JP2017081516A - Steering device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a steering device which inhibits a steering column from being fallen by malfunction and protects a separation mechanism during telescopic adjustment.SOLUTION: A steering device includes an inner column having a first hole, an outer column, an outer column bracket, an inner column bracket, shear pins, a first damper, and a second damper. The outer column has a slit formed by cutting one end. The outer column bracket tightens the outer column with a telescopic friction plate. The inner column bracket is supported by the telescopic friction plate, has a second hole opened therein, and is removably connected to the inner column by the shear pins disposed over the first hole and the second hole. The first damper is attached to an end part inner wall that is an inner wall of an end part of the slit. The second damper is attached to the inner column bracket and faces the first damper.SELECTED DRAWING: Figure 13

Description

  The present invention relates to a steering device.

  A technique using a capsule is widely known as a support structure of a steering device that gives a steering angle to a wheel as the steering wheel rotates. For example, in Patent Document 1, when an excessive load is applied to a steering column attached to a vehicle body via a capsule and the steering column is pushed forward of the vehicle body, a part of the capsule is cut so that the steering column is moved forward of the vehicle body. The technique is described in which the driver (operator) is protected from pushing up the steering wheel (secondary collision).

JP 2007-69800 A

  When the steering column is attached to the vehicle body via a capsule as in the technique described in Patent Document 1, the steering column falls when the capsule is cut. For this reason, when the set value of the separation load at which the steering column moves to the front of the vehicle body is lowered in order to further protect the operator who is light in weight from the secondary collision, the steering column is likely to fall due to a malfunction. If the steering column falls due to a malfunction, it becomes difficult to perform the steering operation thereafter. For this reason, it has been difficult to lower the set value of the separation load.

  Further, in the steering device in which the telescopic position can be adjusted, when the tightening rod comes into contact with the end of the telescopic adjustment long groove, the force applied during the telescopic adjustment may be transmitted to the capsule. For this reason, if the telescopic position is adjusted with an excessive force, the capsule may be cut.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a steering device that can suppress a drop of a steering column due to a malfunction and can protect a separation mechanism during telescopic adjustment.

  In order to achieve the above object, a steering device according to the present invention rotatably supports an input shaft connected to a steering wheel, and has a cylindrical inner column having a first hole, and at least the inner column. A cylindrical part is inserted into the inner side, and is an outer column having a slit cut out at one end on the insertion side of the inner column, and is fixed to a vehicle body side member, supports the outer column, and is a plate material An outer column bracket for fastening the outer column together with the telescopic friction plate, an inner column bracket supported by the telescopic friction plate and having a second hole, and a position straddling the first hole and the second hole. A shear pin that removably connects the inner column and the inner column bracket, and an inner end of the slit. A first damper mounted on the end inner wall is the attached to the inner column bracket, characterized in that it comprises a second damper facing the first damper.

  Thereby, the load applied to the steering wheel at the time of the secondary collision is transmitted to the inner column via the input shaft, thereby moving the inner column forward. On the other hand, the inner column bracket supported by the first telescopic friction plate does not move. For this reason, since a shear force is applied to the shear pin, if the load exceeds the allowable shear force of the shear pin, the shear pin is cut. When the share pin is cut, the connection between the inner column and the inner column bracket is released. As a result, the inner column is supported in the axial direction by the frictional force generated between the inner column and the outer column. For this reason, the inner column can be moved forward of the vehicle body. Even if the shear pin is cut, the outer column remains supported by the outer column bracket fixed to the vehicle body side member. Moreover, the inner column remains supported by the outer column. For this reason, even if the shear pin is cut, the steering column does not fall. Furthermore, when the telescopic position is adjusted, the second damper comes into contact with the first damper when the telescopic position becomes the foremost position. Thereby, a part of the load applied to the inner column is consumed for the deformation of the first damper and the second damper. For this reason, the peak of the shearing force acting on the shear pin when adjusting the telescopic position is less likely to exceed the allowable shearing force of the shear pin. Therefore, the steering device can suppress the dropping of the steering column due to a malfunction, and can protect the separation mechanism at the time of telescopic adjustment.

  As a preferred aspect of the present invention, the first damper includes a flat surface facing the second damper, the second damper includes a plurality of protrusions facing the flat surface, and the Young's modulus of the second damper. Is preferably larger than the Young's modulus of the first damper.

  Thereby, since there is a gap between adjacent protrusions, the flat surface is deformed so as to enter the gap. For this reason, the first damper is easily deformed as compared with a case where the first damper is simply compressed in the axial direction. Therefore, since the peak of the shearing force acting on the shear pin at the time of adjusting the telescopic position tends to be small, the shear pin is more difficult to cut.

  As a desirable mode of the present invention, it is preferable that the inner column bracket includes a through hole penetrating in a radial direction of the inner column, and the second damper includes a retaining portion penetrating the through hole.

  Thereby, the direction of the force applied to the second damper during the telescopic adjustment is different from the direction in which the second damper is prevented from coming off from the inner column bracket. For this reason, even when a force is repeatedly applied to the second damper, the retaining portion is unlikely to be worn, so the retaining portion is unlikely to fall off the inner column bracket. Therefore, the second damper is prevented from falling off from the inner column bracket.

  As a desirable aspect of the present invention, the inner column bracket is disposed on the vehicle body lower side with respect to the inner column, and includes a damper holding portion that is a surface facing the inner column, and the second damper includes the second damper, It is preferable that it is attached to the damper holding part.

  Thereby, since the second damper is housed in the damper holding portion, the size of the device in which the inner column bracket and the second damper are integrated is reduced. Further, since the second damper is placed above the inner column bracket, the second damper is prevented from falling off from the inner column bracket.

  As a desirable mode of the present invention, it is preferable that the first damper and the second damper are synthetic rubber.

  Since synthetic rubber is a highly elastic material, the elastic limit of the first damper and the second damper is increased. For this reason, even when a repeated force is applied to the first damper and the second damper, plastic deformation hardly occurs in the first damper and the second damper. Therefore, the forefront position of the telescopic is prevented from deviating from a predetermined position due to plastic deformation of the first damper and the second damper.

  ADVANTAGE OF THE INVENTION According to this invention, the steering apparatus which can suppress the fall of the steering column by malfunctioning and can protect a detachment mechanism at the time of telescopic adjustment can be provided.

