JP6500580B2 - Steering device - Google Patents

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 for giving a steering angle to wheels as the steering wheel rotates. For example, according to Patent Document 1, an excessive load is applied to a steering column attached to a vehicle body via a capsule, and a part of the capsule is cut when the steering column is pushed forward of the vehicle body. Technology is described that is adapted to move to and protect the driver (operator) from steering wheel thrust (secondary collision).

JP 2007-69800 A

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

  The present invention has been made in view of the above problems, and provides a steering device capable of suppressing the falling of the steering column due to a malfunction even if the setting value of the separation load at which the steering column moves forward to the vehicle body is lowered. With the goal.

  In order to achieve the above object, in a steering apparatus according to the present invention, a cylindrical inner column rotatably supporting an input shaft connected to a steering wheel, and at least a part of the inner column are inserted inside The outer column has a cylindrical shape and has a slit formed by cutting out one end on the insertion side of the inner column, and is fixed to a vehicle body side member to support the outer column, and the outer column is supported together with a telescopic friction plate which is a plate. An outer column bracket for tightening, a rod that penetrates the telescopic friction plate and the outer column bracket and supports the telescopic friction plate, an inner column exposed by the slit, and an inner disposed opposite to the telescopic friction plate Column bracket, said telescopic friction plate and said in A first shear pin that releasably connects the chromatography column bracket, characterized in that it comprises a second shear pin that releasably coupling the inner column and the inner column bracket.

  Thus, in the steering apparatus according to the present invention, when an excessive load is applied to the steering wheel, the load is transmitted to the inner column via the input shaft to move the inner column forward. On the other hand, the telescopic friction plate does not move. Thereby, a shear force is applied to the first shear pin and the second shear pin. Therefore, if the excessive load exceeds the allowable shear force of the first shear pin or the second shear pin, the first shear pin or the second shear pin is cut. When the first shear pin or the second shear pin is cut, the connection between the inner column and the telescopic friction plate is released. When the connection between the inner column and the telescopic friction plate is released, the inner column is axially supported by the frictional force generated between the inner column and the outer column. Thus, the inner column of the steering column can be moved forward of the vehicle body. Also, even if the first shear pin or the second shear pin is cut, the outer column remains supported by the outer column bracket fixed to the vehicle body side member. Also, the inner column remains supported by the outer column. Therefore, even if the first shear pin or the second shear pin is cut, the steering column does not fall. Therefore, the steering apparatus according to the present invention can suppress the falling of the steering column due to a malfunction even if the setting value of the separation load at which the steering column moves forward to the vehicle body is lowered.

  As a desirable mode of the present invention, the telescopic friction plate is provided with a first hole, the inner column bracket is provided with a second hole to be overlapped with the first hole, and the first shear pin is provided with the first It is preferable to be inserted at a position straddling one hole and the second hole.

  Thereby, the telescopic friction plate and the inner column bracket are connected by the first shear pin being inserted into the first hole and the second hole. Thus, the steering device can be easily assembled.

  As a desirable mode of the present invention, the inner column is provided with a third hole, and the inner column bracket is provided with a fourth hole to be overlapped with the third hole, and the second shear pin is provided with the third hole. It is preferable to be inserted at a position straddling the hole and the fourth hole.

  Thus, the second shear pin is inserted into the third hole and the fourth hole, whereby the inner column and the inner column bracket are connected. Thus, the steering device can be easily assembled.

  As a desirable mode of the present invention, the shear strength of the first shear pin is preferably lower than the shear strength of the second shear pin.

  Thus, in the secondary collision, the first shear pin is cut before the second shear pin is cut. For this reason, in the steering apparatus, since the set value of the separation load is adjusted by adjusting the shear strength of the first shear pin, setting of the separation load is easy.

  As a desirable mode of the present invention, the telescopic friction plates are disposed on both sides of the inner column bracket, and the inner column brackets are disposed on both sides of the inner column bracket by the plurality of first shear pins. Preferably, it is connected to a telescopic friction plate.

  As a result, when a load is applied to the inner column bracket, the inner column bracket receives tightening force from both sides, so the posture of the inner column bracket when the first shear pin is cut is stabilized. Therefore, the posture at which the inner column starts moving can be more easily kept straight in the axial direction. Therefore, the inner column is easily moved straight in the axial direction, which prevents the movement of the inner column from being hindered or that the frictional force generated between the inner column and the outer column becomes larger than a predetermined value. .

  According to the present invention, it is possible to provide a steering device capable of suppressing the falling of the steering column due to a malfunction even if the setting value of the separation load at which the steering column moves forward to the vehicle body is lowered.

FIG. 1 is a view schematically showing the periphery of a 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 device according to the present embodiment. FIG. 4 is a perspective view of the steering device according to the present embodiment as viewed from above the vehicle body. FIG. 5 is a cross-sectional view taken along line A-A in FIG. 6 is a cross-sectional view taken along the line B-B in FIG. FIG. 7 is a cross-sectional view taken along the line C-C in FIG. FIG. 8 is an enlarged view of the periphery of the stopper in FIG. FIG. 9 is a cross-sectional view taken along the line DD in FIG. FIG. 10 is an enlarged view of the periphery of the inner column bracket in FIG. FIG. 11 is a view on arrow E in FIG. FIG. 12 is a perspective view of the inner column bracket according to the present embodiment. FIG. 13 is a perspective view of the inner column bracket according to the present embodiment. FIG. 14 is a perspective view showing an inner column, an inner column bracket, and a telescopic friction plate according to the present embodiment. FIG. 15 is a cross-sectional view showing the periphery of the first shear pin in an enlarged manner. FIG. 16 is a view showing only the first shear pin in FIG. 15 as a side view. FIG. 17 is an enlarged cross-sectional view of the periphery of the second shear pin. FIG. 18 is a view showing only the second shear pin in FIG. 17 as a side view. FIG. 19 is a bottom view showing the state of the first shear pin after it has been cut. FIG. 20 is a cross-sectional view showing the vicinity of the first shear pin after being cut. FIG. 21 is an enlarged cross-sectional view of the periphery of the second shear pin after being cut. FIG. 22 is a graph showing the relationship between the displacement amount of the steering column and the load required to move the steering column in the comparative example. FIG. 23 is a diagram showing the relationship between the displacement amount of the steering column and the load required to move the steering column in the present embodiment.

  A mode (embodiment) 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. Further, the components described below include those which can be easily conceived by those skilled in the art and those which are substantially the same. Furthermore, the components described below can be combined as appropriate.

(Embodiment)
FIG. 1 is a view schematically showing the periphery of a 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 device according to the present embodiment. FIG. 4 is a perspective view of the steering device according to the present embodiment as viewed from above the vehicle body. In the following description, the direction on the front side of the vehicle body VB when the steering apparatus 100 is attached to the vehicle body VB in the direction along the rotation center axis Zr described later is simply referred to as the front. Of the directions along the rotation center axis Zr, the direction on the rear side of the vehicle body VB when the steering device 100 is attached to the vehicle body VB is simply described as the rear. Further, among the directions orthogonal to the rotation center axis Zr, the direction on the upper side of the vehicle body VB when the steering device 100 is attached to the vehicle body VB is simply described as upward. Of the directions orthogonal to the rotation center axis Zr, the downward direction of the vehicle body VB when the steering device 100 is attached to the vehicle body VB is simply referred to as the downward direction. That is, in FIG. 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 of transmission of the force applied from the operator, and is joined to the pinion shaft 19. ing.

