JP4581164B2

JP4581164B2 - Automotive pedal device and damper suitable for the same

Info

Publication number: JP4581164B2
Application number: JP32999699A
Authority: JP
Inventors: 正光小島; 美照五十嵐; 勝利熊沢
Original assignee: Oiles Corp
Current assignee: Oiles Corp
Priority date: 1999-11-19
Filing date: 1999-11-19
Publication date: 2010-11-17
Anticipated expiration: 2019-11-19
Also published as: JP2001147729A

Description

【０００１】
【発明の属する技術分野】
本発明は、自動車のアクセルペダルアーム、ブレーキペダルアーム、クラッチペダルアーム等に適宜の制動を与えるダンパを具備したペダル装置及びこのペダル装置に用いて好適なダンパに関する。
【０００２】
【発明が解決しようとする課題】
自動車の低燃費化、二酸化炭素低減のために自動車エンジンの燃料噴射の木目細かな制御が必要とされ、これに伴ってアクセルペダルの踏み込みによるスロットルバルブ開度調整を電子的に行うことが実用化されている。
【０００３】
エンジンの燃料噴射を電子制御で行う自動車では、アクセルペダルアームとスロットルバルブとの間に配されるアクセルワイヤが通常省かれるが、このアクセルワイヤレスの自動車では、アクセルワイヤ付きの自動車と比較して、ペダル踏み力に対する反力が異なる上に、ペダル踏み込み量とペダル踏み力との関係におけるヒステリシス特性が実質的に狭いループ、換言すればペダル踏み込み量に対するペダル踏み力特性が直線的になるために、アクセルワイヤ付きの自動車に乗り慣れた一般の運転者がアクセルワイヤレスの自動車を運転すると、ペダルを踏み込み過ぎて、燃料を今まで以上に消費してしまったり、定速走行時におけるペダル踏み込み量を一定に維持することが困難となる虞がある。
【０００４】
ペダル踏み力に対して大きな反力を得て踏み込み過ぎを防止するために、ペダルアームを初期回動位置に復帰させるリターンスプリングのばね力を単に大きくすると、定速走行時にリターンスプリングからの大きな反力によりペダル踏み足に早期の疲労を生じさせる虞がある。
【０００５】
そこで、一端をコイルばねを介して終端させると共に、固定された螺旋管内を挿通させたダミーケーブルの他端にペダルアームを連結して、当該ダミーケーブルにより従来のアクセルワイヤ付きのものと同様なペダル踏み込み量とペダル踏み力との関係におけるヒステリシス特性を有する反力が得られるようにすることが提案されているが、このダミーケーブルを用いる解決策は、ダミーケーブルを設置するための比較的大きなスペースを必要とするために、トラックやＲＶ車のようにスペースに十分余裕のある大型車種の自動車にしか採用できず、加えて、ダミーケーブルによる反力調整は比較的困難であって、コスト高となる虞がある上に、ヒステリシス特性を得るために、金属製のダミーケーブルを管の樹脂被覆内面に摺動させて、金属製のダミーケーブルと管の樹脂被覆内面との間に摺動抵抗を生じさせているが、この摺動による摩耗で長期の使用において大きな特性変化が生じる虞がある。
【０００６】
以上の問題は、アクセルペダルアームに限って生じるものではなく、上記のようなダミーケーブル等を用いて適宜の復帰回動抵抗を生じさせ、ヒステリシス特性を得る場合にも生じ得るのである。
【０００７】
本発明は、前記諸点に鑑みてなされたものであって、その目的とするところは、ペダル踏み込み量に応じて、そのペダル踏み込み量でのペダルアームの回動位置を一定に維持できるペダル踏み込み力の範囲を大きくでき、しかも、ダミーケーブルに比較して、コンパクトに設置できる上に、ヒステリシス特性をもった反力調整を極めて簡単に行うことができ、特性変化の少ないダンパを具備したペダル装置及びこのペダル装置に用いて好適なダンパを提供することにある。
【０００８】
【課題を解決するための手段】