FIG. 1 is a diagram schematically illustrating the periphery of the steering device according to the present embodiment. FIG. 2 is a side view of the steering device according to the present embodiment. FIG. 3 is a plan view of the steering apparatus according to the present embodiment. FIG. 4 is a bottom view of the steering apparatus according to the present embodiment. FIG. 5 is a perspective view of the steering device according to the present embodiment as viewed from above the vehicle body. FIG. 6 is a perspective view of the steering device according to the present embodiment as viewed from the vehicle body lower side. FIG. 7 is a perspective view of the steering device according to the present embodiment as viewed from the lower side of the vehicle body. 8 is a cross-sectional view taken along line AA in FIG. 9 is a cross-sectional view taken along the line BB in FIG. FIG. 10 is an enlarged view of the periphery of the stopper in FIG. 11 is a cross-sectional view taken along the line CC in FIG. 12 is a cross-sectional view taken along the line DD in FIG. FIG. 13 is an enlarged view of the periphery of the inner column bracket in FIG. FIG. 14 is an enlarged view of the periphery of the shear pin in FIG. FIG. 15 is a diagram for explaining the state of the shear pin after being cut. FIG. 16 is a graph showing the relationship between the amount of displacement of the steering column and the load required to move the steering column for the comparative example. FIG. 17 is a diagram illustrating the relationship between the amount of displacement of the steering column and the load necessary to move the steering column in the present embodiment. FIG. 18 is a perspective view of the first damper according to the present embodiment. FIG. 19 is a side view of the second damper according to the present embodiment. FIG. 20 is a perspective view of the second damper according to the present embodiment. FIG. 21 is a perspective view of the second damper according to the present embodiment. FIG. 22 is a diagram illustrating a state in which the inner column bracket is in contact with the damper in the comparative example. FIG. 23 is a graph showing the relationship between the position of the inner column and the shearing force applied to the shear pin for the comparative example. FIG. 24 is a diagram illustrating a state in which the second damper is in contact with the first damper in the present embodiment. FIG. 25 is a graph showing the relationship between the position of the inner column and the shearing force applied to the shear pin for this embodiment.

  DESCRIPTION OF EMBODIMENTS Embodiments (embodiments) for carrying out the present invention will be described in detail with reference to the drawings. The present invention is not limited by the contents described in the following embodiments. The constituent elements described below include those that can be easily assumed by those skilled in the art and those that are substantially the same. Furthermore, the constituent elements described below can be appropriately combined.

(Embodiment)
FIG. 1 is a diagram schematically illustrating the periphery of the steering device according to the present embodiment. FIG. 2 is a side view of the steering device according to the present embodiment. FIG. 3 is a plan view of the steering apparatus according to the present embodiment. FIG. 4 is a bottom view of the steering apparatus according to the present embodiment. FIG. 5 is a perspective view of the steering device according to the present embodiment as viewed from above the vehicle body. FIG. 6 is a perspective view of the steering device according to the present embodiment as viewed from the vehicle body lower side. FIG. 7 is a perspective view of the steering device according to the present embodiment as viewed from the lower side of the vehicle body. In the following description, the front of the vehicle body VB when the steering device 100 is attached to the vehicle body VB is simply described as the front, and the rear of the vehicle body VB when the steering device 100 is attached to the vehicle body VB is simply described as the rear. The Further, the upper side of the vehicle body VB when the steering device 100 is attached to the vehicle body VB is simply described as the upper side, and the lower side of the vehicle body VB when the steering device 100 is attached to the vehicle body VB is simply described as the lower side. 2, the left side in the figure is the front, the right side in the figure is the rear, the upper side in the figure is the upper side, and the lower side in the figure is the lower side.

(Steering device)
The steering device 100 includes a steering wheel 14, a steering shaft 15, a universal joint 16, a lower shaft 17, and a universal joint 18 in the order in which a force given by an operator is transmitted, and is joined to the pinion shaft 19. ing.

  The steering shaft 15 includes an input shaft 151 and an output shaft 152. The input shaft 151 has one end connected to the steering wheel 14 and the other end connected to the output shaft 152. For example, the surface of the input shaft 151 is coated with a resin. Thereby, the input shaft 151 is connected to the output shaft 152 through the resin. The output shaft 152 has one end connected to the input shaft 151 and the other end connected to the universal joint 16. In the present embodiment, the input shaft 151 and the output shaft 152 are formed of a general steel material such as a carbon steel for machine structure (so-called SC material) or a carbon steel pipe for machine structure (so-called STKM material).

  The lower shaft 17 has one end connected to the universal joint 16 and the other end connected to the universal joint 18. One end of the pinion shaft 19 is connected to the universal joint 18.

  In addition, the steering device 100 includes a cylindrical inner column 51 that supports the input shaft 151 so as to be rotatable about the rotation center axis Zr, and a cylindrical outer column 54 into which at least a part of the inner column 51 is inserted. And a steering column 5 including The inner column 51 is disposed behind the outer column 54. In the following description, a direction parallel to the rotation center axis Zr is simply referred to as an axial direction.

  The steering apparatus 100 includes an outer column bracket 52 that is fixed to the vehicle body side member 13 and supports the outer column 54. The outer column bracket 52 includes a mounting plate portion 522 that is fixed to the vehicle body side member 13 and a frame-shaped support portion 521 that is integrally formed with the mounting plate portion 522. The mounting plate portion 522 of the outer column bracket 52 has a mounting hole 522h as shown in FIG. 3, and is fixed to the vehicle body side member 13 using a mounting member such as the mounting hole 522h and a bolt. The frame-shaped support portions 521 of the outer column bracket 52 are disposed on both sides of the outer column 54 and tighten the outer column 54. Further, the frame-like support portion 521 is provided with a tilt adjustment hole 521h that is a long hole that is long in the vertical direction.

  The outer column 54 has a pivot bracket 55 at the front end. The pivot bracket 55 is supported by the vehicle body side member 12 so as to be rotatable about the rotation shaft 551. The rotation shaft 551 is parallel to the horizontal direction, for example. Thus, the outer column 54 is supported so as to be swingable in the vertical direction.

  8 is a cross-sectional view taken along line AA in FIG. As shown in FIG. 8, the outer column 54 has two rod penetrating portions 31, a first slit 541, and a second slit 542. The rod penetration part 31 is a part which protrudes downward from the outer wall of the inner column 51, for example, and has a rod penetration hole 31h which is a round hole. The rod through holes 31h of the two rod penetrating parts 31 are opposed to each other with the first slit 541 interposed therebetween. A part of the rod penetrating part 31 faces the frame-like support part 521. The rod 33 passes through the two rod through-holes 31 h and passes through the tilt adjustment hole 521 h of the frame-shaped support portion 521, and is connected to the operation lever 53.

  The first slit 541 is a long hole in which one end of the outer column 54 on the insertion side of the inner column 51 is cut out. The first slit 541 is provided at a position between the two rod penetrating portions 31. Since the outer column 54 has the first slit 541, the inner diameter decreases when tightened. Thus, in a state where the outer column 54 is tightened, the inner wall of the outer column 54 and the outer wall of the inner column 51 are in contact with each other in a portion where the outer column 54 covers the inner column 51. For this reason, a frictional force is generated between the outer column 54 and the inner column 51. For example, in this embodiment, the outer wall of the inner column 51 is coated with a low friction material for reducing friction with the outer column 54.