  The steering shaft 15 includes an input shaft 151 and an output shaft 152. One end of the input shaft 151 is connected to the steering wheel 14, and the other end is connected to the output shaft 152. For example, the surface of the input shaft 151 is coated with a resin. Thus, the input shaft 151 is coupled to the output shaft 152 via the resin. One end of the output shaft 152 is connected to the input shaft 151, and the other end is connected to the universal joint 16. In the present embodiment, the input shaft 151 and the output shaft 152 are generally steel such as carbon steel for machine structure (SC material), carbon steel pipe for machine structure (STKM material) or cold-rolled steel plate (SPCC material) It is formed from

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

  The steering device 100 further includes a cylindrical inner column 51 rotatably supporting the input shaft 151 about the rotation center axis Zr, and a cylindrical outer column 54 in which at least a portion of the inner column 51 is inserted inside. And a steering column 5 including the The inner column 51 is disposed rearward of the outer column 54. For example, the inner column 51 and the outer column 54 are formed of carbon steel pipe for machine structure (STKM material) or aluminum alloy for die casting (ADC material).

  The steering device 100 includes an outer column bracket 52 fixed to the vehicle body side member 13 and supporting the outer column 54. Outer column bracket 52 is formed of a general steel material or the like such as a cold-rolled steel plate (SPCC material). The outer column bracket 52 includes an attachment plate portion 522 fixed to the vehicle body side member 13 and a frame-like support portion 521 integrally formed with the attachment plate portion 522. The mounting plate 522 of the outer column bracket 52 has a mounting hole 522h as shown in FIGS. 3 and 4, and is fixed to the vehicle body side member 13 using the mounting hole 522h and a fixing member such as a bolt. The frame-like support portions 521 of the outer column bracket 52 are disposed on both sides of the outer column 54 and clamp the outer column 54. Further, the frame-shaped support portion 521 is provided with a tilt adjustment hole 521 h which is a long hole which is long in the vertical direction of the vehicle body VB.

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

  FIG. 5 is a cross-sectional view taken along line A-A in FIG. As shown in FIG. 5, the outer column 54 has two rod penetrations 31, a first slit 541, and a second slit 542. The rod penetration part 31 is a member which protrudes below, for example from the outer wall of the inner column 51, and has 31 h of rod penetration holes which are round holes. The rod through holes 31 h of the two rod through portions 31 face each other with the first slit 541 interposed therebetween. In addition, a part of the rod penetration portion 31 is opposed to the frame-shaped support portion 521. The rod 33 penetrates the two rod through holes 31 h and penetrates the tilt adjustment hole 521 h of the frame-like support portion 521 and is connected to the operation lever 53.

  The first slit 541 is an elongated hole formed by cutting out one end of the outer column 54 on the insertion side of the inner column 51. The first slit 541 is provided at a position between the two rod penetrations 31. The outer column 54 has the first slit 541 so that the inner diameter decreases when it is 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 at 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 the present embodiment, the outer wall of the inner column 51 is coated with a low-friction material to reduce friction with the outer column 54.

  As shown in FIG. 5, the steering device 100 has a first telescopic friction plate 21 and a second telescopic friction plate 22 in order to strengthen the tightening and holding force on the steering column 5. For example, the first telescopic friction plate 21 and the second telescopic friction plate 22 are formed of a general steel material or the like such as a cold-rolled steel plate (SPCC material). The first telescopic friction plate 21 is a plate-like member having a telescopic adjustment hole 21 h which is a long hole whose longitudinal direction is the direction of the rotation center axis Zr. The first telescopic friction plates 21 are disposed, for example, on both sides of the outer column 54. More specifically, the first telescopic friction plates 21 are disposed two by two at a position between the frame-like support portion 521 and the rod penetration portion 31. The second telescopic friction plate 22 is, for example, a member formed by bending a plate material, 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 connection portion 222 connecting the two friction portions 221, and a bending portion provided in the connection portion 222. And H.223.

  The friction portion 221 has a rod through hole 22 h which is a round hole. The rod 33 passes through the telescopic adjustment hole 21 h and the rod through hole 22 h. Since the connection portion 222 connects and integrates the two friction portions 221, the work of arranging the friction portion 221 between the two first telescopic friction plates 21 is facilitated. Moreover, the connection part 222 can maintain the bent state by having the bending part 223. As shown in FIG. Thereby, the connecting portion 222 is difficult to pull the friction portion 221 even when the tightening state of the outer column bracket 52 changes and the distance between the two friction portions 221 changes. Therefore, the possibility that a gap is generated between the friction portion 221 and the first telescopic friction plate 21 when the friction portion 221 is pulled by the connecting portion 222 is reduced.

  The first telescopic friction plate 21 may not necessarily 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 support portion 521. That is, the first telescopic friction plate 21 may be disposed on the opposite side of the rod penetration portion 31 with the frame-like support portion 521 interposed therebetween.

  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 portion 521 and the first telescopic friction plate 21, between the first telescopic friction plate 21 and the frictional portion 221 of the second telescopic friction plate 22, the first telescopic friction plate 21 and the rod penetration portion Frictional force is generated between them and 31, respectively. For this reason, compared with the case where the 1st telescopic friction plate 21 and the 2nd telescopic friction plate 22 do not exist, the surface which a frictional force produces increases. The frame-like 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 on the frame-like support 521 is relaxed, and the frictional force between the frame-like support 521 and the outer column 54 disappears or decreases. Thus, 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 mounting plate 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 at the time of tilt adjustment and suppresses the falling of the steering column 5. One end of the second spring 57 is attached to the mounting plate 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 with the longitudinal direction of the tilt adjustment hole 521 h. Thereby, rattling of the rod 33 at the time of tilt adjustment is suppressed.

  In addition, when the operation lever 53 is rotated, the tightening force on the frame-like support portion 521 is relaxed, and the width of the first slit 541 of the outer column 54 is increased. As a result, the force with which the outer column 54 clamps the inner column 51 is eliminated, and 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 via the steering wheel 14 after rotating the operation lever 53.

  6 is a cross-sectional view taken along the line B-B in FIG. As shown in FIG. 6, the steering device 100 includes a rotation stopper 543.

  The rotation stopper 543 is formed integrally with the outer column 54, for example, and is disposed at the rear end of the outer column 54. The rotation stopper 543 is an annular member covering the inner column 51 over the entire circumference in the circumferential direction. The rotation stopper 543 is located rearward of the rod penetration portion 31 and the first slit 541. The annular rotation stopper 543 is disposed rearward of the first slit 541 so that the first slit 541 is an elongated hole whose both ends are closed. Thereby, the deformation of the outer column 54 at the time of tightening does not easily concentrate at the rear end of the first slit 541. That is, the deformation of the outer column 54 at the time of tightening tends to be equal between the front side and the rear side of the rod 33. Therefore, the setting of the frictional force between the inner column 51 and the outer column 54 at the time of tightening becomes easy.

