Mounting structure for vibration damping member to balance spring and steering column device

Abstract

To provide a mounting structure for a damping member on a balance spring whereby the damping member can be mounted on the balance spring even in a case where the number of winds of a coil portion is small.SOLUTION: A balance spring 8 has a coil portion 35a and a pair of spring arm portions 36a and 36b, and a damping member 9a is configured to be elastically deformable and have an annular shape in a free state. Each of the pair of spring arm portions 36a and 36b is inserted through an inner side of the damping member 9a. In addition, the damping member 9a is attached to the balance spring 8 in a state in which a crossing portion 43 that is an obstruction portion, which is provided between portions of the damping member 9a through which the pair of spring arm portions 36a and 36b are inserted and which obstructs the passage of the coil portion 35a through the inner side of the damping member 9a, is disposed on a radially outer side of the coil portion 35a.SELECTED DRAWING: Figure 5

Description

[Technical Field]

[0001] The present invention relates to a mounting structure for a vibration damping member to a balance spring and a steering column device. [Background technology]

[0002] 2. Description of the Related Art A steering column device for an automobile incorporates a steering wheel position adjustment device that allows the vertical position and the front-rear position of the steering wheel to be adjusted in accordance with the driver's physique and driving posture.

[0003] 12 and 13 show an example of a steering column device equipped with a steering wheel position adjustment device, which is described in Japanese Patent Laid-Open Publication No. 2008-265647 (Patent Document 1).

[0004] A steering shaft 100 is rotatably supported inside a steering column 101. A steering wheel 102 is fixed to the rear end of the steering shaft 100. The steering shaft 100 has a configuration in which a lower shaft 103 disposed at the front and an upper shaft 104 disposed at the rear are combined by spline engagement or the like to enable torque transmission and extension / contraction, so as to enable adjustment of the fore-and-aft position of the steering wheel 102. Note that the fore-and-aft direction means the fore-and-aft direction of the vehicle, the up-and-down direction means the up-and-down direction of the vehicle, and the width direction means the width direction of the vehicle.

[0005] The steering column 101 has a generally cylindrical shape and is supported relative to the vehicle body. To enable adjustment of the fore-and-aft position of the steering wheel 102, the steering column 101 is configured so that the front side of an upper column 106 located at the rear is loosely fitted to the rear side of a lower column 105 located at the front to allow relative displacement in the axial direction, making the entire length of the steering column 101 extendable and contractible.

[0006] A column-side bracket 108 consisting of a pair of clamped plate portions 107 is provided on the front side of the upper column 106. The column-side bracket 108 is clamped from both widthwise sides by a pair of support plate portions 110 provided on a vehicle-side bracket 109 supported on the vehicle body. An adjustment rod 113 is inserted widthwise through a column-side through-hole 111 that passes through each of the pair of clamped plate portions 107, and through a vehicle-side through-hole 112 that passes through each of the pair of support plate portions 110. In the conventional structure described in JP 2008-265647 A, the column-side through-hole 111 is an elongated hole that extends in the front-rear direction to enable adjustment of the fore-aft position of the steering wheel 102, and the vehicle-side through-hole 112 is an elongated hole that extends in the up-down direction to enable adjustment of the up-down position of the steering wheel 102.

[0007] An anchor portion (head portion) 114 is provided at the base end of the adjustment rod 113, and a retaining member (nut) 115 is attached to the tip end of the adjustment rod 113. A cam device 116 and an adjustment lever 117 are provided between the retaining member 115 and the support plate portion 110 on one side in the width direction (the left side in Figure 13).

[0008] The cam device 116 comprises a movable cam 118 and a fixed cam 119. The movable cam 118 is fitted onto the adjustment rod 113 and has a movable cam surface, which is an uneven surface in the circumferential direction, on its inner surface in the width direction of the vehicle body (the right side in FIG. 13). The fixed cam 119 is supported so as not to rotate relative to the support plate portion 110 on one side in the width direction and has a fixed cam surface, which is an uneven surface in the circumferential direction, on its outer surface in the width direction of the vehicle body (the left side in FIG. 13) that faces the movable cam surface. The adjustment lever 117 has its base fixed to the movable cam 118 so as not to rotate relative to it. The cam device 116 rotates the movable cam 118 relative to the fixed cam 119 based on operation of the adjustment lever 117, thereby changing the rotational phase between the movable cam surface and the fixed cam surface and expanding / reducing the width dimension. This increases or decreases the distance between the pair of support plate portions 110, thereby adjusting the magnitude of the force that clamps the pair of clamped plate portions 107.

[0009] In an unlocked state of the cam device 116, in which the widthwise dimension of the cam device 116 is reduced and the force with which the pair of support plate portions 110 clamp the pair of clamped plate portions 107 is reduced, the position of the steering wheel 102 can be adjusted within the range in which the adjustment rod 113 can be displaced inside the column-side through-hole 111 and the vehicle-body-side through-hole 112. In contrast, in a locked state of the cam device 116, in which the widthwise dimension of the cam device 116 is expanded and the force with which the pair of support plate portions 110 clamp the pair of clamped plate portions 107 is increased, the steering wheel 102 can be maintained in the adjusted position.

[0010] In the conventional structure described in JP 2008-265647 A, a balance spring 120 is provided to prevent the steering column 101 and the steering wheel 102 from dropping downward forcefully due to their own weight when the cam device 116 is in the unlocked state.

[0011] The balance spring 120 is a coil spring (torsion spring) made up of a coil portion 121 and a pair of spring arms 122a, 122b. The balance spring 120 is attached between the adjustment rod 113 and the vehicle body-side bracket 109 by engaging one spring arm 122a of the pair of spring arms 122a, 122b with an anchor portion 114 of the adjustment rod 113 and the other spring arm 122b with the vehicle body-side bracket 109. The balance spring 120 applies an upward elastic force to the steering column 101 via the adjustment rod 113. This prevents the steering column 101 and the steering wheel 102 from falling forcefully downward due to their own weight when the cam device 116 is unlocked to adjust the position of the steering wheel 102.

[0012] In addition, in the conventional structure described in JP 2008-265647 A, a cylindrical vibration-damping member 123 is fitted onto the coil portion 121 that constitutes the balance spring 120. This suppresses the resonance of the balance spring 120 and prevents abnormal noise. [Prior art documents] [Patent documents]

[0013] [Patent Document 1] Japanese Patent Application Laid-Open No. 2008-265647 Summary of the Invention [Problem to be solved by the invention]

[0014] In the conventional structure described in JP 2008-265647 A, the coil portion 121 constituting the balance spring 120 has a relatively large number of turns (three turns in the illustrated example), and the axial dimension of the coil portion 121 is relatively large. Therefore, a vibration-damping member 123 for suppressing resonance of the balance spring 120 can be attached to the coil portion 121 by fitting.

[0015] However, if the number of turns of the coil portion constituting the balance spring is small, for example, one or two turns, the axial dimension of the coil portion becomes short, making it difficult to attach the vibration-damping member to the coil portion by fitting it.