  As shown in FIG. 8, the steering device 100 includes a first telescopic friction plate 21 and a second telescopic friction plate 22 in order to strengthen the tightening holding force with respect to the steering column 5. The first telescopic friction plate 21 is a plate-like member having a telescopic adjustment hole 21h which is a long hole whose longitudinal direction is the axial direction. For example, the first telescopic friction plates 21 are arranged so as to overlap each other at a position between the frame-like support portion 521 and the rod penetration portion 31. The second telescopic friction plate 22 is a member formed by bending a plate material, for example, and has a substantially U shape when viewed from the rotation center axis Zr direction. The second telescopic friction plate 22 includes two friction portions 221 disposed between the two first telescopic friction plates 21, a connecting portion 222 that connects the two friction portions 221, and a bent portion provided in the connecting portion 222. 223.

  The friction part 221 has a rod through hole 22h which is a round hole. The rod 33 passes through the telescopic adjustment hole 21h and the rod through hole 22h. Since the connecting portion 222 connects and integrates the two friction portions 221, the operation of disposing the friction portion 221 between the two first telescopic friction plates 21 is facilitated. Further, the connecting portion 222 has the bent portion 223, so that the bent state can be maintained. Thereby, even if the fastening state of the outer column bracket 52 changes and the distance between the two friction parts 221 changes, the connecting part 222 is difficult to pull the friction part 221. For this reason, when the friction part 221 is pulled by the connection part 222, possibility that a clearance gap will arise between the friction part 221 and the 1st telescopic friction board 21 is suppressed.

  When the frame-shaped support portion 521 is tightened, the friction portions 221 of the first telescopic friction plate 21 and the second telescopic friction plate 22 are pressed against the rod penetration portion 31 of the outer column 54 by the frame-shaped support portion 521. Thereby, between the frame-shaped support part 521 and the 1st telescopic friction board 21, between the 1st telescopic friction board 21 and the friction part 221 of the 2nd telescopic friction board 22, the 1st telescopic friction board 21 and the rod penetration part. A frictional force is generated between each of them. For this reason, compared with the case where there is no 1st telescopic friction board 21 and the 2nd telescopic friction board 22, the surface which produces a frictional force increases. The frame-shaped support portion 521 can tighten the outer column 54 more firmly by the first telescopic friction plate 21 and the second telescopic friction plate 22.

  When the operation lever 53 is rotated, the tightening force with respect to the frame-shaped support portion 521 is loosened, and the frictional force between the frame-shaped support portion 521 and the outer column 54 is eliminated or reduced. Thereby, the tilt position of the outer column 54 can be adjusted. In the present embodiment, the steering device 100 includes a first spring 56 and a second spring 57 as shown in FIG. The first spring 56 and the second spring 57 are, for example, coil springs. One end of the first spring 56 is attached to the attachment plate portion 522, and the other end of the first spring 56 is attached to the outer column 54. The first spring 56 assists the vertical movement of the steering column 5 during tilt adjustment, and suppresses the falling of the steering column 5. One end of the second spring 57 is attached to the attachment plate portion 522, and the other end of the second spring 57 is attached to the operation lever 53. The second spring 57 applies a preload to the rod 33 via the operation lever 53. Specifically, the second spring 57 applies a preload to the rod 33 in a direction intersecting the longitudinal direction of the tilt adjustment hole 521h. Thereby, rattling of the rod 33 during tilt adjustment is suppressed.

  When the operation lever 53 is rotated, the tightening force on the frame-like support portion 521 is loosened, and the width of the first slit 541 of the outer column 54 is increased. Thereby, since the force with which the outer column 54 tightens the inner column 51 is eliminated, the frictional force when the inner column 51 slides is eliminated. Thus, the operator can adjust the telescopic position by pushing and pulling the inner column 51 through the steering wheel 14 after rotating the operation lever 53.

  Note that the first telescopic friction plate 21 does not necessarily have to be disposed at a position between the frame-shaped support portion 521 and the rod penetration portion 31. For example, the first telescopic friction plate 21 may be disposed outside the frame-shaped support portion 521, that is, may be disposed on the opposite side of the rod penetrating portion 31 across the frame-shaped support portion 521.

  The member for strengthening the tightening holding force with respect to the steering column 5 is not necessarily the telescopic friction plate (the first telescopic friction plate 21 and the second telescopic friction plate 22). For example, known means such as a gear meshing type may be used.

  9 is a cross-sectional view taken along the line BB in FIG. FIG. 10 is an enlarged view of the periphery of the stopper in FIG. As shown in FIGS. 9 and 10, the steering device 100 includes a stopper 7. The stopper 7 is attached to a position exposed in the second slit 542 in the inner column 51.

  The stopper 7 includes, for example, a bolt 71, a contact plate 72, a washer 73, a spacer 74, and an energization plate 75. The contact plate 72 is a metal plate-like member having a cylindrical protrusion. A cylindrical protrusion of the contact plate 72 is fitted from the inner side of the inner column 51 into a through hole provided at a position exposed in the second slit 542 of the inner column 51. The contact plate 72 has a female screw on the inner wall of the cylindrical protrusion. The bolt 71 is fastened to the female screw of the contact plate 72. The washer 73 is disposed between the bolt head of the bolt 71 and the contact plate 72. The bottom surface of the washer 73 has a shape that follows the shape of the outer wall of the inner column 51. Thereby, the posture of the bolt 71 is stabilized. The spacer 74 is a member for filling a gap between the inner wall of the second slit 542 and the bolt 71 and a gap between the inner wall of the second slit 542 and the contact plate 72. The spacer 74 is a resin member provided with a through hole, for example. The bolt 71 and the contact plate 72 are disposed inside the through hole of the spacer 74. The energization plate 75 is, for example, a metal plate member. The energization plate 75 is fixed by being sandwiched between the head of the bolt 71 and the spacer 74, for example, and is in contact with the outer column 54. Thereby, the inner column 51 is in an energized state with the outer column 54 via the contact plate 72, the bolt 71, and the energizing plate 75. In the present embodiment, for example, when body grounding is performed for a horn, it is necessary to flow electricity from the input shaft 151 to the vehicle body VB side. However, since the input shaft 151 is connected to the output shaft 152 through the resin coating, electricity does not flow from the input shaft 151 to the output shaft 152. In addition, since the outer wall of the inner column 51 is coated with a low friction material, electricity does not flow from the outer wall of the inner column 51 to the outer column 54. Therefore, in the present embodiment, the stopper 7 has a function of flowing the electricity transmitted from the input shaft 151 to the inner column 51 to the outer column 54.