本発明の第一の態様の自動車のペダル装置は、ペダルアームの回動に漸次増大する抵抗力を付与するダンパを具備しており、このダンパは、ダンパ本体と、このダンパ本体の軸周りの方向且つ軸方向に不動に配されている不動体と、この不動体に対面していると共に、ペダルアームの回動が伝達されて、軸周りの方向に回転される回転体と、この回転体の回転において前記抵抗力として漸次増大する摩擦抵抗力を生じさせる摩擦抵抗力発生手段とを具備しており、回転体は、回転体本体と、この回転体本体の回転により回転されると共に軸方向に可動な可動体とを具備しており、摩擦抵抗力発生手段は、不動体に対面する可動体の一方の面に形成された傾斜面と、可動体に対面する不動体の一方の面に形成されて前記傾斜面に面接触する傾斜面と、可動体を不動体に向かって弾性的に付勢して、両傾斜面を互いに押圧させるばね手段とを具備している。
【０００９】
第一の態様のペダル装置によれば、ペダル踏み込みによるペダルアームの回動で回転体が回転されると、摩擦抵抗力発生手段において増大する摩擦抵抗力が生じるために、この抵抗力により例えばアクセルペダルを踏み込み過ぎて、燃料を今まで以上に消費したりすることをなくし得、しかも、ペダル踏み込み量に応じてそのペダル踏み込み量でのペダルアームの回動位置を一定に維持できるペダル踏み込み力の範囲を大きくできる結果、低速から高速の各速度での定速走行時に当該速度に応じてペダル踏み込み量を容易に一定に維持でき、ペダル踏み足に早期の疲労を生じさせる等の不都合を解消でき、しかも、面接触する両傾斜面における摩擦係数を適宜設定することにより概略ペダルアームの回動に付与できる抵抗力を決定し得、ペダル踏み込み量とペダル踏み力との関係におけるヒステリシス特性をもった反力調整を極めて簡単に行うことができる。。
【００１０】
本発明の第二の態様の自動車のペダル装置では、第一の態様のペダル装置において、不動体は、軸方向に突出してダンパ本体に一体的に形成された突起を具備しており、可動体は、可動体本体と、軸方向であって不動体に向かって突出して可動体本体に一体的に形成された突起とを具備しており、両傾斜面の夫々は、両突起の夫々に形成されている。
【００１１】
第二の態様のペダル装置によれば、摩擦抵抗力発生手段の両傾斜面の夫々を不動体と可動体との夫々の突起に形成し、両突起の傾斜面同士を面接触させるために、極めてコンパクトなものとすることができ、小さなスペースを有効に利用して設置できる。
【００１２】
本発明の第三の態様の自動車のペダル装置では、第一又は第二の態様のペダル装置において、回転体本体は、ダンパ本体に摺動回転自在に接触する鍔部を有しており、摩擦抵抗力発生手段は、ダンパ本体と鍔部との間の互いの摺動回転自在面を更に具備しており、ばね手段は、ダンパ本体と鍔部との間の互いの摺動回転自在面を互いに押圧させるようになっている。
【００１３】
第三の態様のペダル装置によれば、摩擦抵抗力発生手段が、傾斜面に加えて、摺動回転自在面を更に具備しているために、摩擦抵抗力を分担して発生できて傾斜面での負担を軽減でき、しかも、傾斜面と摺動回転自在面とにおける摩擦係数を適宜設定することにより概略ペダルアームの回動に付与できる抵抗力を決定し得るため、第一の態様のペダル装置と同様に、ヒステリシス特性をもった反力調整を極めて簡単に行うことができる。
【００１４】
なお、第三の態様のペダル装置において、摺動回転自在面の夫々もまた、傾斜させて形成してもよい。
【００１５】
本発明の第四の態様の自動車のペダル装置では、第一から第三のいずれかの態様のペダル装置において、回転体本体は、円筒部と、この円筒部に一体的に形成されたばね受け部とを具備しており、可動体は、軸方向に可動に円筒部に装着されており、ばね手段は、ばね受け部と可動体との間に配されている。
【００１６】
第四の態様のペダル装置によれば、回転体の回転と共に回転されるばね受け部と可動体との間にばね手段が配されているために、回転体の回転でばね手段が捩じられることがなく、ばね手段の捩じれで動作不良が生じるようなことをなくし得る。
【００１７】
本発明の第五の態様の自動車のペダル装置では、第一から第四のいずれかの態様のペダル装置において、ペダルアームの回動は、回転自在軸を介して回転体に伝達されるようになっている。
【００１８】
なお、ペダルアームの回動を、回転自在軸を介して直接回転体に伝達してもよいが、ペダルアームと回転自在軸との間又は回転自在軸と回転体との間に歯車機構等を介在させてもよい。
【００１９】
本発明の装置におけるペダルアームとしては、好ましくは、本発明の第六の態様のペダル装置のように、アクセルペダルアームであるが、これに代えて、ブレーキペダルアーム又はクラッチペダルアーム等であってもよい。
【００２０】
