JPH08142877A - Impact absorbing type steering column and manufacture thereof - Google Patents
Impact absorbing type steering column and manufacture thereofInfo
- Publication number
- JPH08142877A JPH08142877A JP30989794A JP30989794A JPH08142877A JP H08142877 A JPH08142877 A JP H08142877A JP 30989794 A JP30989794 A JP 30989794A JP 30989794 A JP30989794 A JP 30989794A JP H08142877 A JPH08142877 A JP H08142877A
- Authority
- JP
- Japan
- Prior art keywords
- spacer
- column
- columns
- dimension
- press
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Steering Controls (AREA)
- Vibration Dampers (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、車両の衝突時において
運転者に作用する衝撃を吸収するために用いられる衝撃
吸収式ステアリングコラムとその製造方法に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a shock absorbing steering column used for absorbing a shock applied to a driver in the event of a vehicle collision and a method for manufacturing the same.
【０００２】[0002]
【従来の技術】筒状の第１コラムに筒状の第２コラムを
筒状のスペーサを介し圧入し、両コラムの軸方向相対移
動によって衝撃エネルギーを吸収するようにした衝撃吸
収式ステアリングコラムが提案されている（実開平１‐
１７２９６５号公報参照）。そのスペーサにより両コラ
ムが互いにこじれるのを防止し、両コラムの円滑な軸方
向相対移動により衝撃エネルギーの吸収を図るものであ
る。従来、そのスペーサの内周および外周は平坦な円筒
面とされている。2. Description of the Related Art An impact absorption type steering column in which a tubular second column is press-fitted into a tubular first column via a tubular spacer so as to absorb impact energy by the relative movement of both columns in the axial direction. Proposed (Actual Kaihei 1-
172965). The spacer prevents both columns from twisting each other, and the impact energy is absorbed by the smooth relative movement of both columns in the axial direction. Conventionally, the inner circumference and outer circumference of the spacer are flat cylindrical surfaces.
【０００３】[0003]
【発明が解決しようとする課題】上記構成の衝撃吸収式
ステアリングコラムにおいては、第１コラムへの第２コ
ラムのスペーサを介する圧入荷重が過大になると、両コ
ラムの軸方向相対移動に要する荷重も過大になる。一
方、その圧入荷重が小さくなり過ぎると、両コラムの軸
方向相対移動に要する荷重も小さくなり過ぎる。すなわ
ち、両コラムの軸方向相対移動に要する荷重を適正な範
囲に設定することができなければ、大きな衝撃が運転者
に作用してしまう。In the shock absorbing steering column having the above-mentioned structure, when the press-fitting load to the first column via the spacer of the second column becomes excessive, the load required for the relative movement of both columns in the axial direction is also increased. Be oversized. On the other hand, if the press-fitting load becomes too small, the load required for the axial relative movement of both columns will become too small. That is, if the load required for the relative movement of both columns in the axial direction cannot be set within an appropriate range, a large impact will act on the driver.
【０００４】そこで、両コラムとスペーサとの間の締め
しろを管理することで、その両コラムの軸方向相対移動
に要する荷重を適正範囲内に設定することが行なわれ
る。すなわち、図１４に示すように、第１コラムの内径
から第２コラムの外径を差し引いた値を２で割ることで
得られる両コラムの間の隙間寸法をＤ１、そのスペーサ
の圧入前の全厚み寸法をＤ２とする場合、その全厚み寸
法と隙間寸法との差Ｄ２−Ｄ１に応じ圧入荷重が変化す
ることから、その差Ｄ２−Ｄ１を管理することで、その
両コラムの軸方向相対移動に要する荷重を適正範囲内に
設定できる。Therefore, by controlling the tightening margin between both columns and the spacer, the load required for the axial relative movement of both columns is set within an appropriate range. That is, as shown in FIG. 14, the gap dimension between both columns obtained by dividing the value obtained by subtracting the outer diameter of the second column from the inner diameter of the first column by D1, is the total dimension of the spacer before press fitting. When the thickness dimension is D2, the press-fit load changes according to the difference D2-D1 between the total thickness dimension and the clearance dimension. Therefore, by managing the difference D2-D1, the axial relative movement of both columns is performed. The load required for can be set within an appropriate range.
【０００５】しかし、第１コラムの内径寸法、第２コラ
ムの外径寸法およびスペーサの圧入前の全厚み寸法は、
一定以上の加工公差が必要である。その公差に応じ、両
コラムの間の隙間寸法Ｄ１およびスペーサの圧入前の全
厚み寸法Ｄ２はばらつく。例えば、図１３における実線
は、従来のスペーサの圧入前の全厚み寸法Ｄ２が一定で
あるとした場合における、両コラムの間の隙間寸法Ｄ１
の設定値からのばらつきと軸方向相対移動に要する荷重
との関係を示し、両コラムの間の隙間寸法Ｄ１は公差範
囲±δ（例えば±０．０２５ｍｍ程度）でばらつき、そ
のばらつきに応じ荷重がばらつくのを確認できる。これ
は、図１４に示すように、両コラムの間の隙間寸法Ｄ１
が±δの範囲でばらつく場合、そのばらつきに応じスペ
ーサの圧入時の圧縮変形量が変動するためである。その
荷重のばらつきは、実際にはスペーサの全厚み寸法もば
らつくため、図１３に示すよりも大きくなる。特に、そ
のスペーサを合成樹脂材により型成形する場合、成形誤
差が大きくなるため、その荷重を適正範囲内に設定する
ことは困難であった。However, the inner diameter of the first column, the outer diameter of the second column and the total thickness of the spacer before press fitting are
Machining tolerance above a certain level is required. Depending on the tolerance, the gap dimension D1 between both columns and the total thickness dimension D2 of the spacer before press fitting vary. For example, the solid line in FIG. 13 indicates a gap dimension D1 between both columns in the case where the total thickness dimension D2 of the conventional spacer before press fitting is constant.