  More specifically, the rotation stopper 543 includes a base 546, a bridge portion 544, and a rotation restricting portion 545 as shown in FIG. The base 546 is, for example, a member that covers the upper side of the inner column 51. When viewed in the rotation center axis Zr direction, the base 546 is substantially U-shaped, and both side surfaces of the base 546 are in contact with the inside of the frame-like support 521. The width of the base 546 in the axial direction of the rod 33 is approximately equal to the distance between the two opposing frame-like supports 521. The bridge portion 544 is a member that covers, for example, the lower side of the inner column 51, and connects the end portions of the base portion 546 to each other. When viewed in the direction of the rotation center axis Zr, the bridge portion 544 is substantially U-shaped and faces the inner column 51 with a gap. The width of the bridge portion 544 in the axial direction of the rod 33 is smaller than the width of the base 546. Thus, rotation restricting portions 545 as stepped portions are formed on both sides of the outer column 54 at the lower end of the base 546. The rotation restricting portion 545 opposes the upper end 212 of the first telescopic friction plate 21 with a gap. At the time of the secondary collision, the upper end 212 of the first telescopic friction plate 21 contacts the rotation restricting portion 545, whereby the rotation of the inner column bracket 4 described later is suppressed. In addition, since the first telescopic friction plate 21 and the rotation stopper 543 do not interfere with each other in normal times, the adjustment of the telescopic position is not inhibited by the rotation stopper 543.

  The bridge portion 544 connects the end portions of the base portion 546 and is located behind the first slit 541. That is, the bridge portion 544 blocks the opening of the first slit 541. Thus, the entry of foreign matter into the first slit 541 when the inner column 51 slides with respect to the outer column 54 is suppressed. Further, since the ends of the base portion 546 are connected by the bridge portion 544, the deformation amount of the base portion 546 at the time of tightening tends to be equalized on both sides of the bridge portion 544.

  The rotation stopper 543 may not necessarily be integrally formed with the outer column 54, and may be attached to the rear end of the outer column 54 as a separate member, for example. In addition, if the steering device 100 does not have the tilt adjustment function, the rotation stopper 543 may be provided as a protrusion that protrudes from the surface (inner surface) facing the outer column 54 of the frame-shaped support portion 521. Further, the bridge portion 544 may not necessarily be provided as a part of the rotation stopper 543, and may be disposed at a position different from the rotation stopper 543. Furthermore, the bridge portion 544 may be omitted.

  FIG. 7 is a cross-sectional view taken along the line C-C in FIG. FIG. 8 is an enlarged view of the periphery of the stopper in FIG. As shown in FIGS. 7 and 8, the steering device 100 includes a stopper 7. The stopper 7 is attached to a position of the inner column 51 exposed by the second slit 542.

  The stopper 7 includes, for example, a bolt 71, a backing plate 72, a washer 73, a spacer 74, and a conducting plate 75. The backing plate 72 is a metal plate-like member provided with a cylindrical protrusion. A cylindrical projection of the backing plate 72 is fitted into the through hole provided at the position exposed by the second slit 542 of the inner column 51 from the inside of the inner column 51. The backing plate 72 has an internal thread on the inner wall of the cylindrical projection. The bolt 71 is fastened to the female screw of the backing plate 72. The washer 73 is disposed between the bolt head of the bolt 71 and the backing plate 72. The bottom surface of the washer 73 is shaped to conform to the shape of the outer wall of the inner column 51. Thereby, the attitude of the bolt 71 is stabilized. The spacer 74 is a member for filling the gap between the inner wall of the second slit 542 and the bolt 71 and the gap between the inner wall of the second slit 542 and the backing plate 72. The spacer 74 is, for example, a resin member provided with a through hole. The bolt 71 and the backing plate 72 are disposed inside the through hole of the spacer 74. The conduction plate 75 is, for example, a plate member made of metal. The energizing plate 75 is, for example, sandwiched and fixed between the head of the bolt 71 and the spacer 74 and is in contact with the outer column 54. As a result, the inner column 51 is in the conductive state with the outer column 54 via the contact plate 72, the bolt 71 and the conductive plate 75. In the present embodiment, for example, when body grounding is performed for the 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 via 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 causing the electricity transmitted from the input shaft 151 to the inner column 51 to flow to the outer column 54.

  The stopper 7 is attached to the inner column 51, and can slide in a state 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 regulates the adjustment range of the telescopic position by contacting the second end inner wall 542 e which is the rear end of the second slit 542 at the time of adjusting the telescopic position. Further, when 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.

  FIG. 9 is a cross-sectional view taken along the line DD in FIG. FIG. 10 is an enlarged view of the periphery of the inner column bracket in FIG. FIG. 11 is a view on arrow E in FIG. 12 and 13 are perspective views of the inner column bracket according to the present embodiment. The steering device 100 includes an inner column bracket 4 formed of metal such as aluminum alloy or steel. For example, as shown in FIG. 10, the inner column bracket 4 is disposed below the inner column 51. As shown in FIGS. 12 and 13, the inner column bracket 4 includes, for example, an arm 41, a protrusion 42, a neck 44, and a leg 43. The arm portion 41 is a member disposed between two pairs of first telescopic friction plates 21 facing each other on both sides of the outer column 54, as shown in FIG. The projecting portion 42 is a member that protrudes in the direction approaching the inner column 51 from both ends of the arm portion 41 and is opposed to the first telescopic friction plate 21. The neck portion 44 is a member that protrudes in the direction approaching the inner column 51 from the middle in the longitudinal direction of the arm portion 41. The leg 43 is a plate-like portion provided at the end of the neck 44 opposite to the arm 41 and is in contact with the inner column 51. As shown in FIG. 12 and FIG. 13, the inner column side surface 431 of the leg 43 is shaped according to the outer wall of the inner column 51. The leg 43 includes, for example, two circular recesses 45 on the surface opposite to the surface facing the inner column 51.

  Further, as shown in FIG. 10, the inner column bracket 4 is provided with a notch 46 and a through hole 47. The notch 46 is a notch formed on the surface facing the inner column 51 at the front end of the inner column bracket 4. The through hole 47 is provided in the notch 46 and penetrates the arm 41 in the radial direction of the inner column 51. The damper 10 is disposed in the notch 46 and the through hole 47.

  In order to releasably connect the first telescopic friction plate 21 and the inner column bracket 4, as shown in FIG. 14, the first hole 21 a is opened in the first telescopic friction plate 21, as shown in FIGS. 12 and 13. A second hole 42 h is opened in the projection 42. The second holes 42 h are arranged to overlap the first holes 21 a. That is, the first hole 21a and the second hole 42h communicate with each other. For example, in the present embodiment, two first holes 21a and two second holes 42h are provided, and the inner circumferences are all the same. The first telescopic friction plate 21 and the inner column bracket 4 are releasably connected by inserting the first shear pin 8 at a position straddling the first hole 21a and the second hole 42h. Thus, the inner column bracket 4 is connected to each of the first telescopic friction plates 21 disposed on both sides of the inner column bracket 4.