ダンパ本体、不動体及び回転体の形成材料としては、ベース材として樹脂からなり、これに充填材が含有されているのが好ましい。なお、ダンパ本体の形成材料としては、場合によっては、ほぼ剛体とみなせる金属でもよい。
【００２１】
本発明のダンパは、上記のいずれかの態様の装置に用いられて好適なものであって、基本的に、ダンパ本体と、ダンパ本体の軸周りの方向且つ軸方向に不動に配されている不動体と、この不動体に対面していると共に、ペダルアームの回動が伝達される回転体と、この回転体の回転において漸次増大する摩擦抵抗力を生じさせる摩擦抵抗力発生手段とを具備しており、回転体は、回転体本体と、この回転体本体の回転により回転されると共に軸方向に可動な可動体とを具備しており、摩擦抵抗力発生手段は、不動体に対面する可動体の一方の面に形成された傾斜面と、可動体に対面する不動体の一方の面に形成されて前記傾斜面に面接触する傾斜面と、可動体を不動体に向かって弾性的に付勢して、両傾斜面を互いに押圧させるばね手段とを具備している。
【００２２】
斯かるダンパでは、所望のヒステリシス特性を得ることができ、自動車のアクセルペダルアーム等の回転自在軸に連結することにより、上記のような好ましい特性を得ることができる。
【００２３】
なお、本発明に係るダンパは、自動車のペダルアームに用いられるものに限定されないのであって、上記のような特性が要求される機構、装置に用いてもよい。
【００２４】
【発明の実施の形態】
次に本発明及びその実施の形態を、図に示す好ましい例を参照して説明する。
なお、本発明はこれら例に何等限定されないのである。
【００２５】
図１から図８において、本例の自動車のペダル装置１は、支持フレーム２と、支持フレーム２に軸Ａを中心として軸Ａ周りの方向であるＲ方向に回動自在に支持されたペダルアーム、本例では剛性金属製のアクセルペダルアーム３と、アクセルペダルアーム３を初期回動位置に回動付勢するばね手段４と、アクセルペダルアーム３のＲ方向の回動に漸次増大する抵抗力を付与するダンパ５と、アクセルペダルアーム３を初期回動位置でその回動を停止させるストッパ（図示せず）とを具備している。
【００２６】
支持フレーム２は、車体１１にリベット又はボルト１２等によりその底板部１３で固定されており、回転自在軸１４をその両側壁部１５及び１６で回転自在に支持している。
【００２７】
アクセルペダルアーム３は、先端にアクセルペダル（図示せず）を有して、回転自在軸１４の一端部１７に固着されており、当該回転自在軸１４を介して支持フレーム２にＲ方向に回動自在に支持されている。
【００２８】
ばね手段４は、本例では、コイルばね、特に好ましくは捩りコイルばね１８からなり、一端部１９が支持フレーム２の側壁部１５に係合し、他端部２０がアクセルペダルアーム３に係合して、図２においてアクセルペダルアーム３をＲ方向において反時計回りの方向に常時弾性的に付勢している。ばね手段４としては、捩りコイルばね１８に代えて、圧縮ばね、特に圧縮コイルばねでもよい。
【００２９】
ダンパ５は、支持フレーム２の側壁部１５にボルト２１等により固定されるダンパ本体２２と、ダンパ本体２２内に、当該ダンパ本体２２に対してその軸Ａ方向及びＲ方向で不動に配された不動体２３と、一方では、不動体２３に対面しており、他方では、その環状の面２４でダンパ本体２２の固定面２５にＲ方向に摺動回転自在に接触した回転体２６と、回転体２６のＲ方向の回転において抵抗力として漸次増大する摩擦抵抗力を生じさせる摩擦抵抗力発生手段２７とを具備している。
【００３０】
ダンパ本体２２は、円筒状の内周面３０を有した円筒部３１と、円筒部３１の一端面に一体的に形成された鍔部３２と、円筒部３１の内周面３０に径方向内方向に突出して一体的に形成された環状板部３３とを具備している。
【００３１】
鍔部３２は、長軸方向の両端部に貫通孔３５及び３６を夫々有しており、貫通孔３５及び３６を通ったボルト２１等により鍔部３２においてダンパ本体２２は、側壁部１５に固定支持されており、環状板部３３の中央貫通孔３７に、後述の回転体本体３８の円筒部３９が回転自在に挿通されている。
【００３２】
不動体２３は、図４に特に詳しく示すように、後述の可動体本体４１の環状の面４２に対面する環状板部３３の一方の面４３の外周側に、軸Ａ方向に突出して一体的に形成された３個の突起４４を具備しており、斯かる突起４４からなる本例の不動体２３は、軸Ａ方向及びＲ方向に不動にされている。突起４４は、Ｒ方向において等角度間隔に配されている。面４３には、段部４５を規定するように、突起４４に連接して凹所４６が形成されている。