[0016] The present invention has been made to solve the above-mentioned problems, and aims to provide a mounting structure for a vibration-damping member to a balance spring, which allows the vibration-damping member to be attached to the balance spring even when the number of turns of the coil portion that makes up the balance spring is small. [Means for solving the problem]

[0017] The mounting structure of a vibration damping member to a balance spring of the present invention relates to a mounting structure of a vibration damping member to a balance spring for applying elastic force to a steering column.

[0018] In a first aspect of the mounting structure for a vibration damping member to a balance spring of the present invention, the balance spring has a coil portion and a pair of spring arms extending from the coil portion. The vibration-damping member is elastically deformable and has an annular shape in a free state. In a first aspect of the mounting structure of the present invention, the vibration-damping member is attached to the balance spring with each of the pair of spring arms inserted inside the vibration-damping member, and an obstacle portion that prevents the coil portion from passing inside the vibration-damping member, located between the portions of the vibration-damping member through which the pair of spring arms are inserted, is positioned radially outside the coil portion.

[0019] In a first aspect of the mounting structure of the present invention, each of the pair of spring arms can be inserted into the inside of an annular insertion ring portion formed by torsional deformation of the vibration-damping member, and the obstruction portion can be an intersection portion formed by torsional deformation of the vibration-damping member. In this case, the intersection may be a torsional intersection formed by twisting the vibration-damping member through 360° or more.

[0020] In a second aspect of the structure for mounting a vibration damping member to a balance spring according to the present invention, the balance spring has a coil portion and a pair of spring arms extending from the coil portion. The vibration-damping member is elastically deformable and has an annular shape in a free state. In a second aspect of the mounting structure of the present invention, the vibration-damping member is attached to the balance spring with each of the pair of spring arms inserted inside the vibration-damping member, and the intermediate portion of the vibration-damping member between the portions through which the pair of spring arms are inserted is inserted radially inside the coil portion.

[0021] In a third aspect of the mounting structure for a vibration-damping member to a balance spring of the present invention, the balance spring comprises a pair of coil spring portions, each of which has a coil portion and a pair of spring arms extending from the coil portion, and a connecting portion that connects one of the spring arms provided on each of the pair of coil spring portions. The vibration-damping member is elastically deformable and has an annular shape in a free state. In a third aspect of the mounting structure of the present invention, the vibration-damping member is attached to the balance spring in such a manner that the other spring arm portion of each of the pair of coil spring portions is inserted inside the vibration-damping member, and the intermediate portion of the vibration-damping member between the portion through which the other spring arm portion of the pair is inserted is inserted radially inside the coil portion of each of the pair of coil spring portions.

[0022] In the third aspect of the mounting structure of the present invention, the intermediate portion of the vibration-damping member can be wrapped around the connecting portion.

[0023] In the mounting structure of the present invention, in any of the first, second and third aspects, the number of turns of the coil portion can be set to 2 or less. Alternatively, in the mounting structure of the present invention, the number of turns of the coil portion can be set to three or more.

[0024] The steering column device of the present invention includes a steering column, a vehicle body side bracket, an adjusting rod, a balance spring, and a vibration damping member. The steering column is provided with a column-side bracket having a column-side through-hole passing through in the width direction. The vehicle body side bracket is provided with a pair of support plate portions that are arranged on both widthwise sides of the column side bracket and each have a vehicle body side through-hole that penetrates in the widthwise direction and extends in the vertical direction. The adjustment rod is inserted in the width direction through the column-side through-hole and the pair of vehicle-body-side through-holes. The balance spring is supported by the vehicle body-side bracket and applies an upward elastic force to the steering column. The vibration damping member is attached to the balance spring and suppresses resonance of the balance spring. In the steering column device of the present invention, the vibration damping member is attached to the balance spring by the attachment structure of the present invention for attaching the vibration damping member to the balance spring. [Effects of the Invention]

[0025] According to the present invention, it is possible to realize a structure for attaching a vibration-damping member to a balance spring, which allows the vibration-damping member to be attached to the balance spring even when the number of turns of the coil portion constituting the balance spring is small. [Brief explanation of the drawings]

[0026] [Figure 1] FIG. 1 is a perspective view showing a steering column device according to a first example of an embodiment, as viewed from the front and bottom. [Figure 2] FIG. 2 is a perspective view showing a state in which a middle portion in the front-rear direction of a steering column device according to a first example of the embodiment is viewed from the front and bottom. [Figure 3] FIG. 3 is a cross-sectional schematic view of a steering column device according to a first example of the embodiment at a middle portion in the front-rear direction. [Figure 4] 4A and 4B are schematic diagrams showing a vibration damping member taken out of a steering column device according to a first example of an embodiment, where (A) is a diagram in a free state and (B) is a diagram after torsional deformation. [Figure 5] FIG. 5 is a perspective view showing the balance spring with the vibration damping member attached, taken out from the steering column device according to the first example of the embodiment. [Figure 6] FIG. 6 is a diagram corresponding to FIG. 5 and shows a second example of the embodiment. [Figure 7] FIG. 7 is a diagram corresponding to FIG. 5 and shows a third example of the embodiment. [Figure 8] FIG. 8 is a diagram corresponding to FIG. 5 and shows a fourth example of the embodiment. [Figure 9] FIG. 9 is a diagram corresponding to FIG. 5 and shows a fifth example of the embodiment. [Figure 10] FIG. 10 is a diagram corresponding to FIG. 5, showing a reference example according to the present invention. [Figure 11] FIG. 11 is a schematic diagram showing a vibration damping member according to a reference example of the present invention in a free state. [Figure 12]FIG. 12 is a side view showing a steering column device of a conventional structure. [Figure 13] FIG. 13 is a cross-sectional view taken along line AA in FIG. DETAILED DESCRIPTION OF THE INVENTION

[0027] [First example of embodiment] A first example of the embodiment will be described with reference to FIGS. The steering column device 1 of this example is for rotatably supporting a steering shaft 2 with respect to a vehicle body, and is equipped with a position adjustment mechanism (tilt / telescopic mechanism) that can adjust the vertical and longitudinal positions of the steering wheel. In the following description, the longitudinal direction means the longitudinal direction of the vehicle body to which the steering column device 1 is mounted, the vertical direction means the vertical direction of the vehicle body, and the width direction means the width direction of the vehicle body. Furthermore, one side in the width direction means the left side in FIG. 3, and the other side in the width direction means the right side in FIG. 3. Furthermore, the outer side in the width direction means both left and right sides in FIG. 3, and the inner side in the width direction means the center side in the left and right directions in FIG. 3.

[0028] In the steering column device 1 of this example, in order to enable adjustment of the fore-aft position of the steering wheel, the steering shaft 2 is configured by combining a lower shaft 3 located at the front and an upper shaft 4 located at the rear, which are capable of transmitting torque and being extendable and contractible, using spline engagement or the like.

[0029] The steering column device 1 includes a steering column 5, a vehicle body side bracket 6, an adjustment rod 7, a balance spring 8, and a pair of vibration damping members 9a and 9b.