  In order to releasably connect the inner column bracket 4 and the inner column 51, as shown in FIG. 10, a third hole 51h is opened in the inner column 51, and a fourth hole 43h is formed in the bottom of the recess 45 of the leg 43 Is open. The fourth hole 43h is disposed to overlap the third hole 51h. That is, the third hole 51 h and the fourth hole 43 h communicate with each other. For example, in the present embodiment, two third holes 51h and four fourth holes 43h are provided, and the inner circumferences are all the same, for example, more than the inner circumferences of the first holes 21a and the second holes 42h. large. By inserting the first shear pin 8 at a position straddling the third hole 51 h and the fourth hole 43 h, the inner column bracket 4 and the inner column 51 are connected in a detachable manner. The third holes 51 h and the fourth holes 43 h are arranged at equal positions from the first telescopic friction plates 21 arranged on both sides of the inner column bracket 4.

  In addition, the inner column bracket 4 is arranged such that at least a part thereof fits into the first slit 541 of the outer column 54. Specifically, the leg portion 43 of the inner column bracket 4 is fitted so as to face the inner wall of the first slit 541.

  The inner column bracket 4 can slide in a state facing the inner wall of the first slit 541 when telescopic adjustment is performed. The inner column bracket 4 regulates the adjustment range of the telescopic position by contacting the first end inner wall 541 e which is the inner wall of the front end of the first slit 541 when adjusting the telescopic position. Further, as shown in FIG. 9, 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 541 e. As a result, after the inner column bracket 4 is separated from the inner column 51, the forward movement amount (stroke amount) of the inner column 51 is ensured to be a predetermined amount or more. Therefore, in the present embodiment, the front limit of the telescopic position is restricted by the inner column bracket 4 and the first end inner wall 541e, and the rear limit of the telescopic position is restricted by the stopper 7 and the second end inner wall 542e. It is done.

  FIG. 15 is a cross-sectional view showing the periphery of the first shear pin in an enlarged manner. FIG. 16 is a view showing only the first shear pin in FIG. 15 as a side view. In the present embodiment, the first shear pin 8 includes an outer pin 81 and an inner pin 82. The outer pin 81 and the inner pin 82 are formed of, for example, a resin such as polyacetal.

  As shown in FIG. 15, the outer pin 81 is a cylindrical member which penetrates the first hole 21a and the second hole 42h. The outer pin 81 includes, for example, a main body portion 811, a retaining portion 812, a flange portion 813, and a guide hole 81 h. The main body portion 811 has a cylindrical shape and penetrates the first hole 21a and the second hole 42h. The retaining portion 812 is provided at one end of the main body portion 811 and is in contact with the edge of the second hole 42 h. The retaining portion 812 is cylindrical and has an outer periphery larger than the inner periphery of the first hole 21a and the inner periphery of the second hole 42h. Since the retaining portion 812 is hooked on the surface of the projecting portion 42, the outer pin 81 is less likely to come off from the first hole 21a and the second hole 42h. The flange portion 813 is provided at the other end of the main body portion 811 and is in contact with the edge of the first hole 21 a. The flange portion 813 has, for example, a disk shape, and has an outer periphery larger than the inner periphery of the first hole 21a and the inner periphery of the second hole 42h. Since the flange portion 813 is hooked on the surface of the first telescopic friction plate 21, the outer pin 81 is less likely to come off from the first hole 21a and the second hole 42h. The guide hole 81 h is a through hole penetrating from the flange portion 813 to the retaining portion 812.

  In the present embodiment, the outer pin 81 is inserted into the first hole 21a and the second hole 42h by press-fitting. The outer pin 81 is inserted into the first hole 21a and the second hole 42h, whereby the first hole 21a and the second hole 42h are positioned. For example, the retaining portion 812 is inserted into the first hole 21a and the second hole 42h from the first hole 21a side. The retaining portion 812 is formed such that the outer periphery of the end portion 81e opposite to the main body portion 811 is smaller than the inner periphery of the first hole 21a and the inner periphery of the second hole 42h. Thus, the retaining portion 812 can be easily inserted into the first hole 21a.

  The outer pin 81 may be inserted into the first hole 21a and the second hole 42h from the second hole 42h side. In addition, 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.

  As shown in FIG. 16, the outer pin 81 includes one notch 81 s provided from the retaining portion 812 toward the flange portion 813. When the retaining portion 812 is inserted into the second hole 42h, the width ds of the notch 81s in the circumferential direction of the outer pin 81 is reduced, and the outer periphery of the retaining portion 812 is reduced. Thereby, the securing portion 812 can easily pass through the first hole 21a and the second hole 42h. In the following description, the width ds of the notch 81s in the circumferential direction of the outer pin 81 is simply described as the width ds of the notch 81s.

  The outer pin 81 may have a plurality of notches 81s. When the notches 81 s are plural, it is preferable that the plural notches 81 s be arranged at equal intervals in the circumferential direction of the outer pin 81.

  Before the outer pin 81 penetrates the first hole 21a and the second hole 42h, the outer periphery of the main body portion 811 is larger than the inner periphery of the first hole 21a and the inner periphery of the second hole 42h. Then, in the state where the outer pin 81 penetrates the first hole 21a and the second hole 42h, the outer periphery of the main body portion 811 is the inner periphery of the first hole 21a and the second hole 42h by the main body portion 811 being deformed. It is equal to the inner circumference of. More specifically, the diameter of the main body portion 811 is a diameter D1 equal to the diameters of the first hole 21a and the second hole 42h. Thus, the main body portion 811 pushes the inner wall of the first hole 21a and the inner wall of the second hole 42h. For this reason, the gap between the main body 811 and the inner wall of the first hole 21a and the gap between the main body 811 and the inner wall of the second hole 42h are less likely to occur. Thereby, rattling of the outer pin 81 is suppressed.

  The inner pin 82 is a member inserted into the guide hole 81 h of the outer pin 81. The inner pin 82 includes, for example, a body portion 821 and a large diameter portion 822. The body portion 821 has a cylindrical shape and penetrates the guide hole 81 h. The large diameter portion 822 is provided at both ends of the body portion 821 and is located outside the guide hole 81 h. The large diameter portion 822 has an outer periphery larger than the inner periphery of the guide hole 81 h. As a result, since the large diameter portion 822 is in contact with the edges of both ends of the guide hole 81 h, the inner pin 82 is less likely to come off the outer pin 81.

  The guide hole 81 h may be provided with a stepped portion in which the inner periphery is enlarged 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 does not easily protrude from the end of the guide hole 81 h.

  In the present embodiment, the inner pin 82 is inserted into the guide hole 81 h by press fitting. For example, the large diameter portion 822 is inserted into the guide hole 81 h from the flange portion 813 side. The large diameter portion 822 is formed such that the outer periphery at the end 82 e opposite to the body portion 821 is smaller than the inner periphery of the outer pin 81. As a result, the large diameter portion 822 is easily inserted into the guide hole 81 h. Further, since the inner pin 82 has the same large diameter portion 822 at both ends, it can be inserted into the guide hole 81 h from either end. Thereby, the assembly of the first shear pin 8 is facilitated.