Shows the relationship between the variation from the set value of and the load required for the relative movement in the axial direction. The gap dimension D1 between both columns varies within the tolerance range ± δ (for example, about ± 0.025 mm), and the load varies depending on the variation. You can see the variations. This is the gap dimension D1 between both columns, as shown in FIG.
This is because when the value of Δ varies within the range of ± δ, the amount of compressive deformation of the spacer during press fitting varies depending on the variation. The variation in the load is actually larger than that shown in FIG. 13 because the total thickness dimension of the spacer also varies. In particular, when the spacer is molded with a synthetic resin material, a molding error increases, and it is difficult to set the load within an appropriate range.
【０００６】本発明は、上記従来技術の問題を解決する
ことのできる衝撃吸収式ステアリングコラムとその製造
方法を提供することを目的とする。An object of the present invention is to provide a shock absorbing steering column and a method for manufacturing the same, which can solve the problems of the prior art.
【０００７】[0007]
【課題を解決するための手段】本件第１発明は、筒状の
第１コラムに筒状の第２コラムが筒状のスペーサを介し
圧入されている衝撃吸収式ステアリングコラムにおい
て、そのスペーサは、合成樹脂材により形成されると共
に外周および内周のうちの少なくとも一方に形成される
複数の突条を有し、その第１コラムの内周および第２コ
ラムの外周のうちの少なくとも一方は、それら突条を介
しスペーサに接することを特徴とする。両コラム間に圧
入されているスペーサの突条の高さ寸法は、突条の形成
されていない部分の厚み寸法よりも小さくされているの
が好ましい。According to the first aspect of the present invention, in a shock absorbing steering column in which a tubular second column is press-fitted into a tubular first column through a tubular spacer, the spacer is It has a plurality of ridges formed of a synthetic resin material and formed on at least one of the outer circumference and the inner circumference, and at least one of the inner circumference of the first column and the outer circumference of the second column is It is characterized in that it is in contact with the spacer through a ridge. The height dimension of the protrusion of the spacer press-fitted between the two columns is preferably smaller than the thickness dimension of the portion where the protrusion is not formed.
【０００８】本件第２発明は、本件第１発明の衝撃吸収
式ステアリングコラムを製造するに際し、そのスペーサ
の圧入前の全厚み寸法を両コラムの間の隙間寸法よりも
大きくし、そのスペーサの圧入前の全厚み寸法から突条
の高さ寸法を差し引いた寸法を両コラムの間の隙間寸法
よりも小さくし、各突条を圧縮変形させつつ第１コラム
に第２コラムをスペーサを介し圧入することを特徴とす
る。According to the second aspect of the present invention, when manufacturing the shock absorbing steering column of the first aspect of the present invention, the total thickness dimension of the spacer before press-fitting is made larger than the gap dimension between both columns, and the press-fitting of the spacer is performed. The dimension obtained by subtracting the height of the ridge from the previous total thickness is made smaller than the gap between both columns, and the second column is press-fitted into the first column via the spacer while compressing and deforming each ridge. It is characterized by
【０００９】[0009]
【発明の作用および効果】本件発明によれば、両コラム
とスペーサとの間の締めしろを管理することで、両コラ
ムの軸方向相対移動に要する荷重を適正範囲内に設定す
ることができる。すなわち、図１２に示すように、第１
コラムの内径から第２コラムの外径を差し引いた値を２
で割ることで得られる両コラムの間の隙間寸法をＤ１、
そのスペーサの圧入前の全厚み寸法をＤ２とする場合、
その全厚み寸法と隙間寸法との差Ｄ２−Ｄ１に応じ圧入
荷重が変化し、その圧入荷重は両コラムの軸方向相対移
動に要する荷重に対応する。その両コラムの軸方向相対
移動に要する荷重のばらつきは、その第１コラムの内径
寸法、第２コラムの外径寸法およびスペーサの圧入前の
全厚み寸法の加工公差に応じ、両コラムの間の隙間寸法
Ｄ１およびスペーサの圧入前の全厚み寸法Ｄ２がばらつ
いたとしても、従来よりも小さくできる。これは、図１
２に示すように、そのスペーサの圧入前の全厚み寸法Ｄ
２を両コラムの間の隙間寸法Ｄ１よりも大きくし、その
スペーサの圧入前の全厚み寸法Ｄ２から突条３ｄの高さ
寸法Ｈを差し引いた寸法Ｄ３を両コラムの間の隙間寸法
Ｄ１よりも小さくすることで、スペーサの圧入時の圧縮
変形量が従来よりも小さくなることによる。すなわち、
両コラムの間の隙間寸法Ｄ１が±δの公差範囲でばらつ
いたとしても、そのばらつきによるスペーサの圧入時の
圧縮変形量の変動は、従来のようにスペーサの内外周が
平坦な円筒面である場合よりも小さくなる。これによ
り、両コラムの軸方向相対移動に要する荷重を適正範囲
内に設定し、適正に衝撃エネルギーを吸収することがで
きる。なお、スペーサの圧入前の全厚み寸法Ｄ２がばら
ついたとしても、Ｄ２＞Ｄ１＞Ｄ３の関係が成立して適
正に衝撃エネルギーを吸収できるように、スペーサの圧
入前の全厚み寸法Ｄ２および突条３ｄの高さ寸法Ｈは設
定される。According to the present invention, by controlling the tightening margin between both columns and the spacer, the load required for the axial relative movement of both columns can be set within an appropriate range. That is, as shown in FIG.