[0030] <Steering column> The steering column 5 has a generally cylindrical shape and is supported relative to the vehicle body with its axial direction facing the front-to-rear direction. To enable adjustment of the fore-and-aft position of the steering wheel, the steering column 5 is configured so that the rear side of an inner column 10, which is a lower column located at the front, and the front side of an outer column 11, which is an upper column located at the rear, are loosely fitted together to allow relative displacement in the axial direction, making the entire length extendable. A steering shaft 2 is rotatably supported inside the steering column 5 via multiple rolling bearings.

[0031] "Innacolumn" The inner column 10 is made of metal such as an iron-based alloy or an aluminum-based alloy. The inner column 10 has a cylindrical shape as a whole. A lower bracket 12 is fixed to the front side of the inner column 10. The lower bracket 12 is supported so as to be able to swing about a tilt shaft 13 arranged in the width direction relative to a vehicle body (not shown).

[0032] Outer Column The outer column 11 is made of metal such as an iron-based alloy or an aluminum-based alloy, and is configured to be cylindrical overall. The front end of the outer column 11 is supported by a vehicle body side bracket 6 that is supported so as to be able to be detached forward from the vehicle body. The outer column 11 has a slit 14 and a column side bracket 15.

[0033] The slit 14 is intended to enable the inner diameter of the front part of the outer column 11 to be expanded or contracted, and extends in the axial direction of the outer column 11. The slit 14 is provided from the middle part in the front-to-rear direction of the underside of the outer column 11 to the front end part. The slit 14 opens to each of the inner circumferential surface and outer circumferential surface of the outer column 11, and also opens to the front end face of the outer column 11.

[0034] The column side bracket 15 is provided at the front end of the outer column 11. The column side bracket 15 is composed of a pair of clamped plate portions 16a, 16b arranged on both sides of the slit 14 in the width direction. The pair of clamped plate portions 16a, 16b are configured in a generally flat plate shape. The pair of clamped plate portions 16a, 16b extend in the up-down direction and are arranged spaced apart in the width direction. Column side through holes 17a, 17b that penetrate in the width direction are formed in the pair of clamped plate portions 16a, 16b at portions that align with each other. In other words, the pair of column side through holes 17a, 17b are aligned in the front-to-rear and up-to-down positions. The column side through holes 17a, 17b are elongated holes that extend in the front-to-rear direction. Note that if a telescopic mechanism is not provided, the column side through holes are simply circular holes.

[0035] <Body side bracket> The vehicle body side bracket 6 supports the front portion of the outer column 11 relative to the vehicle body in a manner that allows it to switch between an unclamped state in which the up-down position and fore-aft position of the steering wheel can be adjusted, and a clamped state in which the steering wheel is held in the adjusted position. The vehicle body side bracket 6 is made of a metal plate that has sufficient rigidity, such as steel or an aluminum alloy, and has a pair of support plate portions 18a, 18b, a top plate portion 19, and a pair of front plate portions 20a, 20b, as shown in Figure 3.

[0036] The pair of support plate portions 18a, 18b are arranged on both widthwise sides of the pair of clamped plate portions 16a, 16b that constitute the column-side bracket 15. The pair of support plate portions 18a, 18b are configured in a generally flat plate shape. The pair of support plate portions 18a, 18b extend in the up-down direction and are arranged spaced apart in the widthwise direction. Vehicle-body-side through holes 21a, 21b that penetrate in the widthwise direction are formed in the pair of support plate portions 18a, 18b at portions that align with each other. The vehicle-body-side through holes 21a, 21b are elongated holes that extend in the up-down direction. Specifically, for example, each of the vehicle-body-side through holes 21a, 21b is an elongated hole that extends in an arc direction centered on the tilt axis 13.

[0037] The top plate portion 19 is disposed above the steering column 5. The upper ends of a pair of support plate portions 18a, 18b are fixed to the underside of the top plate portion 19 by welding or the like. The top plate portion 19 is provided with a plurality of cutouts 22 that are open at their rear ends. The top plate portion 19 is supported by capsules 23 engaged with the cutouts 22 so that it can be detached forward from the vehicle body.

[0038] The pair of front plate portions 20a, 20b are provided at a widthwise distance from each other at the front end of the top plate portion 19. The pair of front plate portions 20a, 20b hang down from the front end of the top plate portion 19. The lower end of each of the pair of front plate portions 20a, 20b is provided with bracket-side locking portions 24a, 24b having a generally J-shape.

[0039] <Adjustment rod> The adjustment rod 7 is arranged with its axial direction oriented in the width direction so that the force with which the pair of support plates 18a, 18b tighten the pair of clamped plates 16a, 16b can be adjusted, and is inserted in the width direction through the pair of column-side through-holes 17a, 17b and the pair of vehicle-body-side through-holes 21a, 21b. The overall length of the adjustment rod 7 is longer than the distance between the outer surfaces of the pair of support plates 18a, 18b. The adjustment rod 7 has an anchor portion 25 such as a head at one end in the width direction (the left side in FIG. 3) and a male thread portion 26 at the other end in the width direction (the right side in FIG. 3).

[0040] An adjustment lever 27 and a cam device 28 are arranged, in order from the outside in the width direction, around a portion of the adjustment rod 7 that protrudes in the width direction from the outer surface of the support plate portion 18a located on one side in the width direction. In other words, the adjustment lever 27 and the cam device 28 are arranged between the inner surface of the anchor portion 25 and the outer surface of the support plate portion 18a in the width direction. A nut 29 and a thrust bearing 30 are arranged, in order from the outside in the width direction, around a portion of the adjustment rod 7 that protrudes in the width direction from the outer surface of the support plate portion 18b located on the other side in the width direction. The nut 29 is threaded onto the male thread portion 26 of the adjustment rod 7.

[0041] The cam device 28 is an expansion / contraction device and has a movable cam 31 arranged on the outside in the width direction and a fixed cam 32 arranged on the inside in the width direction. The movable cam 31 is made of sintered metal and has a movable cam surface that is an uneven surface in the circumferential direction on its inner surface in the width direction of the vehicle body. The movable cam 31 is fixed to the base of the adjustment lever 27 and rotates back and forth in conjunction with the reciprocating swing of the adjustment lever 27. The base of the adjustment lever 27 and the movable cam 31 can be fixed to the adjustment rod 7 so as to rotate integrally with the adjustment rod 7, or can be fitted externally to the adjustment rod 7 so as to be rotatable relative to the adjustment rod 7.

[0042] The fixed-side cam 32 is made of sintered metal and has a fixed-side cam surface that is an uneven surface in the circumferential direction on its outer surface in the width direction of the vehicle body, and a generally rectangular engaging protrusion that protrudes inward in the width direction on its inner surface. Such a fixed-side cam 32 is fitted onto the adjustment rod 7 so as to allow relative rotation with respect to the adjustment rod 7 and relative displacement in the width direction with respect to the adjustment rod 7. The fixed-side cam 32 has the engaging protrusion engaged with the vehicle-side through-hole 21a of the support plate portion 18a arranged on one side in the width direction so as to allow displacement only along the vehicle-side through-hole 21a.

[0043] Cam device 28 changes the rotational phase between the movable cam surface and the fixed cam surface by rotating movable cam 31 relative to fixed cam 32 based on the swing operation of adjustment lever 27, thereby expanding and contracting the width dimension. This expands and contracts the gap between fixed cam 32 of cam device 28 and thrust bearing 30, thereby expanding and contracting the gap between the pair of support plate portions 18a, 18b.