  The stopper 7 is attached to the inner column 51 and can slide while facing the inner wall of the second slit 542 when telescopic adjustment is performed. Since the spacer 74 is made of resin, the stopper 7 slides smoothly with respect to the second slit 542. The stopper 7 is in contact with the second end inner wall 542e that is the rear side end of the second slit 542 when adjusting the telescopic position, thereby restricting the adjustment range of the telescopic position. In addition, since the spacer 74 is in contact with the inner wall of the second slit 542, the stopper 7 suppresses the rotation of the inner column 51 around the rotation center axis Zr.

  11 is a cross-sectional view taken along the line CC in FIG. 12 is a cross-sectional view taken along the line DD in FIG. FIG. 13 is an enlarged view of the periphery of the inner column bracket in FIG. The steering device 100 includes an inner column bracket 4 formed of a metal such as an aluminum alloy or a steel material. For example, as shown in FIG. 12, the inner column bracket 4 is disposed below the inner column 51. As shown in FIG. 4, the inner column bracket 4 includes, for example, an arm part 41, a neck part 44, and a leg part 43. The arm portion 41 is a rod-shaped portion that connects the two sets of first telescopic friction plates 21 facing each other on both sides of the outer column 54. The neck portion 44 is a member protruding from a part of the arm portion 41 in a direction approaching the inner column 51. The leg 43 is a plate-like member provided at the end of the neck 44 opposite to the arm 41 and is in contact with the inner column 51. The inner column side surface 431 of the leg portion 43 shown in FIG. 13 has a shape along the shape of the outer wall of the inner column 51.

  Further, as shown in FIG. 13, the inner column bracket 4 includes a damper holding portion 46, a concave portion 48, and a through hole 47. The damper holding portion 46 is a surface of the arm portion 41 that faces the inner column 51. The concave portion 48 is a substantially rectangular parallelepiped recess formed in the damper holding portion 46, for example. The through hole 47 is provided at the bottom of the recess 48 and penetrates the arm portion 41 in the radial direction of the inner column 51.

  As shown in FIG. 4, the inner column bracket 4 is connected to the first telescopic friction plates 21 arranged on both sides of the outer column 54 by arm portions 41. The inner column bracket 4 is connected to the inner column 51 by a leg portion 43. Further, the inner column bracket 4 is arranged so that at least a part thereof fits into the first slit 541 of the outer column 54. Specifically, the leg 43 of the inner column bracket 4 is fitted so as to face the inner wall of the first slit 541.

  In order to detachably connect the inner column bracket 4 and the inner column 51, the inner column 51 has a first hole 51h and the leg 43 has a second hole 43h as shown in FIG. . The first hole 51h and the second hole 43h communicate with each other. For example, in the present embodiment, two each of the first hole 51h and the second hole 43h are provided, and the inner circumference is the same. By inserting the shear pin 8 at a position straddling the first hole 51h and the second hole 43h, the inner column bracket 4 and the inner column 51 are detachably connected. The share pin 8 is a so-called mechanical fuse. The first holes 51h and the second holes 43h are disposed at positions where the distances from the first telescopic friction plates 21 disposed on both sides of the outer column 54 are equal.

  The inner column bracket 4 can slide while facing the inner wall of the first slit 541 when telescopic adjustment is performed. The inner column bracket 4 is in contact with the first end inner wall 541e that is the inner wall of the front end of the first slit 541 when adjusting the telescopic position, thereby restricting the adjustment range of the telescopic position. Also, as shown in FIG. 12, the distance from the stopper 7 to the front end of the second slit 542 is longer than the distance from the inner column bracket 4 to the first end inner wall 541e. Thereby, after the inner column bracket 4 is detached from the inner column 51, the amount of forward movement (stroke amount) of the inner column 51 is ensured to be a predetermined amount or more. Therefore, in the present embodiment, the limit on the front side of the telescopic position is regulated by the inner column bracket 4 and the first end inner wall 541e, and the limit on the rear side of the telescopic position is the stopper 7 and the second end inner wall 542e. It is regulated by.

  FIG. 14 is an enlarged view of the periphery of the shear pin in FIG. In the present embodiment, the shear pin 8 includes an outer pin 81 and an inner pin 82. The outer pin 81 and the inner pin 82 are made of a resin such as polyacetal, for example.

  As shown in FIG. 14, the outer pin 81 is a cylindrical member that penetrates the first hole 51h and the second hole 43h. The outer pin 81 includes, for example, a main body portion 811, a retaining portion 812, a flange portion 813, and a guide hole 81h. The main body portion 811 has a cylindrical shape and passes through the first hole 51h and the second hole 43h. The retaining portion 812 is provided at one end of the main body portion 811 and is located inside the inner column 51. The retaining portion 812 is cylindrical and has an outer periphery larger than the inner periphery of the first hole 51h and the inner periphery of the second hole 43h. Thereby, since the retaining portion 812 contacts the inner wall of the inner column 51, the outer pin 81 is less likely to fall out of the first hole 51h and the second hole 43h. The flange portion 813 is provided at the other end of the main body portion 811, and is positioned outside the second hole 43 h in the radial direction of the inner column 51. The flange portion 813 has a disk shape, for example, and has an outer periphery larger than the inner periphery of the first hole 51h and the inner periphery of the second hole 43h. Thereby, since the flange part 813 contacts the bottom face of the recessed part 45, it becomes difficult for the outer pin 81 to fall out from the 1st hole 51h and the 2nd hole 43h. The guide hole 81h is a through-hole penetrating from the flange portion 813 to the retaining portion 812.

  The outer pin 81 is inserted into the first hole 51h and the second hole 43h, for example, by press fitting. By inserting the outer pin 81 into the first hole 51h and the second hole 43h, the first hole 51h and the second hole 43h are positioned. For example, the retaining portion 812 is inserted into the first hole 51h and the second hole 43h from the second hole 43h side.

  The outer pin 81 may be inserted into the first hole 51h and the second hole 43h from the first hole 51h side. The outer pin 81 may be press-fitted after providing a rib or the like on the outer wall of the main body portion 811.

  In a state in which the outer pin 81 passes through the first hole 51h and the second hole 43h, the main body portion 811 presses the inner wall of the first hole 51h and the inner wall of the second hole 43h by elastic deformation. For this reason, the clearance gap between the main-body part 811 and the inner wall of the 1st hole 51h and the clearance gap between the main-body part 811 and the inner wall of the 2nd hole 43h become difficult to produce. Thereby, the play of the outer pin 81 is suppressed.