The value obtained by subtracting the outer diameter of the second column from the inner diameter of the column is 2
Divide the gap dimension between both columns obtained by dividing by D1,
When the total thickness dimension of the spacer before press fitting is D2,
The press-fitting load changes according to the difference D2-D1 between the total thickness dimension and the clearance dimension, and the press-fitting load corresponds to the load required for the axial relative movement of both columns. The variation in the load required for the relative movement of both columns in the axial direction depends on the machining tolerance of the inner diameter dimension of the first column, the outer diameter dimension of the second column, and the total thickness dimension of the spacer before press fitting. Even if the gap dimension D1 and the total thickness dimension D2 of the spacer before press-fitting vary, it can be made smaller than before. This is
As shown in 2, the total thickness dimension D of the spacer before press fitting
2 is made larger than the gap dimension D1 between both columns, and the dimension D3 obtained by subtracting the height dimension H of the ridge 3d from the total thickness dimension D2 of the spacer before press fitting is larger than the gap dimension D1 between both columns. By making it smaller, the amount of compressive deformation when the spacer is press-fitted becomes smaller than in the conventional case. That is,
Even if the gap dimension D1 between both columns varies within the tolerance range of ± δ, the variation in the amount of compressive deformation at the time of press-fitting of the spacer due to the variation is due to the flat inner and outer peripheries of the spacer as in the conventional case. Smaller than if. Thereby, the load required for the relative movement of both columns in the axial direction can be set within an appropriate range, and the impact energy can be appropriately absorbed. Even if the total thickness dimension D2 of the spacer before press-fitting varies, the total thickness dimension D2 of the spacer before press-fitting and the ridges are set so that the relationship of D2>D1> D3 is established and the impact energy can be properly absorbed. The height dimension H of 3d is set.
【００１０】両コラム間に圧入されている状態でのスペ
ーサの突条の高さ寸法を、突条の形成されていない部分
の厚み寸法よりも小さくすることで、そのスペーサが合
成樹脂材製で金属等に比べ変形し易いものであっても、
衝撃作用時における突条の変形による両コラムの相対的
な傾きを小さくし、また、その突条の形成されていない
変形し難い部分により両コラムを軸方向相対移動するよ
うに案内できるので、両コラムを円滑に軸方向相対移動
させて適正に衝撃エネルギーを吸収できる。By making the height dimension of the ridges of the spacer in the state of being press-fitted between both columns smaller than the thickness dimension of the portion where the ridges are not formed, the spacer is made of synthetic resin material. Even if it is more easily deformed than metal,
The relative inclination of both columns due to the deformation of the ridges during impact action can be reduced, and both columns can be guided to move axially relative to each other due to the non-deformable portion where the ridges are not formed. The column can be smoothly moved in the axial direction to properly absorb the impact energy.
【００１１】[0011]
【実施例】以下、図面を参照して本発明の実施例を説明
する。Embodiments of the present invention will be described below with reference to the drawings.
【００１２】図１〜図６に示す衝撃吸収式ステアリング
コラム１は、筒状の金属製第１コラム２ａと、この第１
コラム２ａに筒状のスペーサ３を介し圧入される金属製
第２コラム２ｂとを備える。その第１コラム２ａは、ベ
アリング４を介し筒状の第１ハンドルシャフト５を支持
する。その第１ハンドルシャフト５の一端にステアリン
グホイール（図示省略）が連結され、他端に第２ハンド
ルシャフト７の一端が挿入され、その第２ハンドルシャ
フト７はベアリング６を介し第２コラム２ｂにより支持
される。そのベアリング４は、第１コラム２ａの内周に
形成された段差と第１ハンドルシャフト５の外周に取り
付けられた止め輪１２とにより、第１コラム２ａと第１
ハンドルシャフト５とに対する軸方向相対移動が規制さ
れる。The shock absorbing steering column 1 shown in FIGS. 1 to 6 has a cylindrical first metallic column 2a and a first metallic column 2a.
A second metal column 2b press-fitted into the column 2a via a cylindrical spacer 3 is provided. The first column 2a supports a tubular first handle shaft 5 via a bearing 4. A steering wheel (not shown) is connected to one end of the first handle shaft 5, one end of the second handle shaft 7 is inserted into the other end, and the second handle shaft 7 is supported by the second column 2b via a bearing 6. To be done. The bearing 4 has a step formed on the inner circumference of the first column 2a and a retaining ring 12 mounted on the outer circumference of the first handle shaft 5 so that the first column 2a and the first
Axial relative movement with respect to the handle shaft 5 is restricted.