[0044] To adjust the position of the steering wheel, the adjustment lever 27 is swung downward (or upward), for example. This causes the movable cam 31 to rotate in the unlock direction, and the protrusions constituting the movable cam surface and Fixed side cam surfaceand the convex portions constituting the pair of pressing portions are arranged alternately in the circumferential direction, and the cam device 28 is placed in an unlocked state. As a result, the widthwise dimension of the cam device 28 is reduced, and the gap between the fixed cam 32 constituting the pair of pressing portions and the thrust bearing 30 is expanded. Furthermore, the surface pressure at the contact points between the inner surfaces of the support plate portions 18a, 18b and the outer surfaces of the clamped plate portions 16a, 16b is reduced or lost, and at the same time, the inner diameter of the outer column 11 elastically expands, and the surface pressure at the contact points between the inner circumferential surface of the outer column 11 and the outer circumferential surface of the inner column 10 is reduced. In this unclamped state, it is possible to adjust the fore-and-aft position and the up-and-down position of the steering wheel within the range in which the adjustment rod 7 can move inside the pair of column-side through-holes 17a, 17b and the pair of vehicle-body-side through-holes 21a, 21b.

[0045] To hold the steering wheel at a desired position, after moving the steering wheel to the desired position, the adjustment lever 27 is swung in the opposite direction (for example, upward or downward) to that used for adjusting the steering wheel position. This rotates the movable cam 31 in the locking direction, and the tip surface of the convex portion that constitutes the movable cam surface and Fixed side cam surface The tip surfaces of the convex portions constituting the cam device 28 abut against each other, placing the cam device 28 in a locked state. As a result, the width direction dimension of the cam device 28 expands, and the gap between the fixed cam 32 and the thrust bearing 30 constituting the pair of pressing portions decreases. Furthermore, the surface pressure at the contact points between the inner surfaces of the support plate portions 18a, 18b and the outer surfaces of the clamped plate portions 16a, 16b increases, and at the same time, the inner diameter of the outer column 11 elastically contracts, and the surface pressure at the contact points between the inner circumferential surface of the outer column 11 and the outer circumferential surface of the inner column 10 increases. In this clamped state, the steering wheel is held in the adjusted position.

[0046] <Balance spring> The balance spring 8 is supported by the vehicle body bracket 6 so as to span between the vehicle body bracket 6 and the adjustment rod 7, and applies an upward elastic force to the steering column 5. This prevents the steering wheel and steering column 5 from dropping forcefully downward due to their own weight when the cam device 28 is unlocked to adjust the position of the steering wheel. It also reduces the force required to move the steering wheel upward.

[0047] The balance spring 8 is made by bending elastic wire such as stainless spring steel. The balance spring 8 has a so-called double torsion spring structure. That is, the balance spring 8 has a pair of coil spring portions 33a, 33b and a connecting portion 34 that connects the pair of coil spring portions 33a, 33b together.

[0048] The pair of coil spring portions 33a, 33b are spaced apart in the width direction, and the connecting portion 34 is located between the pair of coil spring portions 33a, 33b in the width direction.

[0049] Of the pair of coil spring portions 33a, 33b, the coil spring portion 33a arranged on one side in the width direction (the right side in Figure 2, the front side in Figure 5) has a coil portion 35a and a pair of spring arm portions 36a, 36b.

[0050] The coil portion 35a is formed by spirally winding one longitudinal end portion of the wire. The coil portion 35a is disposed with its central axis facing the width direction when the balance spring 8 is assembled to the steering column device 1. The coil portion 35a is disposed in front of the front plate portion 20a that constitutes the vehicle body side bracket 6. In this example, the number of turns of the coil portion 35a is two. However, when implementing the present invention, the number of turns of the coil portion 35a is not limited to two, and may be one turn, or three or more turns.

[0051] The pair of spring arms 36a, 36b extend from both end portions of the coil portion 35a. When the balance spring 8 is assembled to the steering column device 1, the spring arm 36a, 36b that is disposed on the inner side in the width direction is Taichi The spring arm 36a extends in a generally linear manner downward as it moves away from the coil portion 35a. Others One spring arm 36b is formed from one longitudinal end of the wire rod, and extends in a generally linear fashion in a direction toward the rear as it moves away from coil 35a. The other spring arm 36b has a spring-side locking portion 37a bent in a crank shape at its tip.

[0052] Of the pair of coil spring portions 33a, 33b, the coil spring portion 33b arranged on the other widthwise side (the left side in Figure 2, the back side in Figure 5) has a coil portion 35b and a pair of spring arms 36c, 36d.

[0053] The coil portion 35b is formed by spirally winding the other longitudinal end portion of the wire. The coil portion 35b is disposed coaxially with the coil portion 35a constituting the coil spring portion 33a. Furthermore, the coil portion 35b is disposed in front of the front plate portion 20b constituting the vehicle body side bracket 6 in a state in which the balance spring 8 is assembled to the steering column device 1. In this example, the number of turns of the coil portion 35b is two, the same as the coil portion 35a. However, when implementing the present invention, the number of turns of the coil portion 35b is not limited to two, and may be one turn, or three or more turns.

[0054] The pair of spring arms 36c, 36d extend from both ends of the coil portion 35b. When the balance spring 8 is assembled to the steering column device 1, the spring arm 36c, 36d that is disposed on the inner side in the width direction is TaichiThe spring arm 36c extends in a generally linear manner downward as it moves away from the coil portion 35b, and is disposed generally parallel to one of the spring arms 36a constituting the coil spring portion 33a. Others One spring arm 36d is formed from the other longitudinal end of the wire rod, and extends in a generally linear fashion rearward as it moves away from coil portion 35b. The other spring arm 36d is disposed generally parallel to the other spring arm 36b that constitutes coil spring portion 33a. The tip of the other spring arm 36d is provided with a spring-side locking portion 37b that is bent in a crank shape.

[0055] The connecting portion 34 has a generally T-shape overall, and is disposed below the steering column 5 when the balance spring 8 is assembled to the steering column device 1. Specifically, the connecting portion 34 is disposed between a pair of clamped plate portions 16a, 16b that constitute the outer column 11. The connecting portion 34 is formed by bending a middle portion of the wire rod in the longitudinal direction, and has a pair of connecting arms 38a, 38b and a pressing portion 39.

[0056] The pair of connecting arms 38a, 38b are arranged coaxially with each other, with their central axes oriented in the width direction. The tip (the outer end in the width direction) of one connecting arm 38a, which is arranged on one side in the width direction (the right side in FIG. 2), is connected at a substantially right angle to the lower end of one spring arm 36a constituting the coil spring portion 33a. That is, one connecting arm 38a is bent at a substantially right angle from the lower end of one spring arm 36a of the coil spring portion 33a toward the inside in the width direction. In contrast, the tip (the outer end in the width direction) of the other connecting arm 38b, which is arranged on the other side in the width direction (the left side in FIG. 2), is connected at a substantially right angle to the lower end of one spring arm 36c constituting the coil spring portion 33b. That is, the other connecting arm portion 38b is bent at a substantially right angle from the lower end of one spring arm portion 36c of the coil spring portion 33b toward the inside in the width direction.