  Before the inner pin 82 is inserted into the guide hole 81 h, the outer periphery of the body 821 is larger than the inner periphery of the guide hole 81 h. Then, in a state where the body portion 821 penetrates the guide hole 81h, the outer periphery of the body portion 821 is equal to the inner periphery of the guide hole 81h by the deformation of the body portion 821. Thus, the body portion 821 pushes the inner wall of the guide hole 81 h radially outward. For this reason, a gap between the body portion 821 and the inner wall of the guide hole 81 h is less likely to occur. Thereby, rattling of the inner pin 82 is suppressed.

  When the body portion 821 pushes the inner wall of the guide hole 81 h radially outward, a force for expanding the width ds of the notch 81 s acts on the outer pin 81. Thereby, the frictional force generated between the outer pin 81 and the inner wall of the first hole 21a and the inner wall of the second hole 42h is increased. Furthermore, since the width ds of the notch 81s in the retaining portion 812 is increased, the outer periphery of the retaining portion 812 is increased. Therefore, the first shear pin 8 in which the outer pin 81 and the inner pin 82 are integrated is fixed at a position straddling the first hole 21a and the second hole 42h, and the first telescopic friction plate 21 and the inner column bracket 4 are fixed. It is connected.

  The steering device 100 can be easily assembled since the inner pin 82 is inserted and assembled after the first pin 21a and the second pin 42h are positioned by the outer pin 81.

  Further, the steering apparatus 100 according to the present embodiment is compared to the case where the resin member is filled in the first hole 21a and the second hole 42h by using the first shear pin 8 for the first hole 21a and the second hole 42h. This eliminates the need for an apparatus for filling the resin member and a member for receiving the resin member. For this reason, the steering apparatus 100 according to the present embodiment can be easily assembled.

  FIG. 17 is an enlarged cross-sectional view of the periphery of the second shear pin. FIG. 18 is a view showing only the second shear pin in FIG. 17 as a side view. In the present embodiment, the second shear pin 9 includes an outer pin 91 and an inner pin 92. The outer pin 91 and the inner pin 92 are made of, for example, a resin such as polyacetal.

  As shown in FIG. 17, the outer pin 91 is a cylindrical member penetrating the third hole 51 h and the fourth hole 43 h. The outer pin 91 includes, for example, a main body 911, a stopper 912, a flange 913, and a guide hole 91 h. The main body portion 911 is cylindrical and penetrates the third hole 51 h and the fourth hole 43 h. The retaining portion 912 is provided at one end of the main body 911 and is in contact with the edge of the third hole 51 h. The retaining portion 912 is cylindrical and has an outer periphery larger than the inner periphery of the third hole 51 h and the inner periphery of the fourth hole 43 h. Since the retaining portion 912 is caught on the inner wall of the inner column 51, the outer pin 91 is less likely to come off from the third hole 51h and the fourth hole 43h. The flange portion 913 is provided at the other end of the main body portion 911 and is in contact with the edge of the fourth hole 43 h. The flange portion 913 has, for example, a disk shape, and has an outer periphery larger than the inner periphery of the third hole 51 h and the inner periphery of the fourth hole 43 h. Since the flange portion 913 is hooked on the bottom of the recess 45, the outer pin 91 is less likely to come off from the third hole 51h and the fourth hole 43h. The guide hole 91 h is a through hole penetrating from the flange portion 913 to the retaining portion 912.

  In the present embodiment, the outer pin 91 is inserted into the third hole 51 h and the fourth hole 43 h by press-fitting. The outer pin 91 is inserted into the third hole 51 h and the fourth hole 43 h, whereby the third hole 51 h and the fourth hole 43 h are positioned. For example, the retaining portion 912 is inserted into the third hole 51 h and the fourth hole 43 h from the fourth hole 43 h side. The retaining portion 912 is formed such that the outer periphery at the end 91 e opposite to the main body 911 is smaller than the inner periphery of the third hole 51 h and the inner periphery of the fourth hole 43 h. Thereby, the securing portion 912 is easily inserted into the fourth hole 43 h.

  The outer pin 91 may be inserted into the third hole 51 h and the fourth hole 43 h from the third hole 51 h side. In addition, the outer pin 91 may be press-fitted after providing a rib or the like on the outer wall of the main body 911.

  As shown in FIG. 18, the outer pin 91 includes one notch 91 s provided from the retaining portion 912 toward the flange portion 913. When the retaining portion 912 is inserted into the fourth hole 43h, the width ds of the notch 91s in the circumferential direction of the outer pin 91 decreases, and the outer periphery of the retaining portion 912 decreases. Thereby, the securing portion 912 easily passes through the third hole 51 h and the fourth hole 43 h. In the following description, the width ds of the notch 91s in the circumferential direction of the outer pin 91 is simply described as the width ds of the notch 91s.

  The outer pin 91 may have a plurality of notches 91s. When the notches 91s are plural, it is preferable that the notches 91s be arranged at equal intervals in the circumferential direction of the outer pin 91.

  Before the outer pin 91 penetrates the third hole 51 h and the fourth hole 43 h, the outer periphery of the main body 911 is larger than the inner periphery of the third hole 51 h and the inner periphery of the fourth hole 43 h. Then, in a state where the outer pin 91 penetrates the third hole 51 h and the fourth hole 43 h, the outer periphery of the main body 911 is the inner periphery of the third hole 51 h and the fourth hole 43 h by the main body 911 being deformed. It is equal to the inner circumference of. More specifically, the diameter of the main body portion 911 is a diameter D2 equal to the diameters of the third hole 51h and the fourth hole 43h. The diameter D2 is larger than the diameter D1 of the first shear pin 8. Thus, the main body 911 pushes the inner wall of the third hole 51 h and the inner wall of the fourth hole 43 h. Therefore, the gap between the main body 911 and the inner wall of the third hole 51 h and the gap between the main body 911 and the inner wall of the fourth hole 43 h are less likely to occur. Thereby, rattling of the outer pin 91 is suppressed.

  The inner pin 92 is a member inserted into the guide hole 91 h of the outer pin 91. The inner pin 92 includes, for example, a body portion 921 and a large diameter portion 922. The body portion 921 has a cylindrical shape and penetrates the guide hole 91 h. The large diameter portion 922 is provided at both ends of the body portion 921 and is located outside the guide hole 91 h. The large diameter portion 922 has an outer periphery larger than the inner periphery of the guide hole 91 h. As a result, the large diameter portion 922 is in contact with the edges of both ends of the guide hole 91 h, so the inner pin 92 is unlikely to come off the outer pin 91.

  The guide hole 91 h may be provided with a stepped portion in which the inner periphery is enlarged at the end. In this case, since the large diameter portion 922 is in contact with the edge of the step portion, the inner pin 92 does not easily protrude from the end of the guide hole 91 h.

  In the present embodiment, the inner pin 92 is inserted into the guide hole 91 h by press fitting. For example, the large diameter portion 922 is inserted into the guide hole 91 h from the flange portion 913 side. The large diameter portion 922 is formed such that the outer periphery at the end 92 e opposite to the body portion 921 is smaller than the inner periphery of the outer pin 91. Thus, the large diameter portion 922 can be easily inserted into the guide hole 91 h. Further, since the inner pin 92 has the same large diameter portion 922 at both ends, it can be inserted into the guide hole 91 h from either end. This facilitates the assembly of the second shear pin 9.