【００１３】図２に示すように、その第２ハンドルシャ
フト７の外周に一対の周溝８が形成され、その周溝８に
連通する通孔９が第１ハンドルシャフト５に形成され、
その通孔９と周溝８とに樹脂６０が充填される。衝撃が
作用すると、その樹脂６０が破断され、第１ハンドルシ
ャフト５と第２ハンドルシャフト７とは軸方向相対移動
する。第１ハンドルシャフト５の内周形状と第２ハンド
ルシャフト７の外周形状とは非円形とされることで、第
１ハンドルシャフト５と第２ハンドルシャフト７とは回
転伝達可能に連結されている。As shown in FIG. 2, a pair of peripheral grooves 8 are formed on the outer periphery of the second handle shaft 7, and a through hole 9 communicating with the peripheral groove 8 is formed in the first handle shaft 5.
Resin 60 is filled in the through hole 9 and the circumferential groove 8. When an impact is applied, the resin 60 is broken and the first handle shaft 5 and the second handle shaft 7 move relative to each other in the axial direction. Since the inner peripheral shape of the first handle shaft 5 and the outer peripheral shape of the second handle shaft 7 are non-circular, the first handle shaft 5 and the second handle shaft 7 are coupled so as to be able to rotate.
【００１４】その第１コラム２ａにアッパーブラケット
１１が溶接されている。そのアッパーブラケット１１
は、図３、図４、図５（１）に示すように、第１コラム
２ａの径方向外方に延び出る一対の支持部１１ａを有す
る。各支持部１１ａの一端から第１コラム２ａの軸方向
に直角に延び出る側壁部１１ｄと、各側壁部１１ｄの一
端から第１コラム２ａの軸方向に平行に延び出る突出部
１１ｅとを有する。各支持部１１ａに、ステアリングホ
イール側において開口する切欠１１ｂが形成されてい
る。各切欠１１ｂに連結部材２０が挿入されている。図
５の（２）に示すように、各連結部材２０は、各切欠１
１ｂの内面に入り込む上部２０ａと、各切欠１１ｂの周
囲の下面に沿う下部２０ｂとを有する。各支持部１１ａ
の切欠１１ｂの周縁に沿う部分に複数の通孔が形成さ
れ、各通孔に通じる通孔２０ｃが連結部材２０の下部２
０ｂに形成され、それら通孔に合成樹脂製のピン６１が
挿通される。各ピン６１は、各切欠１１ｂの周囲の上面
に沿う保持部材６１′に一体化されている。各連結部材
２０と各保持部材６１′の上面に、板金製プレート６３
が沿わせられ、そのプレート６３と各連結部材２０に形
成される通孔６３′、２０′に、車体側部材４５に植え
込まれるネジ軸４０が挿通される。そのネジ軸４０にね
じ合わされるナット４１と車体側部材４５とで、そのプ
レート６３と保持部材６１′と支持部１１ａと連結部材
２０とが挟み込まれる。なお、そのプレート６３と連結
部材２０の通孔６３′、２０′は、コラム軸方向が長手
方向の長孔とされ、製作誤差による各部材相互の位置ず
れに対応可能とされている。衝撃が作用すると、そのピ
ン６１が破断され、そのアッパーブラケット１１は第１
コラム２ａと共にプレート６３と保持部材６１′と連結
部材２０とに対し相対移動する。An upper bracket 11 is welded to the first column 2a. The upper bracket 11
As shown in FIG. 3, FIG. 4 and FIG. 5 (1), has a pair of support portions 11a extending outward in the radial direction of the first column 2a. It has a side wall portion 11d extending from one end of each support portion 11a at right angles to the axial direction of the first column 2a, and a protrusion portion 11e extending from one end of each side wall portion 11d in parallel to the axial direction of the first column 2a. A notch 11b that opens on the steering wheel side is formed in each support portion 11a. The connecting member 20 is inserted into each notch 11b. As shown in (2) of FIG. 5, each connecting member 20 has a cutout 1
It has the upper part 20a which penetrates into the inner surface of 1b, and the lower part 20b along the lower surface around each notch 11b. Each support 11a
A plurality of through holes are formed in the portion along the peripheral edge of the notch 11b, and the through holes 20c communicating with the respective through holes are formed in the lower portion 2 of the connecting member 20.
0b, and pins 61 made of synthetic resin are inserted into the through holes. Each pin 61 is integrated with a holding member 61 'along the upper surface around each notch 11b. On the upper surface of each connecting member 20 and each holding member 61 ′, a plate 63 made of sheet metal is provided.
The screw shaft 40 to be planted in the vehicle body side member 45 is inserted into the through holes 63 ′ and 20 ′ formed in the plate 63 and the respective connecting members 20. The plate 63, the holding member 61 ′, the support portion 11 a, and the connecting member 20 are sandwiched by the nut 41 screwed to the screw shaft 40 and the vehicle body-side member 45. The plate 63 and the through holes 63 'and 20' of the connecting member 20 are elongated holes in the longitudinal direction of the column, and are capable of coping with the positional deviation between the respective members due to manufacturing errors. When an impact is applied, the pin 61 is broken and the upper bracket 11 is
Together with the column 2a, they move relative to the plate 63, the holding member 61 ', and the connecting member 20.