【００３３】
回転体２６は、回転体本体３８と、回転体本体３８に対して軸Ａ方向に可動であって、回転体本体３８のＲ方向の回転と共に回転される可動体５１とを具備している。
【００３４】
回転体本体３８は、円筒部３９と、円筒部３９の一端に径方向外方向に一体的に形成された鍔部５５と、円筒部３９の一端の外周面のねじ部５６に螺着されて固定された有底円筒状のばね受け体５７とを具備している。
【００３５】
可動体５１は、円筒部３９の外周面に、軸方向に伸び且つ互いにＲ方向に平行に配されて形成された複数のスプライン溝６１の夫々に嵌合する複数のスプライン突起６２を内周面に有し、この円筒部３９の外周面へのスプライン結合により軸Ａ方向に摺動自在であって、且つ円筒部３９のＲ方向の回転と共に回転されるように、当該円筒部３９の外周面に装着された環状の可動体本体４１と、図７に特に詳細に示すように、軸Ａ方向であって不動体２３である突起４４に向かって突出して可動体本体４１の一方の面４２の外周側に一体的に形成された３個の突起６３とを具備しており、突起６３は、可動体本体４１の一方の面４２にＲ方向において等角度間隔に配されている。面４２には、段部６４を規定するように、突起６３に連接して凹所６５が形成されている。
【００３６】
円筒部３９内には、回転自在軸１４の他端部７０が固定的に挿着されるようになっており、円筒部３９、円筒部３９に一体的に形成された鍔部５５、円筒部３９に固着されたばね受け体５７、円筒部３９にスプライン結合された可動体本体４１及び可動体本体４１に一体的に形成された突起６３の夫々は、回転自在軸１４のＲ方向の回転と共に、同様にＲ方向に回転されるようになっている。
【００３７】
摩擦抵抗力発生手段２７は、突起４４の夫々に形成された軸Ａ方向に直交する方向に対して傾斜角θを有した傾斜面７１と、Ｒ方向の回転において傾斜面７１に面接触するように突起６３の夫々に形成されており、傾斜面７１と同様に軸Ａ方向に直交する方向に対して傾斜角θを有した傾斜面７２と、鍔部５５及び環状板部３３の互いの摺動回転自在面である面２４及び固定面２５と、円筒部３９の外周面及び可動体本体４１の内周面のスプライン結合における軸Ａ方向の相互摺動面と、可動体本体４１を不動体２３に向かって弾性的に付勢する圧縮コイルばね７３とを具備している。
【００３８】
傾斜面７１及び７２は、互いに面接触するように相補的に形成されており、圧縮コイルばね７３は、傾斜面７１及び７２の相互並びに面２４及び固定面２５の相互を互いに押圧させるように、弾性的に縮められてばね受け体５７内に円筒部３９と同心に且つ可動体本体４１とばね受け体５７の底部７５との間に一端で可動体本体４１に他端でばね受け体５７の底部７５に夫々接触して配されている。
【００３９】
傾斜面７１及び７２は、突起６３のＲ方向の回転において、コイルばね７３の弾性力に抗して可動体本体４１を不動体２３から軸Ａ方向に離反させてばね受け体５７の底部７５に接近させて、コイルばね７３のばね反力を増大させることにより、前記摩擦抵抗力を増大させるようになっている。
【００４０】
なお、凹所４６の夫々には、突起６３の夫々の軸Ａ方向の先端が落ち込み、凹所６５の夫々には、突起４４の夫々の軸Ａ方向の先端が落ち込み、而して、段部４５及び段部６４により傾斜面７１と傾斜面７２との初期面接触位置が規定されるようになっている。
【００４１】
以上のペダル装置１を具備した車両、例えば自動車では、アクセルペダルの踏み込みで、アクセルペダルアーム３が、コイルばね１８の弾性力に抗して図２においてＲ方向において時計回りの方向に回動されると、アクセルペダルアーム３の回動角を検出する検出器を含む図示しない電子制御装置によりエンジンに対する燃料噴射が促進されて加速され、逆に、アクセルペダルの踏み込み解除で、アクセルペダルアーム３が、コイルばね１８の弾性力により図２におけるＲ方向において反時計回りの方向に回動されると、図示しない電子制御装置によりエンジンに対する燃料噴射が減少されて減速される。
【００４２】
ペダル装置１では、アクセルペダルの踏み込みによるアクセルペダルアーム３の回動で、回転体２６がＲ方向に回転されると、突起６３もＲ方向に回転されて、突起６３のＲ方向の回転により、傾斜面７２で傾斜面７１に面接触した突起６３を有した可動体５１は、図９に示すように、軸Ａ方向においてコイルばね７３の弾性力に抗して底部７５に向かって移動され、逆に、ペダル踏み込みが解除されると、コイルばね１８の弾性力によりアクセルペダルアーム３は、元の位置に復帰され、同じく、可動体５１は、図１に示すように、元の位置に復帰される。