  Before the inner pin 92 is inserted into the guide hole 91 h, the outer periphery of the body 921 is larger than the inner periphery of the guide hole 91 h. When the body portion 921 penetrates the guide hole 91h, the outer periphery of the body portion 921 is equal to the inner periphery of the guide hole 91h by the deformation of the body portion 921. Thus, the body portion 921 pushes the inner wall of the guide hole 91 h radially outward. For this reason, a gap between the body portion 921 and the inner wall of the guide hole 91 h is less likely to occur. Thereby, rattling of the inner pin 92 is suppressed.

  When the body portion 921 pushes the inner wall of the guide hole 91 h radially outward, a force for expanding the width ds of the notch 91 s acts on the outer pin 91. Thereby, the frictional force generated between the outer pin 91 and the inner wall of the third hole 51 h and the inner wall of the fourth hole 43 h is increased. Furthermore, since the width ds of the notch 91s in the retaining portion 912 is increased, the outer periphery of the retaining portion 912 is increased. For this reason, the second shear pin 9 in which the outer pin 91 and the inner pin 92 are integrated is fixed at a position straddling the third hole 51 h and the fourth hole 43 h and connects the inner column 51 and the inner column bracket 4. There is.

  The steering device 100 can be easily assembled because the inner pin 92 is inserted and assembled after the third hole 51 h and the fourth hole 43 h are positioned by the outer pin 91.

  Further, the steering apparatus 100 according to the present embodiment is compared to the case where the resin member is filled in the third hole 51 h and the fourth hole 43 h by using the second shear pin 9 in the third hole 51 h and the fourth hole 43 h. This eliminates the need for an apparatus for filling the resin member and a member for receiving the resin member. For this reason, the steering apparatus 100 according to the present embodiment can be easily assembled.

  As shown in FIG. 17, the depth d3 of the recess 45 is preferably equal to or greater than the length d4 of the portion of the second shear pin 9 that protrudes from the fourth hole 43h. As a result, the second shear pin 9 does not protrude beyond the surface of the inner column bracket 4. For this reason, the possibility that the second shear pin 9 may be damaged by an external force is reduced.

  In the present embodiment, the shear strength of the first shear pin 8 is lower than the shear strength of the second shear pin 9. More specifically, for example, the first shear pin 8 and the second shear pin 9 are formed of the same material, and the diameter D1 of the first shear pin 8 is smaller than the diameter D2 of the second shear pin 9. For this reason, the shear strength of one first shear pin 8 is lower than the shear strength of one second shear pin 9. Since two first shear pins 8 and two second shear pins 9 are provided in this embodiment, the sum of the shear strengths of the two first shear pins 8 is greater than the sum of the shear strengths of the two second shear pins 9. It's getting lower. Therefore, when the same load acts on the first shear pin 8 and the second shear pin 9, the first shear pin 8 is cut earlier than the second shear pin 9.

  The diameter D1 of the first shear pin 8 may not necessarily be smaller than the diameter D2 of the second shear pin 9. For example, the first shear pin 8 and the second shear pin 9 may have the same size, and the first shear pin 8 and the second shear pin 9 may be formed of different materials. That is, the sizes and materials of the first shear pin 8 and the second shear pin 9 may be appropriately adjusted so that the shear strength of the first shear pin 8 is lower than the shear strength of the second shear pin 9.

  The first shear pin 8 may not necessarily be configured of the outer pin 81 and the inner pin 82 described above. For example, the first shear pin 8 may be formed by solidification of a resin or the like filled at a position across the first hole 21a and the second hole 42h. In addition, the second shear pin 9 may not necessarily be configured by the outer pin 91 and the inner pin 92 described above. For example, the second shear pin 9 may be formed by solidification of a resin or the like filled at a position across the third hole 51 h and the fourth hole 43 h.

  The number of first holes 21a and the number of second holes 42h may be one or three or more. The number of third holes 51 h and the number of fourth holes 43 h may be one or three or more. The first shear pin 8 and the second shear pin 9 may be made of, for example, metal including non-ferrous metal such as aluminum alloy, rubber, plastic, wood or the like.

  When an excessive load is applied to the steering wheel 14, the load is transmitted to the inner column 51 via the input shaft 151 to move the inner column 51 forward. On the other hand, the first telescopic friction plate 21 does not move. Thereby, a shear force is applied to the first shear pin 8 and the second shear pin 9. As described above, the shear strength of the first shear pin 8 is lower than the shear strength of the second shear pin 9. Therefore, when the excessive load exceeds the allowable shear force of the first shear pin 8, the first shear pin 8 is cut. When the first shear pin 8 is cut, the connection between the inner column 51 and the first telescopic friction plate 21 is released. When the connection between the inner column 51 and the first telescopic friction plate 21 is released, the inner column 51 is axially supported by the frictional force generated between the inner column 51 and the outer column 54. . Therefore, when the operator collides with the steering hole 14 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.

  In addition, even if the first 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. In addition, the inner column 51 remains supported by the outer column 54. Therefore, even if the first shear pin 8 is cut, the steering column 5 does not fall.

  FIG. 19 is a bottom view showing the state of the first shear pin after it has been cut. FIG. 20 is a cross-sectional view showing the vicinity of the first shear pin after being cut. As shown in FIG. 19, when the first shear pin 8 is cut, the inner column 51 and the inner bracket 4 connected by the second shear pin 9 move forward. As shown in FIG. 20, the first shear pin 8 is cut at the cut surface BK1. The cut surface BK1 is generated at a portion of the first shear pin 8 straddling the first hole 21a and the second hole 42h. In the cross section shown in FIG. 20, the cut surface BK1 is located on the extension of the boundary between the first telescopic friction plate 21 and the projection 42. The outer pin 81 is cut at the main body portion 811, and the inner pin 82 is cut at the body portion 821. Therefore, the allowable shear force of the first 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 in the cut surface BK1.

  As shown in FIG. 16, it is preferable that the distance d1 from the flange portion 813 to the tip end 81sb of the notch 81s is larger than the distance d2 from the flange portion 813 to the projecting portion 42. Thereby, the notch 81s is not included in the cut surface BK1 when the first shear pin 8 is cut. For this reason, since the lack part for notch 81s is lose | eliminated in the cross section of the main-body part 811 in cut surface BK1, the dispersion of the allowable shear force of the 1st shear pin 8 is suppressed.

  In addition, after the first shear pin 8 is cut, it is desirable that the inner column 51 move straight in the axial direction. When the moving direction of the inner column 51 is a direction making an angle with 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 Is more likely to be larger than a predetermined value.

  In the present embodiment, the inner column bracket 4 is connected to the first telescopic friction plates 21 arranged on both sides of the inner column bracket 4 by the first shear pin 8 as shown in FIG. Thus, when an axial load is applied to the inner column bracket 4, the inner column bracket 4 receives a tightening force from both sides. Therefore, the posture of the inner column bracket 4 when the first shear pin 8 is cut is stabilized. Therefore, the posture when the inner column 51 starts to move tends to be kept straight in the axial direction. Thus, the inner column 51 can easily move straight in the axial direction.

  Further, even if the inner column bracket 4 can not receive the tightening force from both sides equally, the stopper 7 is fitted in the second slit 542, so the inner column 51 The two slits 542 are guided longitudinally or axially. Therefore, the posture of the inner column bracket 4 when the first shear pin 8 is cut is stabilized.