【００１５】各プレート６３は、保持部材６１′と車体
側部材４５とで挟み込まれる上部６３ａと、その上部６
３ａの一端から第１コラム２ａの軸方向に直角に延び出
る中間部６３ｂと、その中間部６３ｂの一端から第１コ
ラム２ａの軸方向に平行に延び出る下部６３ｃとを有す
る。各中間部６３ｂはアッパーブラケット１１の各支持
部１１ａに形成される開口１１ｆに挿入されると共に各
側壁部１１ｄに沿い、各下部６３ｃは突出部１１ｅに沿
う。各下部６３ｃと突出部１１ｅとにリング６４が嵌合
される。これにより、衝撃が作用してアッパーブラケッ
ト１１がプレート６３に対し相対移動すると、そのアッ
パーブラケット１１の開口１１ｆの内面によりプレート
６３の中間部６３ｂが押され、図６に示すように、プレ
ート６３が塑性変形する。Each plate 63 has an upper portion 63a sandwiched between the holding member 61 'and the vehicle body side member 45, and an upper portion 6a thereof.
It has an intermediate portion 63b extending from one end of 3a at a right angle to the axial direction of the first column 2a, and a lower portion 63c extending from one end of the intermediate portion 63b in parallel to the axial direction of the first column 2a. Each intermediate portion 63b is inserted into an opening 11f formed in each supporting portion 11a of the upper bracket 11 and along each side wall portion 11d, and each lower portion 63c is along the protruding portion 11e. The ring 64 is fitted to each lower portion 63c and the protruding portion 11e. As a result, when an impact acts and the upper bracket 11 moves relative to the plate 63, the intermediate portion 63b of the plate 63 is pushed by the inner surface of the opening 11f of the upper bracket 11, and as shown in FIG. Plastically deforms.
【００１６】図１に示すように、その第２コラム２ｂに
ロアブラケット１０が溶接され、そのロアブラケット１
０を介し第２コラム２ｂは車体に取り付けられる。As shown in FIG. 1, a lower bracket 10 is welded to the second column 2b, and the lower bracket 1 is
The second column 2b is attached to the vehicle body through 0.
【００１７】図７、図８の（１）、（２）に示すよう
に、前記スペーサ３は例えばナイロン等の合成樹脂材に
より円筒形に型成形され、軸方向に沿う割り溝３ａを有
することで径方向に弾性変形可能とされ、また、一端に
内向きに突出するフランジ３ｂを有する。そのフランジ
３ｂは第２コラム２ｂの端面に接する。そのスペーサ３
は、その外周の周方向に間隔をおいた複数の領域に、軸
方向に沿って形成された複数の突条３ｄを有する。その
突条３ｄの形成されていない外周領域３ｅは平坦な円筒
面とされている。これにより、第１コラム２ａの内周面
は各突条３ｄを介しスペーサ３に接する。図８の（３）
に示すように、両コラム２ａ、２ｂ間に圧入された状態
でのスペーサ３の突条３ｄの高さ寸法ｈは、突条３ｄの
形成されていない部分３ｆの厚み寸法Ｄ３よりも小さく
されている。As shown in (1) and (2) of FIGS. 7 and 8, the spacer 3 is formed by molding a synthetic resin material such as nylon into a cylindrical shape and has a split groove 3a along the axial direction. It is elastically deformable in the radial direction and has a flange 3b protruding inward at one end. The flange 3b contacts the end surface of the second column 2b. The spacer 3
Has a plurality of ridges 3d formed along the axial direction in a plurality of circumferentially spaced regions on its outer circumference. The outer peripheral region 3e where the protrusion 3d is not formed is a flat cylindrical surface. As a result, the inner peripheral surface of the first column 2a contacts the spacer 3 via each ridge 3d. (3) in FIG.
As shown in, the height dimension h of the protrusion 3d of the spacer 3 in the state of being press-fitted between the columns 2a and 2b is smaller than the thickness dimension D3 of the portion 3f where the protrusion 3d is not formed. There is.
【００１８】図１２に示すように、そのスペーサ３の圧
入前の全厚み寸法Ｄ２は両コラム２ａ、２ｂの間の隙間
寸法Ｄ１よりも大きく、そのスペーサ３の圧入前の全厚
み寸法２から突条の高さ寸法Ｈを差し引いた寸法Ｄ３は
両コラム２ａ、２ｂの間の隙間寸法Ｄ１よりも小さくさ
れる。その圧入前のスペーサ３は第２コラム２ｂの外周
に嵌合され、その一端のフランジ３ｂは第２コラム２ｂ
の端面に当接される。そのスペーサ３の外周に第１コラ
ム２ａが圧入され、その圧入の際に各突条３ｄが圧縮変
形される。なお、スペーサ３の圧入前の全厚み寸法Ｄ２
がばらついたとしても、Ｄ２＞Ｄ１＞Ｄ３の関係が成立
して適正に衝撃エネルギーを吸収できるように、スペー
サ３の圧入前の全厚み寸法Ｄ２および突条３ｄの高さ寸
法Ｈが設定される。As shown in FIG. 12, the total thickness dimension D2 of the spacer 3 before press-fitting is larger than the gap dimension D1 between the columns 2a and 2b, and the spacer 3 projects from the total thickness dimension 2 of the spacer 3 before press-fitting. The dimension D3 obtained by subtracting the height H of the strip is made smaller than the gap dimension D1 between the columns 2a and 2b. The spacer 3 before press-fitting is fitted to the outer periphery of the second column 2b, and the flange 3b at one end thereof is the second column 2b.