  The inner pin 82 is a member that is inserted into the guide hole 81 h of the outer pin 81. The inner pin 82 includes, for example, a body part 821 and a large diameter part 822. The body portion 821 is cylindrical and penetrates the guide hole 81h. The large diameter portion 822 is provided at both ends of the body portion 821, and is located outside the guide hole 81h. The large diameter portion 822 has an outer periphery larger than the inner periphery of the guide hole 81h. As a result, the large-diameter portion 822 contacts the edges at both ends of the guide hole 81 h, so that the inner pin 82 is unlikely to come off the outer pin 81.

  Note that the guide hole 81h may include a stepped portion having an enlarged inner periphery at the end. In this case, since the large diameter portion 822 is in contact with the edge of the step portion, the inner pin 82 is difficult to protrude from the end portion of the guide hole 81h.

  In the present embodiment, the inner pin 82 is inserted into the guide hole 81h by press-fitting. For example, the large diameter portion 822 is inserted into the guide hole 81h from the flange portion 813 side. Since the inner pin 82 has the same large diameter portion 822 at both ends, the inner pin 82 can be inserted into the guide hole 81h from either end. Thereby, the assembly of the shear pin 8 becomes easy.

  When the inner pin 82 passes through the guide hole 81h, the body portion 821 pushes the inner wall of the guide hole 81h radially outward by elastic deformation. For this reason, a gap between the body portion 821 and the inner wall of the guide hole 81h is less likely to occur. Thereby, the play of the inner pin 82 is suppressed.

  Since the steering device 100 is assembled by inserting the inner pin 82 after positioning the first hole 51h and the second hole 43h with the outer pin 81, the steering device 100 can be easily assembled.

  The shear pin 8 does not necessarily have to be configured by the outer pin 81 and the inner pin 82 described above. For example, the shear pin 8 may be formed by hardening a resin or the like filled in a position straddling the first hole 51h and the second hole 43h. That is, the shear pin 8 may be a connecting member that removably connects the inner column bracket 4 and the inner column 51.

  When an excessive load is applied to the steering wheel 14, this load is transmitted to the inner column 51 via the input shaft 151, thereby moving the inner column 51 forward. On the other hand, the inner column bracket 4 supported by the first telescopic friction plate 21 does not move. For this reason, since a shearing force is applied to the shear pin 8, when the load exceeds the allowable shearing force of the shear pin 8, the shear pin 8 is cut. When the share pin 8 is cut, the connection between the inner column 51 and the inner column bracket 4 is released. As a result, the inner column 51 is supported in the axial direction by the frictional force generated between the inner column 51 and the outer column 54. Therefore, when an operator collides with the steering hole 14 during a secondary collision and an excessive load is applied, the force for moving the inner column 51 is reduced immediately after the excessive load is applied, and the impact is absorbed.

  Even when the shear pin 8 is cut, the outer column 54 remains supported by the outer column bracket 52 fixed to the vehicle body side member 13. Further, the inner column 51 remains supported by the outer column 54. For this reason, even if the shear pin 8 is cut, the steering column 5 does not fall.

  FIG. 15 is a diagram for explaining the state of the shear pin after being cut. As shown in FIG. 15, the shear pin 8 is cut along the cut surface BK. The cut surface BK is generated in a portion of the shear pin 8 that straddles the first hole 51h and the second hole 43h. In the cross section shown in FIG. 15, the cut surface BK is located on the extension line of the outer wall of the inner column 51, that is, on the extension line of the inner column side surface 431 of the leg portion 43. The outer pin 81 is cut at the main body portion 811, and the inner pin 82 is cut at the body portion 821. For this reason, the allowable shear force of the shear pin 8 depends on the cross-sectional area of the main body portion 811 and the cross-sectional area of the body portion 821 at the cut surface BK.

  Further, it is desirable that the inner column 51 moves straight in the axial direction after the shear pin 8 is cut. When the moving direction of the inner column 51 is an angle with respect to the axial direction of the outer column 54, the movement of the inner column 51 may be hindered or the frictional force generated between the inner column 51 and the outer column 54 This is because there is a high possibility that becomes larger than a predetermined value.

  In the present embodiment, the inner column bracket 4 is joined to the first telescopic friction plates 21 disposed on both sides of the outer column 54 as shown in FIG. Accordingly, when an axial load is applied to the inner column bracket 4, the inner column bracket 4 receives a tightening force from both sides of the outer column 54. For this reason, the attitude | position of the inner column bracket 4 when the shear pin 8 is cut | disconnected is stabilized. Therefore, the posture when the inner column 51 starts to move is easily kept straight with respect to the axial direction. Therefore, it becomes easy for the inner column 51 to move straight in the axial direction.

  Further, the first hole 51h and the second hole 43h are arranged at positions where the distances from the first telescopic friction plates 21 facing each other on both sides of the inner column bracket 4 are equal. Thus, when an axial load is applied to the inner column bracket 4, the inner column bracket 4 receives the tightening force from both sides of the outer column 54 more evenly, so the inner column bracket when the shear pin 8 is cut. 4's posture is stabilized. Therefore, the posture when the inner column 51 starts to move is easily maintained more straight in the axial direction. Therefore, it becomes easier for the inner column 51 to move straight in the axial direction.

  Even if the inner column bracket 4 cannot receive the tightening force from both sides of the outer column 54 evenly, the stopper 7 is fitted in the second slit 542. 51 is guided in the longitudinal direction of the second slit 542, that is, in the axial direction. For this reason, the attitude | position of the inner column bracket 4 when the shear pin 8 is cut | disconnected is stabilized.

  Further, as shown in FIG. 13, the first hole 51h and the second hole 43h are provided at two different positions in the axial direction. For this reason, two shear pins 8 are arranged at different positions in the axial direction. If each of the first hole 51h and the second hole 43h is provided, that is, if one shear pin 8 is disposed, the inner column bracket 4 may rotate around the shear pin 8. On the other hand, in this embodiment, the rotation of the inner column bracket 4 is suppressed by arranging the two shear pins 8 at different positions in the axial direction. For this reason, the posture of the inner column bracket 4 when the shear pin 8 is cut is more stable.

  The allowable shear force of the shear pin 8 can be adjusted by changing the number of the first holes 51h and the second holes 43h, the cross-sectional areas of the first holes 51h and the second holes 43h, and the material of the shear pin 8. For example, the number of the first holes 51h and the second holes 43h may be 1 or 3 or more, respectively. Further, the shear pin 8 may be formed of, for example, a metal containing a non-ferrous metal, rubber, or the like.

  FIG. 16 is a graph showing the relationship between the amount of displacement of the steering column and the load required to move the steering column for the comparative example. FIG. 17 is a diagram illustrating the relationship between the amount of displacement of the steering column and the load necessary to move the steering column in the present embodiment. 16 and 17, the horizontal axis represents the amount of displacement of the steering column forward, and the vertical axis represents the load necessary for moving the steering column forward.