[0057] The pressing portion 39 has a generally U-shape and is composed of a pair of straight portions 40a, 40b and a generally arc-shaped connecting portion 41. The pair of straight portions 40a, 40b extend linearly in the front-rear direction and are arranged parallel to each other and spaced apart in the width direction. The rear ends of the pair of straight portions 40a, 40b are connected to each other by the connecting portion 41. Of the pair of straight portions 40a, 40b, the front end of one straight portion 40a arranged on one side in the width direction is connected at a generally right angle to the base end (the inner end in the width direction) of one connecting arm 38a, and the front end of the other straight portion 40b arranged on the other side in the width direction is connected at a generally right angle to the base end (the inner end in the width direction) of the other connecting arm 38b. In other words, one straight portion 40a is bent at approximately a right angle from the base end of one connecting arm 38a toward the rear, and the other straight portion 40b is bent at approximately a right angle from the base end of the other connecting arm 38b toward the rear.

[0058] The balance spring 8 twists the pair of coil spring portions 33a, 33b, and in a state in which the pair of coil spring portions 33a, 33b generate an elastic force in the torsional direction, the pair of spring-side locking portions 37a, 37b are respectively locked to the pair of bracket-side locking portions 24a, 24b provided on the vehicle-body-side bracket 6, and the tip portion (rear end portion) of the pressing portion 39 is engaged with (abuts against) the underside of the middle portion in the width direction of the adjustment rod 7. As a result, the balance spring 8 is elastically supported between the vehicle-body-side bracket 6 and the adjustment rod 7, and applies an upward elastic force to the outer column 11 via the adjustment rod 7. When practicing the present invention, it is also possible to apply an elastic force directly to the outer column by the balance spring.

[0059] <Vibration-damping member> The pair of vibration-damping members 9a, 9b suppresses resonance of the balance spring 8 and is attached to the balance spring 8 so as not to come off. Each of the pair of vibration-damping members 9a, 9b is made of an elastically deformable material, such as rubber or synthetic resin. As shown in FIG. 4A, each of the pair of vibration-damping members 9a, 9b is configured in a ring shape, such as a circular ring, an elliptical ring, or a rectangular ring (in the illustrated example, a circular ring), in a free state. Each of the pair of vibration-damping members 9a, 9b has a circular cross section and a wire diameter approximately equal to that of the balance spring 8. Furthermore, the diameter (inner diameter) of the pair of vibration-damping members 9a, 9b in a free state is larger than the outer diameter of the coil portions 35a, 35b. In this example, the pair of vibration-damping members 9a, 9b are identical components having the same shape and size. However, when implementing the present invention, the pair of vibration-damping members may also be components having different shapes. The cross-sectional shape of the vibration-damping member may also be rectangular.

[0060] Of the pair of vibration-damping members 9a, 9b, one vibration-damping member 9a is attached to one coil spring portion 33a located on one side in the width direction, and the other vibration-damping member 9b is attached to the other coil spring portion 33b located on the other side in the width direction. In this example, the attachment structure of the vibration-damping member 9a to one coil spring portion 33a and the attachment structure of the vibration-damping member 9b to the other coil spring portion 33b are the same except that they are oriented in opposite directions in the width direction. Therefore, with regard to the attachment structures of the vibration-damping members 9a, 9b, only the attachment structure of the vibration-damping member 9a to one coil spring portion 33a will be described, and an explanation of the attachment structure of the vibration-damping member 9b to the other coil spring portion 33b will be omitted.

[0061] In this example, the vibration-damping member 9a is attached in an elastically deformed state to one of the coil spring portions 33a that constitute the balance spring 8. Specifically, the vibration-damping member 9a is attached in a state in which it is torsionally deformed by 180° to one of the coil spring portions 33a. As shown in FIG. 4(A) to (B), the shape of the vibration-damping member 9a changes from a ring shape to an eight-shape due to the torsional deformation. After the torsional deformation, the vibration-damping member 9a has a pair of insertion ring portions 42a, 42b and an intersection portion 43 that serves as an obstruction portion.

[0062] Each of the pair of insertion rings 42a, 42b is formed in an annular shape. The inner diameter of each of the insertion rings 42a, 42b is larger than the wire diameter of the balance spring 8 and smaller than the outer diameter of the coil portion 35a. Therefore, the coil portion 35a cannot be inserted through the inside of the insertion rings 42a, 42b.

[0063] The intersection 43 is formed by torsionally deforming the annular vibration-damping member 9a by 180° and is composed of the proximal portions of the pair of insertion rings 42a, 42b. The intersection 43 has a generally X-shape and is located in the middle of the vibration-damping member 9a after torsional deformation. The intersection 43 obstructs the passage of the coil portion 35a inside the vibration-damping member 9a. As shown in FIG. 4A, in the free ring shape of the vibration-damping member 9a, the inner diameter is larger than that of the coil portion 35a, allowing the coil portion 35a to pass inside. However, as shown in FIG. 4B, in the torsionally deformed state, an X-shaped intersection 43 is formed in the middle, and the intersection 43 prevents the coil portion 35a from passing inside the vibration-damping member 9a.

[0064] 1, 2, and 5, with the vibration-damping member 9a attached to one of the coil spring portions 33a, the pair of spring arms 36a, 36b constituting the coil spring portion 33a are inserted inside the vibration-damping member 9a. Specifically, the pair of spring arms 36a, 36b are inserted inside the pair of insertion rings 42a, 42b provided on the vibration-damping member 9a after torsional deformation. In other words, one spring arm 36a is inserted in the up-down direction inside one insertion ring portion 42a, and the other spring arm 36b is inserted in the front-rear direction inside the other insertion ring portion 42b.

[0065] With the pair of spring arms 36a, 36b inserted inside the pair of insertion rings 42a, 42b, an intersection 43 provided between the portion of the vibration damping member 9a through which the pair of spring arms 36a, 36b are inserted is disposed radially outside the coil portion 35a. As shown in Fig. 1, with the steering column device 1 attached to the vehicle body, the intersection 43 is disposed in a portion of the radially outer portion of the coil portion 35a that is located rearward and downward.

[0066] With the vibration-damping member 9a attached to one of the coil spring portions 33a, the insertion ring portions 42a, 42b (opposite portions in the arrangement direction of the insertion ring portions 42a, 42b) are in contact with the spring arms 36a, 36b, respectively. The intersection portion 43 is also in contact with the coil portion 35a from the radially outer side. In this example, the elastic restoration force of the torsionally deformed vibration-damping member 9a can be utilized to elastically press the insertion ring portions 42a, 42b against the spring arms 36a, 36b, respectively. When implementing the present invention, the intersection portion 43 can also be elastically pressed against the coil portion 35a.