【００４３】
そして、ペダル装置１では、コイルばね７３の漸次増大する弾性力により互いに押し付けられた傾斜面７１と傾斜面７２とにおける摩擦抵抗、面２４と固定面２５とにおける摩擦抵抗並びに円筒部３９と可動体本体４１とのスプライン結合における摩擦抵抗により、図１０の線ｂ−ｃで示すように、ペダル踏み込みに基づくアクセルペダルアーム３の回動に適宜の漸次増大する抵抗力（反力）が付与され、而して、アクセルペダルを踏み込み過ぎて、燃料を必要以上に消費するような事態をなくし得、また、角度αｅｆ°でのペダル踏み込み解除では、アクセルペダルアーム３は、コイルばね１８の弾性力により小さな抵抗力をもって早期に初期位置に回動復帰されることになる。
【００４４】
加えて、ペダル装置１では、ペダル踏み込み後、例えば定常走行時に相当する角度αｅｆ°でペダル踏み込みを維持する場合には、図１０に示すように、ペダル踏み力をＴｅからＴｆまで減少させても、傾斜面７１と傾斜面７２とにおける摩擦抵抗、面２４と固定面２５とにおける摩擦抵抗並びに円筒部３９と可動体本体４１とのスプライン結合における摩擦抵抗に基づくペダルアーム回動角とペダル踏み力とのヒステリシス特性ａ−ｂ−ｅ−ｆにより、そのアクセルペダルアーム３の回動角αｅｆ°を維持できるために、ペダル踏み足に早期の疲労を生じさせる等の不都合を解消できる。すなわちペダル装置１では、ペダル踏み込み量に応じてそのペダル踏み込み量でのアクセルペダルアーム３の回動角αｅｆ°を一定に維持できるペダル踏み力Ｔの範囲Ｔｅ−Ｔｆを大きくできる結果、低速から高速の各速度での定速走行時に当該速度に応じてペダル踏み込み量を容易に一定に維持でき、ペダル踏み足に早期の疲労を生じさせる等の不都合を解消できる。
【００４５】
更にペダル装置１によれば、傾斜面７１と傾斜面７２とにおける摩擦抵抗、面２４と固定面２５とにおける摩擦抵抗並びに円筒部３９と可動体本体４１とのスプライン結合における摩擦抵抗により概略アクセルペダルアーム３の回動に付与できる抵抗力を決定し得るため、ヒステリシス特性をもった反力調整を極めて簡単に行うことができ、その上、夫々の値を適宜設定することにより、極めてコンパクトなものとすることができ、小さなスペースを有効に利用して設置できる。
加えて、ペダル装置１によれば、摩擦抵抗力発生手段２７が、傾斜面７１及び７２に加えて、摺動回転自在面である面２４及び固定面２５を更に具備しているために、摩擦抵抗力を分担して発生できて傾斜面７１及び７２での負担を軽減できる。
【００４６】
また、ペダル装置１によれば、コイルばね７３は、相互に相対回転しない可動体本体４１とばね受け体５７の底部７５との間に配されているために、可動体本体４１の回転においても捩られることがなく、而して、コイルばね７３の捩じれによる作動不良等の不都合が生じることがない。
【００４７】
【発明の効果】
本発明によれば、ペダル踏み込み量に応じて、そのペダル踏み込み量でのペダルアームの回動位置を一定に維持できるペダル踏み込み力の範囲を大きくでき、しかも、ダミーケーブルに比較して、コンパクトに設置できる上に、ヒステリシス特性をもった反力調整を極めて簡単に行うことができ、特性変化の少ないダンパを具備したペダル装置及びこのペダル装置に用いて好適なダンパを提供することができる。
【図面の簡単な説明】
【図１】本発明の好ましい実施の形態の例の正面断面図である。
【図２】図１に示す例の左側面図である。
【図３】図１に示す例のダンパの右側面図である。
【図４】（ａ）は、図１に示す例の環状板部の左側面図であり、（ｂ）は、環状板部の一方の面に一体成形された突起、凹所及び段部を展開して示す説明図である。
【図５】図１に示す例の可動体の左側面図である。
【図６】可動体の一方の面に形成された突起などを省略した図５に示す可動体のＶＩ−ＶＩ線矢視断面図である。
【図７】（ａ）は、図１に示す例の可動体の右側面図であり、（ｂ）は、可動体の一方の面に一体成形された突起、凹所及び段部を展開して示す説明図である。
【図８】図１に示す例の回転体本体の円筒部及び鍔部の正面図である。
【図９】図１に示す例のダンパの動作説明図である。
【図１０】図１に示す例のペダルアーム回動角とペダル踏み力との関係図である。
【符号の説明】
１自動車のペダル装置
３アクセルペダルアーム
５ダンパ
２２ダンパ本体
２３不動体
２６回転体