Is abutted on the end face of. The first column 2a is press-fitted into the outer periphery of the spacer 3, and the protrusions 3d are compressed and deformed during the press-fitting. The total thickness dimension D2 of the spacer 3 before press fitting
Even if there are variations, the total thickness dimension D2 of the spacer 3 before press fitting and the height dimension H of the protrusion 3d are set so that the relationship of D2>D1> D3 is established and the impact energy can be properly absorbed. .
【００１９】上記構成において、車両の衝突により衝撃
力が作用すると、樹脂６０、６１が剪断されて衝撃エネ
ルギーが吸収され、両コラム２ａ、２ｂが軸方向相対移
動することによってプレート６３が塑性変形することで
衝撃エネルギーが吸収され、両コラム２ａ、２ｂを軸方
向相対移動させるのに要する荷重に応じた衝撃エネルギ
ーが吸収される。In the above structure, when an impact force acts due to a collision of a vehicle, the resins 60 and 61 are sheared to absorb the impact energy, and the columns 2a and 2b relatively move in the axial direction, whereby the plate 63 is plastically deformed. As a result, the impact energy is absorbed, and the impact energy corresponding to the load required to move the columns 2a and 2b relative to each other in the axial direction is absorbed.
【００２０】上記実施例によれば、スペーサ３の圧入前
の全厚み寸法Ｄ２は両コラム２ａ、２ｂの間の隙間寸法
Ｄ１よりも大きく、そのスペーサ３の圧入前の全厚み寸
法Ｄ２から突条３ｄの高さ寸法Ｈを差し引いた寸法Ｄ３
は両コラム２ａ、２ｂの間の隙間寸法Ｄ１よりも小さい
ので、スペーサ３の圧入時における圧縮変形量は、従来
のようにスペーサの内外周が平坦な円筒面である場合よ
りも小さくなる。これにより、加工公差に応じ両コラム
２ａ、２ｂの間の隙間寸法Ｄ１およびスペーサ３の圧入
前の全厚み寸法Ｄ２がばらついたとしても、そのばらつ
きによるスペーサ３の圧入時の圧縮変形量の変動は従来
より小さくなり、その圧入荷重に対応する両コラム２
ａ、２ｂの軸方向相対移動に要する荷重のばらつきも従
来より小さくできる。図１３における２点鎖線は、上記
実施例のスペーサ３の圧入前の全厚み寸法Ｄ２が一定で
あるとした場合における、両コラム２ａ、２ｂ間の隙間
寸法Ｄ１の設定値からのばらつきと軸方向相対移動に要
する荷重との関係を示し、その隙間寸法Ｄ１のばらつき
に対する荷重のばらつきは、実線で示した従来のスペー
サの荷重のばらつきよりも小さくなるのを確認できる。
これにより、両コラム２ａ、２ｂの軸方向相対移動に要
する荷重を適正範囲内に設定し、適正に衝撃エネルギー
を吸収できる。According to the above embodiment, the total thickness dimension D2 of the spacer 3 before press-fitting is larger than the gap dimension D1 between the columns 2a and 2b, and the total thickness dimension D2 of the spacer 3 before press-fitting is projected from the total thickness dimension D2. Dimension D3 less height dimension H of 3d
Is smaller than the gap dimension D1 between the columns 2a and 2b, the amount of compressive deformation when the spacer 3 is press-fitted is smaller than in the conventional case where the inner and outer peripheries of the spacer are flat cylindrical surfaces. As a result, even if the gap dimension D1 between the columns 2a and 2b and the total thickness dimension D2 of the spacer 3 before press-fitting vary depending on the working tolerance, the variation of the compression deformation amount at the press-fitting of the spacer 3 due to the variation. Both columns 2 that are smaller than conventional ones and can handle the press-fitting load
The variation in the load required for the axial relative movement of a and 2b can be made smaller than before. The two-dot chain line in FIG. 13 indicates the variation from the set value of the gap dimension D1 between the columns 2a and 2b and the axial direction when the total thickness dimension D2 of the spacer 3 before press-fitting is constant. It can be confirmed that the relation with the load required for the relative movement is shown, and the variation of the load with respect to the variation of the gap dimension D1 is smaller than the variation of the load of the conventional spacer shown by the solid line.
Thereby, the load required for the axial relative movement of both columns 2a, 2b can be set within an appropriate range, and the impact energy can be properly absorbed.