  The comparative example is an example in which the outer column is attached to the vehicle body via a capsule as in the technique described in Patent Document 1. In the comparative example, the outer column is arranged on the rear side of the inner column, and when an excessive load is applied to the outer column, the rod contacts the end of the telescopic adjustment hole provided integrally with the outer column, and the bracket The load is transmitted to the capsule via the. A force F2c shown in FIG. 16 indicates the allowable shear force of the capsule.

  In the comparative example, the outer column is supported in the axial direction by a frictional force generated between the outer column and the inner column by tightening the bracket. A force F1c illustrated in FIG. 16 indicates the friction force supporting the outer column. The force F1c is smaller than the force F2c. In order to prevent the outer column from moving due to a load applied during normal use, the force F1c needs to be maintained at a predetermined value or more.

  In the comparative example, when a load of force F2c or more is applied to the outer column, the capsule is cut and the outer column is detached from the vehicle body. Thereafter, the outer column moves in the axial direction while absorbing the impact by the frictional force with the inner column. However, as described above, since the force F1c is maintained at a predetermined value or more, it is difficult to make the outer column move smoothly to make it easier to protect the operator from the secondary collision.

  On the other hand, in this embodiment, the inner column 51 is a member that contacts the first telescopic friction plate 21 and the first telescopic friction plate 21 with the first friction force generated between the outer column bracket 52 and the outer column 54 by tightening. The second frictional force generated between the outer column bracket 52, the second telescopic friction plate 22, and the outer column 54 is supported in the axial direction. A force F1 illustrated in FIG. 17 indicates the first friction force, and a force F3 indicates the sum of the first friction force and the second friction force. A force F2 shown in FIG. 17 indicates the allowable shear force of the shear pin 8. The force F2 is smaller than the force F3 and larger than the force F1.

  In the present embodiment, when a load of force F2 or more is applied to the inner column 51, the shear pin 8 is cut and the inner column 51 is detached from the inner column bracket 4. Thereby, since the connection between the inner column 51 and the first telescopic friction plate 21 is released, the second frictional force described above does not act on the inner column 51. For this reason, after the shear pin 8 is cut, the inner column 51 moves in the axial direction while absorbing the impact by the first frictional force described above. When the first frictional force is set to be small, the steering device 100 according to the present embodiment can smooth the movement of the inner column 51 and can more easily protect the operator from the secondary collision.

  In the present embodiment, even if the set value of the first frictional force is reduced, the second frictional force supplements the reduced amount of the first frictional force out of the force for supporting the inner column 51 in the axial direction. can do. For this reason, the steering device 100 according to the present embodiment adjusts the setting value of the first friction force and the setting value of the second friction force, so that the inner column 51 moves due to a load applied during normal use. It can suppress and can protect an operator from a secondary collision more easily.

  By the way, when performing the telescopic adjustment after operating the operation lever 53 in normal use, if the inner column bracket 4 comes into contact with the first end inner wall 541e, a shearing force acts on the shear pin 8. For this reason, when the force applied to the inner column 51 at the time of telescopic adjustment is excessive, the shear pin 8 may be cut by the telescopic adjustment. Therefore, the steering device 100 according to the present embodiment includes the first damper 6 and the second damper 9. As shown in FIGS. 12 and 13, the first damper 6 is attached to the first end inner wall 541 e, and the second damper 9 is attached to the inner column bracket 4.

  FIG. 18 is a perspective view of the first damper according to the present embodiment. The first damper 6 is made of, for example, synthetic rubber, and is a rectangular plate member as shown in FIG. The first damper 6 includes a flat surface 61 and a notch 62. The flat surface 61 is a surface orthogonal to the axial direction, for example. The notch 62 is, for example, a rectangular depression as viewed from the axial direction. The first damper 6 is fixed to the first end inner wall 541e with an adhesive, for example. Specifically, the first damper 6 is fixed to the first end inner wall 541e so that the notch 62 is positioned upward.

  FIG. 19 is a side view of the second damper according to the present embodiment. FIG. 20 is a perspective view of the second damper according to the present embodiment. FIG. 21 is a perspective view of the second damper according to the present embodiment. In FIG. 19, the inner column bracket 4 is indicated by a broken line. The second damper 9 is made of, for example, synthetic rubber. More specifically, the Young's modulus of the second damper 9 is larger than the Young's modulus of the first damper 6. That is, the rigidity of the second damper 9 is larger than the rigidity of the first damper 6. As shown in FIGS. 19 to 21, the second damper 9 includes a base portion 91, a plurality of protrusions 92, and a retaining portion 99. For example, the base 91, the plurality of protrusions 92, and the retaining portion 99 are integrally formed.

  The base portion 91 has a substantially rectangular parallelepiped shape that contacts the damper holding portion 46. The protrusion 92 is a member that protrudes forward from the base 91 and has, for example, a substantially triangular prism shape whose longitudinal direction is a direction orthogonal to the axial direction. The number of the protrusions 92 is five, for example, and the five protrusions 92 are arranged in parallel to each other toward the short direction of the first slit 541. A gap 921 is formed between the adjacent protrusions 92.

  Note that the number of the protrusions 92 is not limited, and may be four or less, or may be six or more. Further, the projection 92 does not necessarily have a substantially triangular prism shape, and may be a substantially rectangular parallelepiped shape, a substantially cylindrical shape, a substantially conical shape, a substantially hemispherical shape, or the like. The protrusion 92 may protrude rearward from the base 91. Moreover, the base 91 and the protrusion 92 may have a cavity inside. That is, the base 91 and the protrusion 92 may be hollow members.

  The retaining portion 99 is a member for preventing the second damper 9 from falling off from the inner column bracket 4. The retaining portion 99 includes a first fitting portion 94, a second fitting portion 95, a positioning portion 96, and a guide portion 97. The first fitting portion 94 is provided behind the base portion 91 and is in contact with the neck portion 44 of the inner column bracket 4. The first fitting portion 94 is fitted in the recess 48 of the inner column bracket 4. The 2nd fitting part 95 protrudes below from the 1st fitting part 94, for example, is cylindrical. The second fitting portion 95 passes through the through hole 47 of the inner column bracket 4. The outer periphery of the second fitting portion 95 is substantially equal to the inner periphery of the through hole 47. The positioning portion 96 protrudes downward from the lower end portion of the second fitting portion 95 and has, for example, a substantially conical shape whose outer periphery decreases from the second fitting portion 95 side downward. The upper end portion of the positioning portion 96, that is, the maximum outer peripheral portion is in contact with the surface of the arm portion 41 of the inner column bracket 4. The outer periphery of the upper end portion (maximum outer peripheral portion) of the positioning portion 96 is larger than the inner periphery of the through hole 47, and the outer periphery of the lower end portion (minimum outer peripheral portion) of the positioning portion 96 is smaller than the inner periphery of the through hole 47. . The guide part 97 protrudes downward from the lower end part of the positioning part 96, for example, is cylindrical. The outer periphery of the guide portion 97 is smaller than the inner periphery of the through hole 47.