２７摩擦抵抗力発生手段[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a pedal device including a damper that applies appropriate braking to an accelerator pedal arm, a brake pedal arm, a clutch pedal arm, and the like of an automobile, and a damper suitable for use in the pedal device.
[0002]
[Problems to be solved by the invention]
In order to reduce fuel consumption and reduce carbon dioxide in automobiles, it is necessary to finely control the fuel injection of automobile engines. Along with this, it is practical to electronically adjust the throttle valve opening by depressing the accelerator pedal. Has been.
[0003]
In an automobile in which the fuel injection of the engine is electronically controlled, the accelerator wire arranged between the accelerator pedal arm and the throttle valve is usually omitted, but in this accelerator wireless automobile, compared to an automobile with an accelerator wire, Since the reaction force against the pedal depression force is different and the hysteresis characteristic in the relationship between the pedal depression amount and the pedal depression force is a substantially narrow loop, in other words, the pedal depression force characteristic with respect to the pedal depression amount is linear, When a general driver who is accustomed to a car with an accelerator wire is driving an accelerator wireless car, the pedal will be depressed too much and fuel will be consumed more than before, or the amount of pedal depression during constant speed driving will be constant. It may be difficult to maintain the temperature.
[0004]
In order to obtain a large reaction force against the pedal depressing force and prevent excessive depression, simply increasing the spring force of the return spring that returns the pedal arm to the initial rotation position will result in a large reaction from the return spring during constant speed driving. There is a risk of premature fatigue of the pedal foot by force.