[0067] When the vibration-damping member 9a is attached to the balance spring 8 (coil spring portion 33a), the crossing portion 43 prevents the vibration-damping member 9a from slipping out toward the front and upward from the balance spring 8. Furthermore, because one spring arm portion 36a is inserted vertically inside one insertion ring portion 42a, the vibration-damping member 9a is prevented from slipping out in the front-to-rear direction from the balance spring 8. Furthermore, because the other spring arm portion 36b is inserted vertically inside the other insertion ring portion 42b, the vibration-damping member 9a is also prevented from slipping out in the up-to-down direction from the balance spring 8. In this way, in this example, the vibration-damping member 9a is attached to the balance spring 8 so that it cannot come off.

[0068] There is no particular restriction on the procedure for attaching the vibration-damping member 9a to the balance spring 8, but for example, it can be attached in the following procedure. First, one coil spring portion 33a constituting the balance spring 8 is inserted into the inside of the annular vibration damping member 9a in a free state, with the other spring arm portion 36b at the front. Then, the annular vibration damping member 9a is placed around one spring arm portion 36a. In other words, one spring arm portion 36a is inserted into the inside of the annular vibration damping member 9a.

[0069] Next, the annular vibration damping member 9a is torsionally deformed to form the pair of insertion ring portions 42a, 42b and the intersection portion 43. In this state, one spring arm portion 36a is inserted into the inside of one insertion ring portion 42a.

[0070] Thereafter, the other spring arm portion 36b is inserted into the other insertion ring portion 42b. As a result, with the pair of spring arms 36a, 36b inserted into the pair of insertion ring portions 42a, 42b, the crossing portion 43 is connected to the coil portion 35a The axial direction of the ...

[0071] In this example, after a pair of vibration damping members 9a, 9b are attached to the balance spring 8, the balance spring 8 is attached so as to span between the bracket 6 on the vehicle body side and the adjustment rod 7.

[0072] In the steering column device 1 of this example, the balance spring 8 applies an upward elastic force to the steering column 5 via the adjustment rod 7, so even when the adjustment lever 27 is operated to unlock the cam device 28 in order to adjust the position of the steering wheel, the steering column 5 and the steering wheel can be prevented from dropping downward forcefully due to their own weight. Also, the force required to move the steering wheel upward can be reduced.

[0073] Furthermore, in the steering column device 1 of this example, a pair of vibration-damping members 9a, 9b are attached to the balance spring 8, which makes it possible to suppress resonance of the balance spring 8. For example, when adjusting the longitudinal position or vertical position of the steering wheel, if the adjustment rod 7 hits the longitudinal ends of the column-side through-holes 17a, 17b or the vertical ends of the vehicle-body-side through-holes 21a, 21b with great force, resonance may occur in the balance spring 8 that is in contact with the adjustment rod 7. However, in this example, since the vibration-damping members 9a, 9b are attached to the balance spring 8, resonance in the balance spring 8 can be suppressed, and abnormal noise can be suppressed. Specifically, vibrations transmitted from the balance spring 8 deform the vibration-damping members 9a, 9b, which converts vibration energy into thermal energy, thereby suppressing (damping) vibration of the balance spring 8.

[0074] In particular, in this example, even when the number of turns of the coil portions 35a, 35b that make up the balance spring 8 is small, the vibration damping members 9a, 9b can be attached to the balance spring 8. That is, in this example, the pair of vibration damping members 9a, 9b are attached to the balance spring 8 in a state in which they are torsionally deformed into an eight-shaped configuration. Specifically, in a state in which the pair of spring arms 36a, 36b are inserted inside the pair of insertion rings 42a, 42b provided on the vibration damping member 9a after torsion deformation, the crossing portion 43 provided between the portions of the vibration damping member 9a through which the pair of spring arms 36a, 36b are inserted is rotated by the coil portion 35a When the vibration-damping members 9a, 9b are attached in this manner, the crossing portion 43 prevents the vibration-damping members 9a, 9b from falling off the balance spring 8 as the coil portions 35a, 35b pass inside the vibration-damping members 9a, 9b, and the insertion ring portions 42a, 42b also prevent the vibration-damping members 9a, 9b from falling off the balance spring 8. Therefore, in this example, even if the number of turns of the coil portions 35a, 35b that make up the balance spring 8 is small, the vibration-damping members 9a, 9b can be attached to the balance spring 8 so that they cannot fall off.

[0075] The vibration (amplitude) generated in the balance spring 8 tends to be large at positions away from the support portions (contact portions) of the balance spring 8 with the vehicle body side bracket 6 and the adjustment rod 7. In this example, the vibration-damping members 9a, 9b can be made to actively contact the coil portions 35a, 35b, which are located away from the support portions of the balance spring 8 and are prone to large vibrations, thereby effectively suppressing the generation of abnormal noise.

[0076] [Second example of embodiment] A second example of the embodiment will be described with reference to FIG.

[0077] In this example, the vibration-damping members 9c and 9d are also configured to have an annular shape in a free state. However, in this example, the vibration-damping members 9c and 9d are attached to the pair of coil spring portions 33a and 33b that make up the balance spring 8 in a state where they are torsionally deformed by 360°. The vibration-damping members 9c and 9d change from a ring shape to a roughly figure-eight shape due to the torsional deformation. The vibration-damping members after torsional deformation 9c, 9d The connector 42 includes a pair of insertion rings 42c and 42d and an intersection 43a that serves as an obstacle.

[0078] The intersection 43a is formed by twisting each of the vibration damping members 9c and 9d through 360°, and is not a simple intersection in a roughly X-shape, but a twisted intersection with a twisted portion in the center.

[0079] In the present embodiment, each of the vibration-damping members 9c, 9d is attached to the balance spring 8 in a state where it is torsionally deformed 360°. This allows the torsionally deformed vibration-damping members 9c, 9d to exert a greater force to restore their elasticity than in the structure of the first embodiment. This allows for a greater force to elastically press each of the insertion rings 42c, 42d against the spring arms 36a to 36d. This enhances the vibration-damping effect of the vibration-damping members 9c, 9d on the balance spring 8. Furthermore, compared to the structure of the first embodiment, the inner diameter of the insertion rings 42c, 42d can be made smaller, more effectively preventing the coil portions 35a, 35b from passing through the inside of the insertion rings 42c, 42d. The other configurations and effects are the same as those of the first embodiment.

[0080] [Third example of embodiment] A third example of the embodiment will be described with reference to FIG.

[0081] In this example, the vibration-damping members 9e and 9f are also annular in their free state. In this example, the intermediate portions 45 of the vibration-damping members 9e and 9f are attached to the pair of coil spring portions 33a and 33b that make up the balance spring 8, respectively, with the intermediate portions 45 inserted radially inside the coil portions 35a and 35b. Note that in this example, the attachment structure of the vibration-damping member 9e to one coil spring portion 33a and the attachment structure of the vibration-damping member 9f to the other coil spring portion 33b are the same except that their orientations in the width direction are opposite. Therefore, regarding the attachment structures of the vibration-damping members 9e and 9f, only the attachment structure of the vibration-damping member 9e to one coil spring portion 33a will be described, and the attachment structure of the vibration-damping member 9f to the other coil spring portion 33b will not be described.