  When the second damper 9 is attached to the inner column bracket 4, the retaining portion 99 is inserted into the through hole 47 from the concave portion 48 side. Since the outer periphery of the guide portion 97 is smaller than the inner periphery of the through hole 47, the guide portion 97 can easily enter the through hole 47. Thereafter, for example, after the positioning portion 96 contacts the edge of the through hole 47, the positioning portion 96 is press-fitted into the through hole 47. The positioning portion 96 passes through the through-hole 47 while being deformed by being pushed into the through-hole 47 with the guide portion 97 inserted in the through-hole 47 in advance. The positioning part 96 contacts the surface of the arm part 41 by elastically deforming after passing through the through hole 47. For this reason, the second damper 9 is prevented from falling off from the inner column bracket 4.

  When the retaining portion 99 is pushed into the through hole 47, the retaining portion 99 may fall down. However, in the present embodiment, even if the retaining portion 99 falls down, the guide portion 97 contacts the inner wall of the through hole 47. Thereby, the angle at which the retaining portion 99 falls is regulated to a predetermined angle or less. Thereby, the posture of the retaining portion 99 when being pushed into the through hole 47 is easily stabilized. For this reason, the second damper 9 can be easily attached to the inner column bracket 4.

  FIG. 22 is a diagram illustrating a state in which the inner column bracket is in contact with the inner wall of the first end portion in the comparative example. FIG. 23 is a graph showing the relationship between the position of the inner column and the shearing force applied to the shear pin for the comparative example. In the comparative example, a damper 6c made of synthetic rubber is provided on the first end inner wall 541e, while no damper is provided on the inner column bracket 4c. 22 and 23, the axial position of the inner column 51 is indicated by x, and the value of x increases as the position of the inner column 51 moves forward. In FIG. 23, x when the front end portion of the inner column bracket 4c is in contact with the first end inner wall 541e is indicated as x1.

  In the comparative example, when the telescopic adjustment is performed after the operation lever 53 is operated, the front end portion of the inner column bracket 4c comes into contact with the damper 6c when the telescopic position becomes the forefront (x = x1). When the force f1 is applied to the inner column 51 with the inner column bracket 4c in contact with the damper 6c, the force f1 is applied to the damper 6c as a reaction force from the first end inner wall 541e. Since the damper 6c which is a synthetic rubber is deformed to some extent, a part of the force f1 is consumed for the deformation of the damper 6c. For this reason, a force f2c smaller than the force f1 acts on the shear pin 8 as a shearing force fc via the inner column bracket 4c. However, since the size of the damper 6c attached to the first end inner wall 541e is limited, the force f2c may not be sufficiently reduced. For this reason, as shown in FIG. 23, when the force f1 is larger than the allowable shear force fa of the shear pin 8, the force f2c acting on the shear pin 8 may be larger than the allowable shear force fa of the shear pin 8. Therefore, in the comparative example, when telescopic adjustment is performed, if the inner column bracket 4c collides with the first end inner wall 541e with a force larger than the allowable shear force fa of the shear pin 8, x = x2 in FIG. At that time, the shear pin 8 is cut.

  FIG. 24 is a diagram illustrating a state in which the second damper is in contact with the first damper in the present embodiment. FIG. 25 is a graph showing the relationship between the position of the inner column and the shearing force applied to the shear pin for this embodiment. 24 and 25, the position of the inner column 51 in the axial direction is indicated by x, and the value of x increases as the position of the inner column 51 moves forward. In FIG. 25, x when the second damper 9 is in contact with the first damper 6 is indicated as x1.

  In the present embodiment, when the telescopic adjustment is performed after the operation lever 53 is operated, the second damper 9 comes into contact with the first damper 6 when the telescopic position becomes the forefront (x = x1). The protrusion 92 of the second damper 9 is in contact with the flat surface 61 of the first damper 6. As described above, the Young's modulus of the second damper 9 is larger than the Young's modulus of the first damper 6. For this reason, when the second damper 9 is pressed against the first damper 6, the first damper 6 is greatly deformed. Since there is a gap 921 between adjacent protrusions 92, the flat surface 61 is deformed so as to enter the gap 921. The second damper 9 is also deformed in the axial direction. The spring constants of the first damper 6, the projection 92, the base 91, and the first fitting portion 94 are k6, k92, k91, and k94, respectively, and the first damper 6, the projection 92, the base 91, and the first fitting portion 94 are combined. If the overall spring constant is K, K is defined by the following formula (1). The first damper 6 and the second damper 9 according to the present embodiment have a predetermined spring constant K, that is, a predetermined shock absorption capacity, by appropriately adjusting k6, k92, k91, and k94.

  1 / K = (1 / k6) + (1 / k92) + (1 / k91) + (1 / k94) (1)

  Since both the first damper 6 and the second damper 9 are deformed, the amount of movement of the inner column 51 until the shear force f applied to the shear pin 8 reaches a peak force f2 with respect to the comparative example shown in FIG. Becomes larger. That is, x3 shown in FIG. 25 is larger than x2 shown in FIG. Further, since the flat surface 61 is deformed so as to enter the gap 921, the first damper 6 is easily deformed as compared with a case where it is simply compressed in the axial direction as in the comparative example shown in FIG. For this reason, in this embodiment, the peak shear force applied to the shear pin 8 is smaller than that of the comparative example. That is, the force f2 shown in FIG. 25 is smaller than the force f2c shown in FIG. Therefore, in the present embodiment, when performing telescopic adjustment, even if a force larger than the allowable shear force fa of the shear pin 8 acts on the inner column 51, the shear pin 8 is easily cut off.

  As described above, the steering device 100 according to the present embodiment includes the inner column 51, the outer column 54, the outer column bracket 52, the inner column bracket 4, the shear pin 8, the first damper 6, and the second damper. 9. The inner column 51 is a cylindrical member that rotatably supports an input shaft 151 connected to the steering wheel 14 and has a first hole 51h. The outer column 54 has a cylindrical shape into which at least a part of the inner column 51 is inserted inside, and has a first slit 541 in which one end on the insertion side of the inner column 51 is cut out. The outer column bracket 52 is fixed to the vehicle body side member 13, supports the outer column 54, and tightens the outer column 54 together with a telescopic friction plate (first telescopic friction plate 21) which is a plate material. The inner column bracket 4 is supported by a telescopic friction plate (first telescopic friction plate 21), and a second hole 43h is opened. The share pin 8 is in a position straddling the first hole 51h and the second hole 43h, and connects the inner column 51 and the inner column bracket 4 in a detachable manner. The first damper 6 is attached to a first end inner wall 541e that is an inner wall of the end of the first slit 541. The second damper 9 is attached to the inner column bracket 4 and faces the first damper 6.