[0005]
Therefore, one end is terminated via a coil spring, and a pedal arm is connected to the other end of the dummy cable inserted through the fixed spiral tube, and the pedal is the same as that with a conventional accelerator wire by the dummy cable. Although it has been proposed to obtain a reaction force having a hysteresis characteristic in the relationship between the depression amount and the pedal depression force, the solution using this dummy cable is a relatively large space for installing the dummy cable. Therefore, it can only be used for large-sized vehicles with sufficient space, such as trucks and RV vehicles. In addition, reaction force adjustment with a dummy cable is relatively difficult, resulting in high costs. In order to obtain hysteresis characteristics, a metal dummy cable is slid on the resin-coated inner surface of the tube to Although cause sliding resistance between the manufacturing of the dummy cable and the resin-coated inner surface of the tube, there is a possibility that a large characteristic change occurs in long-term use in wear due to the sliding.
[0006]
The above problem does not occur only in the accelerator pedal arm, but can also occur when hysteresis characteristics are obtained by generating an appropriate return rotation resistance using the dummy cable as described above.
[0007]
The present invention has been made in view of the above-described points, and an object of the present invention is to provide a pedal depression force capable of maintaining a constant rotation position of the pedal arm at the pedal depression amount according to the pedal depression amount. In addition to being able to be installed more compactly than a dummy cable, it is possible to adjust the reaction force with hysteresis characteristics very easily, and to provide a pedal device equipped with a damper with little characteristic change. An object of the present invention is to provide a damper that is suitable for use in this pedal device.
[0008]
[Means for Solving the Problems]
The pedal device for an automobile according to the first aspect of the present invention includes a damper that applies a gradually increasing resistance force to the rotation of the pedal arm. The damper includes a damper main body and an axis around the damper main body. A non-moving body arranged in a fixed direction and in an axial direction, a rotating body facing the non-moving body, a rotation of a pedal arm being transmitted and rotating in a direction around an axis, and the rotating body A frictional resistance generating means for generating a frictional resistance force that gradually increases as the resistance force in the rotation of the rotary body. The rotary body is rotated by the rotation of the rotary body main body and is axially rotated. And a frictional resistance generating means is provided on the inclined surface formed on one surface of the movable body facing the non-moving body and on one surface of the non-moving body facing the movable body. Inclination formed and in surface contact with the inclined surface If, resiliently biased toward the movable member non moving object, and a spring means for pressing together the two inclined surfaces.
[0009]
According to the pedal device of the first aspect, when the rotating body is rotated by the rotation of the pedal arm by depressing the pedal, a frictional resistance force that increases in the frictional resistance force generating means is generated. It is possible to eliminate excessive fuel consumption by depressing the pedal too much, and the pedal depressing force that can maintain the pedal arm rotation position at the pedal depressing amount according to the pedal depressing amount is constant. As a result of the wide range, the pedal depression amount can be easily kept constant according to the speed when driving at a constant speed from low speed to high speed, and problems such as premature fatigue on the pedal foot can be eliminated. In addition, the resistance force that can be imparted to the rotation of the pedal arm can be determined by appropriately setting the friction coefficient on both inclined surfaces that are in surface contact with each other. It is possible to perform the reaction force adjustment with hysteresis characteristics in the relationship between the depression amount and the pedal depression force very simply. .
[0010]
According to a second aspect of the present invention, in the pedal device of the first aspect, in the pedal device of the first aspect, the non-moving body includes a protrusion that protrudes in the axial direction and is integrally formed with the damper body. Comprises a movable body main body and projections that are axially projecting toward the non-moving body and are integrally formed with the movable body main body, and each of the inclined surfaces is formed on each of the two projections. Has been.
[0011]
According to the pedal device of the second aspect, each of the inclined surfaces of the frictional resistance generating means is formed on the respective protrusions of the non-moving body and the movable body, and the inclined surfaces of both protrusions are in surface contact with each other. It can be extremely compact and can be installed using a small space effectively.
[0012]
In the pedal device for an automobile according to the third aspect of the present invention, in the pedal device according to the first or second aspect, the rotating body main body has a flange portion that contacts the damper main body so as to be slidably rotatable. The resistance force generating means further includes a sliding and rotating surface between the damper main body and the flange portion, and the spring means has a mutual sliding and rotatable surface between the damper main body and the flange portion. They are designed to be pressed against each other.