[0082] In this example, with the vibration-damping member 9e attached to one of the coil spring portions 33a, a pair of spring arms 36a, 36b constituting the coil spring portion 33a are inserted inside diametrically opposite portions of the annular vibration-damping member 9e. In this state, an intermediate portion 45 consisting of a pair of linear portions 44a, 44b located between the portions of the vibration-damping member 9e through which the pair of spring arms 36a, 36b are inserted is disposed radially inside the coil portion 35a. The pair of linear portions 44a, 44b constituting the intermediate portion 45 may or may not intersect with each other by torsional deformation of the vibration-damping member.

[0083] There is no particular restriction on the procedure for attaching the vibration-damping member 9e to the balance spring 8, but for example, it can be attached in the following procedure. First, one coil spring portion 33a constituting the balance spring 8 is inserted into the inside of the annular vibration damping member 9e in a free state, with the other spring arm portion 36b at the front. Then, the annular vibration damping member 9e is placed around one spring arm portion 36a. In other words, one spring arm portion 36a is inserted inside the annular vibration damping member 9e.

[0084] Next, a portion of the vibration-damping member 9e, including a portion located diametrically opposite the portion through which one spring arm portion 36a is inserted, is inserted radially inside the coil portion 35a that constitutes one coil spring portion 33a from the inside to the outside in the width direction.

[0085] Thereafter, the other spring arm portion 36b is inserted into the inside of the portion of the vibration damping member 9e that has been inserted radially inside the coil portion 35a. As a result, with the pair of spring arms 36a, 36b inserted inside the vibration damping member 9e, the middle portion 45 of the vibration damping member 9e is inserted and positioned radially inside the coil portion 35a.

[0086] In the above-described example, when the vibration-damping members 9e, 9f are attached to the balance spring 8, the middle portions 45 of the vibration-damping members 9e, 9f are inserted radially inside the coil portions 35a, 35b, thereby preventing the vibration-damping members 9e, 9f from falling off the balance spring 8.

[0087] In this example, the vibration damping members 9e, 9f use the force of the pair of linear portions 44a, 44b elastically restoring in the direction away from each other to elastically press the pair of linear portions 44a, 44b toward the radially inner side of the coil portions 35a, 35b, and also elastically press the portions of the vibration damping members 9e, 9f that connect the pair of linear portions 44a, 44b against the spring arms 36a to 36d, thereby suppressing the occurrence of resonance in the balance spring 8.

[0088] Furthermore, because the intermediate portions 45 of the vibration-damping members 9e, 9f are disposed radially inward of the coil portions 35a, 35b, the amount by which the vibration-damping members 9e, 9f protrude from the coil portions 35a, 35b can be kept small, thereby enabling the steering column device 1 to be made more compact. The other configurations and effects are the same as those of the first embodiment.

[0089] [Fourth Example of Embodiment] A fourth example of the embodiment will be described with reference to FIG.

[0090] In this example, one vibration damping member 9g is attached to the balance spring 8. Specifically, a pair of vibration damping members 9g are attached to both of a pair of coil spring portions 33a, 33b that make up the balance spring 8. The vibration damping member 9g of this example is configured to be annular in a free state, but has a larger diameter (longer circumferential length) than the vibration damping members 9a to 9f of the first to third examples of the embodiment.

[0091] In this example, with the vibration damping member 9g attached to the balance spring 8, the other spring arm 36b constituting one coil spring portion 33a and the other spring arm 36d constituting the other coil spring portion 33b are inserted inside the vibration damping member 9g. In this state, ends on both sides in the width direction of an intermediate portion 45a of the vibration damping member 9g, which is located between the portions through which the pair of other spring arms 36b, 36d are inserted, are disposed so as to be inserted radially inside the coil portions 35a, 35b.

[0092] There is no particular restriction on the procedure for attaching the vibration-damping member 9g to the balance spring 8, but for example, it can be attached in the following procedure. First, the other spring arm 36b of one coil spring portion 33a constituting the balance spring 8 is inserted into the inside of the vibration damping member 9g.

[0093] Next, the other spring arm of the vibration damping member 9g is attached to the inside. 36bThe portion including the portion located on the diametrically opposite side of the portion where the wire has been inserted is inserted through the radially inner side of the coil portion 35a constituting one coil spring portion 33a from the outside in the width direction toward the inside, and is then hung over the base end of the pressing portion 39 constituting the connecting portion 34, and then inserted through the radially inner side of the coil portion 35b constituting the other coil spring portion 33b from the outside in the width direction toward the inside.

[0094] Then, the other spring arm 36d of the other coil spring portion 33b is inserted into the inside of the portion of the vibration damping member 9g that has been inserted through the radially inner side of the coil portion 35b of the other coil spring portion 33b. As a result, with the pair of other spring arms 36b, 36d inserted into the inside of the vibration damping member 9g, the middle portion of the vibration damping member 9g is 45a can be inserted and disposed radially inside the coil portions 35a and 35b.

[0095] In the above-described example, when the vibration-damping member 9g is attached to the balance spring 8, the middle portion 45a of the vibration-damping member 9g is inserted radially inside the coil portions 35a and 35b, thereby preventing the vibration-damping member 9g from falling off the balance spring 8.

[0096] In this example, the portion of intermediate portion 45a of vibration-damping member 9g that is inserted radially inside coil portions 35a, 35b uses its elastic restoring force to elastically press intermediate portion 45a radially inside coil portions 35a, 35b, and also elastically presses both diametrically (widthwise) side portions of vibration-damping member 9g against the other spring arm portion 36b of one coil spring portion 33a and the other spring arm portion 36d that constitutes the other coil spring portion 33b. This suppresses the occurrence of resonance in balance spring 8.

[0097] Furthermore, because the intermediate portion 45a of the vibration-damping member 9g is disposed radially inward of the coil portions 35a, 35b, it is possible to minimize the amount of protrusion of the vibration-damping member 9g from the coil portions 35a, 35b, thereby saving space in the steering column device 1. Furthermore, in this example, because the pair of vibration-damping members 9g is attached to both of the pair of coil spring portions 33a, 33b that constitute the balance spring 8, it is possible to reduce the number of parts and also reduce the number of steps required to attach the vibration-damping member 9g. The other configurations and effects are the same as those of the first embodiment.

[0098] [Fifth Example of Embodiment] A fifth example of the embodiment will be described with reference to FIG.

[0099] This example is a modification of the fourth example of the embodiment. In this example, with the vibration-damping member 9g attached to the balance spring 8, the widthwise intermediate portion of the intermediate portion 45a constituting the vibration-damping member 9g is wrapped around the base end of the pressing portion 39 constituting the connection portion 34 of the balance spring 8.

[0100] In the present example as described above, the intermediate portion 45a of the vibration-damping member 9g is wrapped around the base end of the pressing portion 39 that constitutes the connecting portion 34, which effectively prevents the vibration-damping member 9g from falling off the balance spring 8. Furthermore, the vibration-damping member 9g can be brought into strong contact with the balance spring 8, which enhances the vibration-damping effect of the vibration-damping member 9g. The other configurations and effects are the same as those of the first and fourth embodiments.

[0101] [Reference example] A reference example of the present invention will be described with reference to FIGS.