  Thereby, the load applied to the steering wheel 14 at the time of the secondary collision is transmitted to the inner column 51 via the input shaft 151, thereby moving the inner column 51 forward. On the other hand, the inner column bracket 4 supported by the first telescopic friction plate 21 does not move. For this reason, since a shearing force is applied to the shear pin 8, when the load exceeds the allowable shearing force of the shear pin 8, the shear pin 8 is cut. When the share pin 8 is cut, the connection between the inner column 51 and the inner column bracket 4 is released. As a result, the inner column 51 is supported in the axial direction by the frictional force generated between the inner column 51 and the outer column 54. For this reason, the inner column 51 can be moved forward of the vehicle body. Even when the shear pin 8 is cut, the outer column 54 remains supported by the outer column bracket 52 fixed to the vehicle body side member 13. Further, the inner column 51 remains supported by the outer column 54. For this reason, even if the shear pin 8 is cut, the steering column 5 does not fall. Further, when the telescopic position is adjusted, the second damper 9 comes into contact with the first damper 6 when the telescopic position becomes the foremost position. Thereby, a part of the load applied to the inner column 51 is consumed for the deformation of the first damper 6 and the second damper 9. For this reason, the peak of the shearing force acting on the shear pin 8 when adjusting the telescopic position is less likely to exceed the allowable shearing force of the shear pin 8. Therefore, the steering device 100 can suppress the drop of the steering column 5 due to a malfunction, and can protect the separation mechanism during telescopic adjustment.

  In the steering device 100 according to the present embodiment, the first damper 6 includes a flat surface 61 that faces the second damper 9. The second damper 9 includes a plurality of protrusions 62 that face the flat surface 61. The Young's modulus of the second damper 9 is larger than the Young's modulus of the first damper 6.

  Accordingly, since there is a gap 921 between the adjacent protrusions 92, the flat surface 61 is deformed so as to enter the gap 921. For this reason, the 1st damper 6 becomes easy to change compared with the case where it is simply compressed in the direction of an axis. Therefore, since the peak of the shearing force acting on the shear pin 8 is easily reduced when adjusting the telescopic position, the shear pin 8 is more difficult to cut.

  In the steering device 100 according to the present embodiment, the inner column bracket 4 includes a through hole 47 that penetrates the inner column 51 in the radial direction. The second damper 9 includes a retaining portion 99 that penetrates the through hole 47.

  Thereby, the direction of the force applied to the second damper 9 during telescopic adjustment is different from the direction in which the second damper 9 is prevented from coming off from the inner column bracket 4. For this reason, even when a force is repeatedly applied to the second damper 9, the retaining portion 99 is unlikely to be worn, and the retaining portion 99 is unlikely to fall off the inner column bracket 4. Accordingly, the second damper 9 is prevented from falling off from the inner column bracket 4.

  In the steering apparatus 100 according to the present embodiment, the inner column bracket 4 is disposed on the vehicle body lower side with respect to the inner column 51, and includes a damper holding portion 46 that is a surface facing the inner column 51. The second damper 9 is attached to the damper holding part 46.

  Thereby, since the 2nd damper 9 is stored in the damper holding | maintenance part 46, the magnitude | size as an apparatus with which the inner column bracket 4 and the 2nd damper 9 were united is reduced in size. Further, since the second damper 9 is placed above the inner column bracket 4, the second damper 9 is prevented from falling off from the inner column bracket 4.

  In the steering device 100 according to the present embodiment, the first damper 6 and the second damper 9 are synthetic rubber.

  Since the synthetic rubber is a highly elastic material, the elastic limit of the first damper 6 and the second damper 9 is increased. For this reason, even when a force is repeatedly applied to the first damper 6 and the second damper 9, plastic deformation hardly occurs in the first damper 6 and the second damper 9. Therefore, it is possible to prevent the forefront position of the telescopic from being deviated from a predetermined position by plastic deformation of the first damper 6 and the second damper 9.

12, 13 Car body side member 14 Steering wheel 15 Steering shaft 151 Input shaft 152 Output shaft 16 Universal joint 17 Lower shaft 18 Universal joint 19 Pinion shaft 100 Steering device 21 First telescopic friction plate 22 Second telescopic friction plate 31 Rod penetration portion 33 Rod 4 Inner column bracket 43h Second hole 46 Damper holding portion 47 Through hole 5 Steering column 51 Inner column 51h First hole 52 Outer column bracket 53 Operation lever 54 Outer column 541 First slit 541e First end inner wall 542 Second slit 542e Second end inner wall 6 First damper 61 Flat surface 7 Stopper 8 Shear pin 9 Second damper 91 Base 92 Projection 94 First fitting portion 95 Second fitting portion 96 Positioning Part 97 guide portion 99 retaining portion BK cutting plane VB body

Claims (5)

A cylindrical inner column having a first hole formed therein, rotatably supporting an input shaft coupled to the steering wheel;
An outer column having a cylindrical shape into which at least a part of the inner column is inserted inside, and having a slit cut out at one end on the insertion side of the inner column;
An outer column bracket that is fixed to a vehicle body side member, supports the outer column, and tightens the outer column together with a telescopic friction plate that is a plate material;
An inner column bracket supported by the telescopic friction plate and having a second hole;
A shear pin in a position straddling the first hole and the second hole and releasably connecting the inner column and the inner column bracket;
A first damper attached to an end inner wall that is an inner wall of the end of the slit;
A second damper attached to the inner column bracket and facing the first damper;
A steering apparatus comprising: The first damper includes a flat surface facing the second damper,
The second damper includes a plurality of protrusions facing the flat surface,
The steering device according to claim 1, wherein a Young's modulus of the second damper is larger than a Young's modulus of the first damper. The inner column bracket includes a through-hole penetrating in the radial direction of the inner column,
The steering apparatus according to claim 1, wherein the second damper includes a retaining portion that penetrates the through hole. The inner column bracket is disposed on the vehicle body lower side with respect to the inner column, and includes a damper holding portion that is a surface facing the inner column,
The steering apparatus according to any one of claims 1 to 3, wherein the second damper is attached to the damper holding portion.   The steering device according to any one of claims 1 to 4, wherein the first damper and the second damper are made of synthetic rubber.

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