position. The figure similar to FIG. 1 shown in the state corresponding to the lower limit position. The figure similar to FIG. 1 which shows Example 2 of this invention. The schematic side view which shows the steering apparatus with a position adjustment function which shows the same Example 3. FIG. FIG. 6 is an enlarged view of a portion A in FIG. 5, showing a state in which the swing angle of the steering column is adjusted to an intermediate position. The partial schematic side view which shows two examples of another shape of the receiving surface which can be employ | adopted when implementing this invention. The schematic side view which shows the steering apparatus with a position adjustment function known conventionally. The B section enlarged view of FIG. 8 shown in the state which match | combined the rocking | fluctuation angle of the steering column with the intermediate position. CC sectional drawing of FIG. D arrow line view of FIG. FIG. 12 is a view similar to FIG. 11, showing the swing angle of the steering column adjusted to the upper limit position. FIG. 12 is a view similar to FIG. 11, similarly showing the lower limit position.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Steering wheel 2 Steering shaft 3 Steering column 4 Horizontal axis 5 Fixed bracket 6 Vertical plate part 7 Long hole 8, 8a, 8b Lifting bracket 9 Side plate part 10 Through-hole 11 Tilt bolt 12 Head part 13 Engagement part 14 Tilt nut 15 Tilt Lever 16 Bottom plate portion 17, 17a, 17b, 17c Receiving surface 18 Recess 19 Biasing spring 20 Coil spring portion 21 Pressing arm portion 22 Support arm portion 23 First straight portion 24 Second straight portion 25 Front plate portion 26 Notch 27 Through hole 28 Inner shaft 29 Outer shaft 30 Inner column 31 Outer column 32 Second long hole 33 Auxiliary power unit

Claims (3)

  A steering shaft for fixing the steering wheel is inserted into the rear end portion, a steering column whose front end portion is pivotally supported by a horizontal axis with respect to the vehicle body, a fixed bracket fixed to the vehicle body, and an intermediate portion of the steering column with respect to the fixed bracket. A switching means capable of switching between a state in which the portion or the rear end portion is fixed and a state in which the rear end portion is not fixed, and an urging spring, and the urging spring includes a coil spring portion and both ends of the wire constituting the coil spring portion. A pair of arms provided in a state of extending radially outward from the virtual cylindrical surface including the outer peripheral surface of the coil spring portion from the portion, and twisting the coil spring portion to In a state where the elastic force in the torsional direction is generated by the spring portion, one arm portion of the pair of arm portions is coupled to a support member fixed to the vehicle body, and the other arm portion is coupled to the step. By making the receiving surface provided on the lower surface of the ring column or the member fixed to the steering column so as to be displaceable in the front-rear direction along the receiving surface, the receiving surface is moved upward based on the elasticity in the torsional direction. The contact position of the other arm portion with respect to the receiving surface is pressed to one end side in the axial direction of the steering column as the steering column is swung downward about the horizontal axis. In the steering device with a position adjusting function that moves to the other axial end of the steering column in accordance with the swing, the receiving surface is directed toward one axial end of the steering column, It is characterized by an inclined surface that inclines in a direction toward the upper direction of swinging of the steering column at a rate larger than the central axis of the steering column. That position adjustable steering device.   One end of the steering column in the axial direction is the rear end side, and the other end in the axial direction is also the front end side, and the switching means switches the state where the intermediate or rear end of the steering column is not fixed to the fixed bracket. In this state, the length of the steering column can be expanded and contracted with respect to the position of the horizontal axis, and the contact position of the other arm portion with respect to the receiving surface is determined with reference to the position of the horizontal axis. As the column length increases, it moves to the front end side of the steering column and to the rear end side of the steering column as the length of the steering column is reduced with reference to the position of the horizontal axis. The steering apparatus with a position adjusting function according to claim 1.   The steering device with a position adjusting function according to any one of claims 1 to 2, wherein an auxiliary power device for an electric power steering device is supported in a portion of the steering column closer to the rear side than the horizontal axis. .

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