【００２１】また、両コラム２ａ、２ｂ間に圧入されて
いる状態でのスペーサ３の突条３ｄの高さ寸法ｈを、突
条３ｄの形成されていない部分３ｆの厚み寸法Ｄ３より
も小さくすることで、そのスペーサ３が合成樹脂材製で
金属等に比べ変形し易いものであっても、衝撃作用時に
おける突条３ｄの変形による両コラム２ａ、２ｂの相対
的な傾きを小さくし、また、その突条３ｄの形成されて
いない変形し難い部分３ｆにより両コラム２ａ、２ｂを
軸方向相対移動するように案内できるので、両コラム２
ａ、２ｂを円滑に軸方向相対移動させて適正に衝撃エネ
ルギーを吸収できる。Further, the height dimension h of the protrusion 3d of the spacer 3 in a state of being press-fitted between the columns 2a and 2b is made smaller than the thickness dimension D3 of the portion 3f where the protrusion 3d is not formed. Thus, even if the spacer 3 is made of a synthetic resin material and is more easily deformed than metal or the like, the relative inclination between the columns 2a and 2b due to the deformation of the protrusion 3d at the time of impact is reduced, and , The columns 3a and 2b, which are not formed with the protrusions 3d and are not easily deformed, can guide the two columns 2a and 2b so as to relatively move in the axial direction.
Impact energy can be properly absorbed by smoothly moving a and 2b relative to each other in the axial direction.
【００２２】なお、本発明は上記実施例に限定されな
い。例えば、上記実施例ではスペーサ３を円筒形状とし
たが、図９に示すように、円筒形の一端において開口す
る複数の切欠３ｇを有する形状とし、その切欠３ｇを除
く外周全域に突条３ｄを設けてもよい。また、上記実施
例では円筒形のスペーサ３の外周の周方向に間隔をおい
た複数の領域に突条３ｄを形成したが、図１０に示すよ
うに、外周の全領域に突条３ｄを形成してもよい。な
お、この場合はスペーサ３の圧入時の圧縮変形量は従来
よりは少ないが上記実施例よりも多くなるため、図１３
において破線で示すように、両コラム２ａ、２ｂ間の隙
間寸法Ｄ１の設定値からのばらつきに対する両コラム２
ａ、２ｂの軸方向相対移動に要する荷重のばらつきは、
実線で示した従来のスペーサよりも小さくなるが、上記
実施例よりは大きくなる。また、上記実施例ではスペー
サ３の一端から内向きに突出するフランジ３ｂを第２コ
ラム２ｂの端面に当接させたが、図１１に示すように、
スペーサ３の一端から外向きに突出するフランジ３ｈを
第１コラム２ａの端面に当接させてもよく、この場合、
突条はスペーサ３の内周に設ける。また、スペーサ３の
内周と外周の両方に突条を設けてもよい。また、上記実
施例ではスペーサ３の軸方向に沿って突条３ｄを設けた
が、スペーサの周方向に沿って突条を設けてもよい。ま
た、上記実施例ではスペーサ３の突条３ｄの断面形状が
略三角形のものについて説明したが、その断面形状を略
台形としてもよい。The present invention is not limited to the above embodiment. For example, although the spacer 3 has a cylindrical shape in the above-described embodiment, as shown in FIG. 9, it has a shape having a plurality of notches 3g that open at one end of the cylinder, and the protrusions 3d are provided on the entire outer periphery except the notch 3g. It may be provided. Further, in the above-described embodiment, the ridges 3d are formed in a plurality of circumferentially spaced regions on the outer periphery of the cylindrical spacer 3, but as shown in FIG. 10, the ridges 3d are formed in the entire outer periphery. You may. In this case, the amount of compressive deformation when the spacer 3 is press-fitted is smaller than that of the conventional example, but is larger than that of the above-described embodiment.
As indicated by a broken line in FIG. 2, both columns 2a and 2b are provided with respect to variations in the gap dimension D1 from the set value.
The variation of the load required for the axial relative movement of a and 2b is
It is smaller than the conventional spacer shown by the solid line, but larger than the above-mentioned embodiment. Further, in the above embodiment, the flange 3b protruding inward from one end of the spacer 3 is brought into contact with the end face of the second column 2b, but as shown in FIG.
The flange 3h protruding outward from one end of the spacer 3 may be brought into contact with the end surface of the first column 2a. In this case,
The ridge is provided on the inner circumference of the spacer 3. Further, ridges may be provided on both the inner circumference and the outer circumference of the spacer 3. Further, although the protrusion 3d is provided along the axial direction of the spacer 3 in the above embodiment, the protrusion may be provided along the circumferential direction of the spacer. Further, in the above-described embodiment, the ridge 3d of the spacer 3 has a substantially triangular sectional shape, but the sectional shape may be substantially trapezoidal.
【図１】本発明の実施例のステアリングコラムの断面図FIG. 1 is a sectional view of a steering column according to an embodiment of the present invention.
【図２】そのステアリングコラムの部分断面図FIG. 2 is a partial sectional view of the steering column.
【図３】そのステアリングコラムの部分側面図FIG. 3 is a partial side view of the steering column.
【図４】そのステアリングコラムの部分平面図FIG. 4 is a partial plan view of the steering column.
【図５】そのステアリングコラムの（１）は部分断面
図、（２）は連結部材と保持部材の斜視図5 is a partial sectional view of the steering column (1), and (2) is a perspective view of a connecting member and a holding member. FIG.
【図６】そのステアリングコラムの衝撃作用後の側面図FIG. 6 is a side view of the steering column after impact is applied.
【図７】そのステアリングコラムのスペーサの斜視図FIG. 7 is a perspective view of a spacer of the steering column.