  FIG. 21 is an enlarged cross-sectional view of the periphery of the second shear pin after being cut. As shown in FIG. 21, when the inner column 51 and the inner column bracket 4 move forward, the damper 10 provided on the inner column bracket 4 contacts the first end inner wall 541e. As a result, the movement of the inner column bracket 4 is restricted while the inner column 51 is further moved forward, so that a shearing force is applied to the second shear pin 9. If the shear force applied to the second shear pin 9 exceeds the allowable shear force of the second shear pin 9, the second shear pin 9 is cut. When the second shear pin 9 is cut, the connection between the inner column 51 and the inner column bracket 4 is released.

  As shown in FIG. 21, the second shear pin 9 is cut at the cut surface BK2. The cut surface BK2 is generated in a portion of the second shear pin 9 straddling the third hole 51 h and the fourth hole 43 h. In the cross section shown in FIG. 21, the cut surface BK2 is located on the extension of the outer wall of the inner column 51, that is, the extension of the inner column side surface 431 of the leg 43. The outer pin 91 is cut by the main body 911, and the inner pin 92 is cut by the body 921. Therefore, the allowable shear force of the second shear pin 9 depends on the cross-sectional area of the main body 911 and the cross-sectional area of the body 921 in the cut surface BK2.

  As shown in FIG. 18, it is preferable that the distance d5 from the flange portion 913 to the tip end 91sb of the notch 91s is larger than the distance d6 from the flange portion 913 to the outer wall of the inner column 51. Thereby, the notch 91s is not included in the cut surface BK2 when the second shear pin 9 is cut. For this reason, since the loss part for notch 91s is lose | eliminated in the cross section of the main-body part 911 in cut surface BK2, the dispersion of the allowable shear force of the 2nd shear pin 9 is suppressed.

  In addition, after the second shear pin 9 is cut, it is desirable that the inner column 51 move straight in the axial direction. When the moving direction of the inner column 51 is a direction making an angle with 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 Is more likely to be larger than a predetermined value.

  As shown in FIG. 10, the third holes 51h and the fourth holes 43h are provided at two different positions in the axial direction. Therefore, two second shear pins 9 are disposed at different positions in the axial direction. If one third hole 51 h and one fourth hole 43 h are provided, that is, one second shear pin 9 is arranged, the inner column bracket 4 can rotate about the second shear pin 9. There is sex. On the other hand, in the present embodiment, the rotation of the inner column bracket 4 is suppressed by arranging two second shear pins 9 at different positions in the axial direction. Therefore, the posture of the inner column bracket 4 when the second shear pin 9 is cut is stabilized.

  FIG. 22 is a graph showing the relationship between the displacement amount of the steering column and the load required to move the steering column in the comparative example. FIG. 23 is a diagram showing the relationship between the displacement amount of the steering column and the load required to move the steering column in the present embodiment. 22 and 23, the horizontal axis represents the amount of displacement of the steering column forward, and the vertical axis represents the load required to move the steering column forward.

  A comparative example is an example in case an outer column is attached to a vehicle body via a capsule like the technique of patent document 1. As shown in FIG. In the comparative example, the outer column is disposed rearward 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 force F2c shown in FIG. 22 indicates the allowable shear force of the capsule.

  In the comparative example, the outer column is axially supported by the frictional force generated with the inner column by the tightening of the bracket. A force F1c shown in FIG. 22 indicates the frictional force supporting the outer column. Force F1c is smaller than force F2c. In order to prevent the outer column from moving due to the load applied in 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 movement of the outer column smooth to make the operator more easily protected from the secondary collision.

  On the other hand, in the present 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. It is axially supported by a second friction force generated between (the outer column bracket 52, the second telescopic friction plate 22, and the outer column 54). The force F1 shown in FIG. 23 indicates a first friction force, and the force F3 indicates the sum of the first friction force and the second friction force. Further, a force F21 shown in FIG. 23 indicates the allowable shear force of the first shear pin 8. Force F21 is smaller than force F3 and larger than force F1. The force F22 indicates the allowable shear force of the second shear pin 9. Force F22 is smaller than force F3 and larger than force F21.

  In the present embodiment, when a load of force F21 or more is applied to the inner column 51, the first shear pin 8 is cut and the inner column bracket 4 is separated from the first telescopic friction plate 21. As a result, since the connection between the inner column bracket 4 and the first telescopic friction plate 21 is released, the above-mentioned second frictional force does not act on the inner column 51. For this reason, after the first shear pin 8 is cut, the inner column 51 moves in the axial direction while absorbing an impact by the above-described first frictional force. In the steering apparatus 100 according to the present embodiment, when the first frictional force is set small, the movement of the inner column 51 can be smoothed to make it easier to 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 complements the portion of the force for supporting the inner column 51 in the axial direction by reducing the first frictional force. can do. For this reason, the steering apparatus 100 according to the present embodiment moves the inner column 51 by a load applied in normal use by adjusting the set value of the first frictional force and the set value of the second frictional force. It can be suppressed and it is easier to protect the operator from secondary collisions.

  Furthermore, after the first shear pin 8 is cut, if a load of force F22 or more is applied to the inner column 51 with the damper 10 in contact with the first end inner wall 541e, the second shear pin 9 is cut. At this time, since the impact energy is consumed to cut the second shear pin 9, the impact is absorbed. That is, the impact is absorbed in two stages by cutting the first shear pin 8 and the second shear pin 9 at different timings. Therefore, the steering device 100 can more easily protect the operator from the secondary collision.

  The second share pin 9 may be disconnected before the first share pin 8 is disconnected. Alternatively, the first shear pin 8 and the second shear pin 9 may be cut almost simultaneously. For example, when a secondary collision occurs in a state where the telescopic position is adjusted most toward the front, the damper 10 is already in contact with the first end inner wall 541 e, so the first shear pin 8 and the second shear pin 9 are substantially It is cut at the same time. Even in these cases, the inner column bracket 4 separates from the first telescopic friction plate 21 at the time of a secondary collision. However, it is preferable that the first shear pin 8 be cut prior to the second shear pin 9 in that the impact is easily absorbed.

  By the way, when performing telescopic adjustment after operating the operation lever 53 in normal use, a shear force acts on the first shear pin 8 when the inner column bracket 4 contacts the first end inner wall 541 e. For this reason, when the force applied to the inner column 51 at the time of telescopic adjustment is excessive, the first shear pin 8 may be cut off by the telescopic adjustment. Therefore, the steering device 100 according to the present embodiment includes the damper 10 as described above. As shown in FIG. 10, the damper 10 is made of, for example, synthetic rubber, and is attached to the front end of the inner column bracket 4. More specifically, the damper 10 is fixed to the inner column bracket 4 through the through hole 47 of the inner column bracket 4.