[0102] In this reference example, vibration-damping members 46a, 46b are attached to the coil portions 35a, 35b of the pair of coil spring portions 33a, 33b that constitute the balance spring 8, respectively.

[0103] Each of the vibration damping members 46a, 46b is elastically deformable and has a generally Ω shape in a free state, as shown in Fig. 11. Each of the vibration damping members 46a, 46b has a generally C-shaped main body 47 and a pair of extending arms 48a, 48b extending from the main body 47. The distal ends of the extending arms 48a, 48b are provided with spherical locking portions 49a, 49b, respectively.

[0104] In this example, with a circumferential portion of the coil portions 35a, 35b inserted inside the main body 47 that constitutes each of the vibration damping members 46a, 46b, the pair of extending arms 48a, 48b are twisted to engage the spherical locking portions 49a, 49b provided at the respective tips with each other, thereby attaching the vibration damping members 46a, 46b to the coil portions 35a, 35b, respectively.

[0105] In the above-described example, as in each example of the embodiment, vibration-damping members 46a, 46b can be attached to the balance spring 8 even when the number of turns of the coil portions 35a, 35b that make up the balance spring 8 is small. The other configurations and effects are the same as those of the first embodiment.

[0106] Although the embodiments of the present invention have been described above, the present invention is not limited to these and can be modified as appropriate within the scope of the technical concept of the invention. Furthermore, the structures of the examples of the embodiments and the structures of the reference examples can be combined as appropriate as long as no contradiction occurs.

[0107] When implementing the present invention, the shape of the balance spring is not limited to the structures shown in the embodiments and can be modified as appropriate as long as it can impart an appropriate amount of upward elastic force to the steering column. For example, the present invention can be applied to a balance spring disposed on only one widthwise side of the vehicle-side bracket, as in the conventional structure described in JP 2008-265647 A. The shape of the vibration-damping member attached to the balance spring can also be modified as appropriate. The manner in which the vibration-damping member is attached to the balance spring is also not limited to the structures shown in the embodiments and can be modified as appropriate, such as by wrapping a portion of the vibration-damping member around a coil portion. Furthermore, the present invention can be applied to springs attached to adjustment levers (so-called tilt levers) for adjusting the position of the steering wheel, in addition to balance springs. [Explanation of symbols]

[0108] 1. Steering column device 2 steering shaft 3 Lower shaft 4 Upper Shaft 5. Steering column 6 Body side bracket 7 Adjustment Rod 8 Balance Spring 9a~9g Vibration damping members 10 Innacolumn 11 Outer Column 12 Lower bracket 13 Tilt axis 14 Slit 15 Column side bracket 16a, 16b Clamped plate part 17a, 17b Column side through holes 18a, 18b Support plate part 19 Top plate 20a, 20b Front plate part 21a, 21b Car body side through holes 22 Cutout 23 capsules 24a, 24b Bracket side locking portion 25 Anchor Section 26 Male thread 27 Adjustment lever 28 Cam device 29 Nut 30 Thrust bearing 31 Movable cam 32 Fixed side cam 33a, 33b Coil spring part 34 Connection 35a, 35b Coil section 36a~36d Spring arm 37a, 37a Spring side locking portion 38a, 38b Connecting arms 39 Pressing section 40a, 40b Straight section 41 Connecting part 42a~42d Insertion ring 43, 43a intersection 44a, 44b Linear part 45, 45a middle part 46a, 46b vibration damping member 47 Main body 48a, 48b Extending arms 49a, 49b Spherical locking part 100 steering shaft 101 Steering column 102 Steering Wheel 103 Lower shaft 104 Upper shaft 105 Roar Column 106 Upper Column 107 Clamped plate part 108 Column side bracket 109 Body side bracket 110 Support plate part 111 Column side through hole 112 Body side through hole 113 Adjustment rod 114 Anchor Section 115 Stopper member 116 Cam device 117 Adjustment lever 118 Movable cam 119 Fixed side cam 120 Balance spring 121 Coil section 122a, 122b spring arm 123 Vibration-damping members

Claims

1. A mounting structure for a vibration damping member on a balance spring for applying elastic force to a steering column, The balance spring has a coil portion and a pair of spring arms extending from the coil portion, The vibration damping member is elastically deformable and has an annular shape in a free state, The pair of spring arms are inserted into the inside of the vibration-damping member, and an obstacle portion that obstructs the passage of the coil portion through the inside of the vibration-damping member is disposed radially outside the coil portion, and the vibration-damping member is attached to the balance spring. Mounting structure of vibration damping member to balance spring.

2. Each of the pair of spring arms is inserted into an annular insertion ring portion formed by torsional deformation of the vibration damping member, The obstacle portion is an intersection portion formed by torsional deformation of the vibration damping member.

2. A mounting structure for a vibration damping member to a balance spring according to claim 1.

3. 3. The mounting structure for a vibration damping member to a balance spring according to claim 2, wherein the intersecting portion is formed by twisting the vibration damping member through 360 degrees or more.

4. A mounting structure for a vibration damping member on a balance spring for applying elastic force to a steering column, The balance spring has a coil portion and a pair of spring arms extending from the coil portion, The vibration damping member is elastically deformable and has an annular shape in a free state, The vibration damping member is attached to the balance spring in a state in which each of the pair of spring arms is inserted into the inside of the vibration damping member, and an intermediate portion of the vibration damping member between the portions through which the pair of spring arms is inserted is inserted radially inside the coil portion. Mounting structure of vibration damping member to balance spring.

5. A mounting structure for a vibration damping member on a balance spring for applying elastic force to a steering column, the balance spring includes a pair of coil spring portions, each of which has a coil portion and a pair of spring arms extending from the coil portion, and a connecting portion that connects one of the spring arms provided on each of the pair of coil spring portions to each other, The vibration damping member is elastically deformable and has an annular shape in a free state, The vibration damping member is attached to the balance spring in a state in which the other spring arm portion of each of the pair of coil spring portions is inserted inside the vibration damping member, and an intermediate portion of the vibration damping member between the portions through which the other spring arm portion of the pair is inserted is inserted radially inside the coil portion of each of the pair of coil spring portions. Mounting structure of vibration damping member to balance spring.

6. 6. The structure for attaching a vibration-damping member to a balance spring according to claim 5, wherein the intermediate portion of the vibration-damping member is wrapped around the connecting portion.

7. 7. The structure for mounting a vibration damping member to a balance spring according to claim 1, wherein the number of turns of the coil portion is two or less.

8. a steering column including a column-side bracket having a column-side through-hole penetrating in the width direction; a vehicle body side bracket including a pair of support plate portions disposed on both sides of the column side bracket in the width direction, the support plate portions each having a vehicle body side through-hole that penetrates the support plate portions in the width direction and extends in the vertical direction; an adjustment rod that is inserted in the width direction through the column-side through-hole and the pair of vehicle-body-side through-holes; a balance spring supported by the vehicle body-side bracket and applying an upward elastic force to the steering column; a vibration-damping member attached to the balance spring and configured to suppress resonance of the balance spring; A steering column device, wherein the vibration-damping member is attached to the balance spring by the attachment structure for attaching the vibration-damping member to the balance spring according to any one of claims 1 to 7.

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