【図８】そのスペーサの（１）は縦断面図、（２）は横
断面図、（３）は両コラム間への圧入状態での部分断面
図8 (a) is a vertical sectional view, FIG. 8 (2) is a horizontal sectional view, and FIG. 8 (3) is a partial sectional view in a press-fitted state between both columns.
【図９】本発明の変形例のスペーサの斜視図FIG. 9 is a perspective view of a spacer according to a modified example of the present invention.
【図１０】本発明の変形例のスペーサの斜視図FIG. 10 is a perspective view of a spacer according to a modified example of the present invention.
【図１１】本発明の変形例のステアリングコラムの部分
断面図FIG. 11 is a partial cross-sectional view of a steering column according to a modified example of the present invention.
【図１２】本発明のステアリングコラムの作用説明図FIG. 12 is an explanatory view of the operation of the steering column of the present invention.
【図１３】両コラム間の隙間のばらつきと両コラムを軸
方向相対移動させるのに要する荷重との関係を示す図FIG. 13 is a diagram showing the relationship between the variation in the gap between both columns and the load required to relatively move both columns in the axial direction.
【図１４】従来のステアリングコラムの作用説明図FIG. 14 is an operation explanatory view of a conventional steering column.
２ａ 第１コラム ２ｂ 第２コラム ３ スペーサ ３ｄ 突条 2a 1st column 2b 2nd column 3 Spacer 3d Projection
Claims (3)
筒状のスペーサを介し圧入されている衝撃吸収式ステア
リングコラムにおいて、そのスペーサは、合成樹脂材に
より形成されると共に外周および内周のうちの少なくと
も一方に形成される複数の突条を有し、その第１コラム
の内周および第２コラムの外周のうちの少なくとも一方
は、それら突条を介しスペーサに接することを特徴とす
る衝撃吸収式ステアリングコラム。1. A shock absorbing steering column in which a tubular second column is press-fitted into a tubular first column via a tubular spacer, the spacer being formed of a synthetic resin material and at the outer periphery and A plurality of protrusions are formed on at least one of the inner circumferences, and at least one of the inner periphery of the first column and the outer periphery of the second column is in contact with the spacer through the protrusions. Shock absorption type steering column.
突条の高さ寸法は、突条の形成されていない部分の厚み
寸法よりも小さくされている請求項１に記載の衝撃吸収
式ステアリングコラム。2. The shock absorbing steering system according to claim 1, wherein the height dimension of the protrusion of the spacer press-fitted between both columns is smaller than the thickness dimension of the portion where the protrusion is not formed. column.
テアリングコラムを製造するに際し、そのスペーサの圧
入前の全厚み寸法を両コラムの間の隙間寸法よりも大き
くし、そのスペーサの圧入前の全厚み寸法から突条の高
さ寸法を差し引いた寸法を両コラムの間の隙間寸法より
も小さくし、各突条を圧縮変形させつつ第１コラムに第
２コラムをスペーサを介し圧入することを特徴とする衝
撃吸収式ステアリングコラムの製造方法。3. When manufacturing the shock absorbing steering column according to claim 1 or 2, the total thickness dimension of the spacer before press-fitting is made larger than the clearance dimension between both columns, and the spacer before press-fitting. Make the dimension of the total thickness of the product minus the height of the ridges smaller than the gap between the columns, and press-fit the second column into the first column via the spacer while compressing and deforming each ridge. A method of manufacturing a shock absorbing steering column, characterized by:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30989794A JP3611885B2 (en) | 1994-11-18 | 1994-11-18 | Shock absorbing steering column and manufacturing method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30989794A JP3611885B2 (en) | 1994-11-18 | 1994-11-18 | Shock absorbing steering column and manufacturing method thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08142877A true JPH08142877A (en) | 1996-06-04 |
| JP3611885B2 JP3611885B2 (en) | 2005-01-19 |
Family
ID=17998646
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP30989794A Expired - Fee Related JP3611885B2 (en) | 1994-11-18 | 1994-11-18 | Shock absorbing steering column and manufacturing method thereof |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3611885B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004108502A1 (en) | 2003-06-03 | 2004-12-16 | Nsk Ltd. | Impact absorbing steering column device for vehicle |
| GB2368894B (en) * | 2000-11-14 | 2005-07-20 | Nastech Europ Ltd | Steering column assembly for a vehicle |
| US7168741B2 (en) | 2002-11-28 | 2007-01-30 | Koyo Seiko Co., Ltd | Steering apparatus |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4868213B2 (en) | 2005-12-21 | 2012-02-01 | アイシン精機株式会社 | Energy absorbing steering column |
-
1994
- 1994-11-18 JP JP30989794A patent/JP3611885B2/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2368894B (en) * | 2000-11-14 | 2005-07-20 | Nastech Europ Ltd | Steering column assembly for a vehicle |
| US7168741B2 (en) | 2002-11-28 | 2007-01-30 | Koyo Seiko Co., Ltd | Steering apparatus |
| WO2004108502A1 (en) | 2003-06-03 | 2004-12-16 | Nsk Ltd. | Impact absorbing steering column device for vehicle |
| US7506893B2 (en) | 2003-06-03 | 2009-03-24 | Nsk Ltd. | Impact absorbing steering column device for vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3611885B2 (en) | 2005-01-19 |
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