  When performing telescopic adjustment after operating the operation lever 53, the damper 10 contacts the first end inner wall 541e when the telescopic position is at the foremost position. When a force is applied to the inner column 51 in a state where the damper 10 is in contact with the first end inner wall 541 e, a reaction force from the first end inner wall 541 e is applied to the damper 10. Thereby, since the damper 10 is deformed, a part of the force applied to the damper 10 is consumed to deform the damper 10. Then, a force smaller than the force applied to the damper 10 is transmitted to the inner column bracket 4, and a shear force having a magnitude substantially equal to the force transmitted to the inner column bracket 4 acts on the first shear pin 8. For this reason, the shear force acting on the first shear pin 8 is smaller than the force applied to the inner column 51. Therefore, the steering device 100 according to the present embodiment can suppress the disconnection of the first shear pin 8 when performing telescopic adjustment, and can protect the detachment mechanism.

  As described above, the steering apparatus 100 according to the present embodiment includes the inner column 51, the outer column 54, the outer column bracket 52, the rod 33, the inner column bracket 4, the first shear pin 8, and the second shear pin And 9. The inner column 51 is a cylindrical member rotatably supporting the input shaft 151 connected to the steering wheel 14. The outer column 54 has a tubular shape in 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 away. The outer column bracket 52 is fixed to the vehicle body side member 13, supports the outer column 54, and clamps the outer column 54 together with a telescopic friction plate (first telescopic friction plate 21) which is a plate material. The rod 33 penetrates the telescopic friction plate (first telescopic friction plate 21) and the outer column bracket 52, and supports the telescopic friction plate (first telescopic friction plate 21). The inner column bracket 4 is disposed to face the inner column 51 exposed by the first slit 541 and the telescopic friction plate (first telescopic friction plate 21). The first shear pin 8 releasably connects the telescopic friction plate (first telescopic friction plate 21) and the inner column bracket 4. The second share pin 9 releasably connects the inner column 51 and the inner column bracket 4.

  Thus, in the steering apparatus 100 according to the present embodiment, when an excessive load is applied to the steering wheel 14, the load is transmitted to the inner column 51 via the input shaft 151 to move the inner column 51 forward. . On the other hand, the first telescopic friction plate 21 does not move. Thereby, a shear force is applied to the first shear pin 8 and the second shear pin 9. Therefore, when the excessive load exceeds the allowable shear force of the first shear pin 8 or the second shear pin 9, the first shear pin 8 or the second shear pin 9 is cut. When the first shear pin 8 or the second shear pin 9 is cut, the connection between the inner column 51 and the first telescopic friction plate 21 is released. When the connection between the inner column 51 and the first telescopic friction plate 21 is released, the inner column 51 is axially supported by the frictional force generated between the inner column 51 and the outer column 54. . Therefore, the inner column 51 of the steering column 5 can be moved forward. In addition, even if the first shear pin 8 or the second shear pin 9 is cut, the outer column 54 remains supported by the outer column bracket 52 fixed to the vehicle body side member 13. In addition, the inner column 51 remains supported by the outer column 54. Therefore, even if the first shear pin 8 or the second shear pin 9 is disconnected, the steering column 5 does not fall. Therefore, the steering apparatus 100 according to the present embodiment does not cause the steering column 5 to malfunction even if the set value (the allowable shear force of the first shear pin 8 or the second shear pin 9) of the separation load at which the steering column 5 moves forward is lowered. Can control the fall of the

  In the steering apparatus 100 according to the present embodiment, a first hole 21a is opened in the telescopic friction plate (first telescopic friction plate 21). In the inner column bracket 4, a second hole 42h to be overlapped with the first hole 21a is opened. The first shear pin 8 is inserted at a position straddling the first hole 21a and the second hole 42h.

  Thus, the first shear pin 21 is inserted into the first hole 21a and the second hole 42h, whereby the first telescopic friction plate 21 and the inner column bracket 4 are connected. Thus, the steering device 100 can be easily assembled.

  In the steering device 100 according to the present embodiment, a third hole 51 h is opened in the inner column 51. In the inner column bracket 4, a fourth hole 43h to be overlapped with the third hole 51h is opened. The second shear pin 9 is inserted at a position straddling the third hole 51 h and the fourth hole 43 h.

  Thereby, the inner column 51 and the inner column bracket 4 are connected by inserting the second shear pin 9 into the third hole 51 h and the fourth hole 43 h. Thus, the steering device 100 can be easily assembled.

  In the steering device 100 according to the present embodiment, the shear strength of the first shear pin 8 is lower than the shear strength of the second shear pin 9.

  Thereby, at the time of a secondary collision, the first shear pin 8 is cut before the second shear pin 9 is cut. For this reason, in the steering apparatus 100, since the set value of the separation load is adjusted by adjusting the shear strength of the first shear pin 8, setting of the separation load is easy.

  In the steering device 100 according to the present embodiment, the telescopic friction plates (the first telescopic friction plates 21) are disposed on both sides of the inner column bracket 4. The inner column bracket 4 is connected to the respective telescopic friction plates (first telescopic friction plate 21) disposed on both sides of the inner column bracket 4 by a plurality of first shear pins 8.

  As a result, when a load is applied to the inner column bracket 4, the inner column bracket 4 receives a tightening force from both sides, so the posture of the inner column bracket 4 when the first shear pin 8 is cut is stabilized. Therefore, the posture when the inner column 51 starts to move can be more easily kept straight in the axial direction. Therefore, the inner column 51 is easily moved straight in the axial direction, so that the movement of the inner column 51 is impeded or the frictional force generated between the inner column 51 and the outer column 54 becomes larger than a predetermined value. Is suppressed.

12, 13 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 21a First hole 22 Second telescopic friction plate 31 Rod penetrating portion 33 Rod 4 Inner column bracket 41 Arm portion 42 Projection portion 42 h Second hole 43 Leg portion 43 h Fourth hole 5 Steering column 51 Inner column 51 h Third 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 7 stopper 8 first shear pin 81 outer pin 82 inner pin 9 second shear pin 91 outer pin 92 Inner pin BK1, BK2 cut surface VB body

Claims (5)

A cylindrical inner column rotatably supporting an input shaft connected to the steering wheel;
An outer column having a cylindrical shape in which at least a part of the inner column is inserted inside, and having a slit in which one end on the insertion side of the inner column is cut out;
An outer column bracket fixed to a vehicle body side member, supporting the outer column, and tightening the outer column together with a telescopic friction plate which is a plate material;
A rod which penetrates the telescopic friction plate and the outer column bracket and supports the telescopic friction plate;
The inner column exposed by the slit and an inner column bracket disposed to face the telescopic friction plate;
A first shear pin that releasably connects the telescopic friction plate and the inner column bracket;
A second shear pin that releasably connects the inner column and the inner column bracket;
A steering apparatus comprising: A first hole is opened in the telescopic friction plate,
The inner column bracket is provided with a second hole overlapping the first hole,
The steering apparatus according to claim 1, wherein the first shear pin is inserted at a position straddling the first hole and the second hole. A third hole is opened in the inner column,
The inner column bracket is provided with a fourth hole to be overlapped with the third hole,
The steering apparatus according to claim 1, wherein the second shear pin is inserted at a position straddling the third hole and the fourth hole.   The steering apparatus according to any one of claims 1 to 3, wherein a shear strength of the first shear pin is lower than a shear strength of the second shear pin. The telescopic friction plates are disposed on both sides of the inner column bracket,
The inner column bracket is connected to each of the telescopic friction plates disposed on both sides of the inner column bracket by a plurality of first shear pins. Steering device as described.

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