[0013]
According to the pedal device of the third aspect, since the frictional resistance generating means further includes a sliding and rotating surface in addition to the inclined surface, the frictional resistance force can be shared and generated. The resistance of the pedal according to the first aspect can be determined by appropriately setting the coefficient of friction between the inclined surface and the sliding rotatable surface, and the resistance force that can be imparted to the rotation of the pedal arm can be determined. As with the apparatus, reaction force adjustment with hysteresis characteristics can be performed very easily.
[0014]
In the pedal device according to the third aspect, each of the sliding and rotatable surfaces may be formed to be inclined.
[0015]
According to a fourth aspect of the present invention, in the pedal device of the first aspect, in the pedal device according to any one of the first to third aspects, the rotating body has a cylindrical portion and a spring receiving portion formed integrally with the cylindrical portion. The movable body is mounted on the cylindrical portion so as to be movable in the axial direction, and the spring means is disposed between the spring receiving portion and the movable body.
[0016]
According to the pedal device of the fourth aspect, the spring means is twisted by the rotation of the rotating body because the spring means is arranged between the spring receiving portion rotated with the rotation of the rotating body and the movable body. Therefore, it is possible to eliminate a malfunction caused by twisting of the spring means.
[0017]
In the pedal device for an automobile according to the fifth aspect of the present invention, in the pedal device according to any one of the first to fourth aspects, the rotation of the pedal arm is transmitted to the rotating body via the rotatable shaft. It has become.
[0018]
The rotation of the pedal arm may be transmitted directly to the rotating body via the rotatable shaft, but a gear mechanism or the like may be provided between the pedal arm and the rotating shaft or between the rotatable shaft and the rotating body. It may be interposed.
[0019]
The pedal arm in the device of the present invention is preferably an accelerator pedal arm as in the pedal device of the sixth aspect of the present invention, but instead of this, a brake pedal arm or a clutch pedal arm, etc. Also good.
[0020]
As a material for forming the damper main body, the non-moving body, and the rotating body, it is preferable that the base material is made of a resin and contains a filler. In addition, as a material for forming the damper main body, a metal that can be regarded as a substantially rigid body may be used in some cases.
[0021]
The damper according to the present invention is suitable for use in the apparatus according to any one of the above aspects, and is basically arranged so as to be stationary in the direction around the axis of the damper main body and the axis of the damper main body and in the axial direction. A non-moving body, a rotating body facing the non-moving body, to which rotation of the pedal arm is transmitted, and a frictional resistance generating means for generating a frictional resistance force that gradually increases with the rotation of the rotating body. The rotating body includes a rotating body main body and a movable body that is rotated by the rotation of the rotating body main body and movable in the axial direction, and the frictional resistance generating means faces the non-moving body. An inclined surface formed on one surface of the movable body, an inclined surface formed on one surface of the non-moving body facing the movable body and in surface contact with the inclined surface, and the movable body elastic toward the non-moving body And spring means for pressing both inclined surfaces against each other. It is Bei.
[0022]
With such a damper, a desired hysteresis characteristic can be obtained, and the preferable characteristic as described above can be obtained by connecting to a rotatable shaft such as an accelerator pedal arm of an automobile.
[0023]
Note that the damper according to the present invention is not limited to that used for a pedal arm of an automobile, and may be used for a mechanism or device that requires the above characteristics.
[0024]
DETAILED DESCRIPTION OF THE INVENTION
Next, the present invention and its embodiments will be described with reference to preferred examples shown in the drawings.
The present invention is not limited to these examples.
[0025]
1 to 8, a pedal device 1 for an automobile according to the present embodiment includes a support frame 2 and a pedal arm supported by the support frame 2 so as to be rotatable in an R direction, which is a direction around the axis A, around the axis A. In this example, the accelerator pedal arm 3 made of rigid metal, the spring means 4 that urges the accelerator pedal arm 3 to the initial rotation position, and the resistance force that gradually increases as the accelerator pedal arm 3 rotates in the R direction. And a stopper (not shown) for stopping the rotation of the accelerator pedal arm 3 at the initial rotation position.
[0026]
The support frame 2 is fixed to the vehicle body 11 with rivets or bolts 12 or the like at the bottom plate portion 13, and rotatably supports the rotatable shaft 14 at both side wall portions 15 and 16.
[0027]
The accelerator pedal arm 3 has an accelerator pedal (not shown) at the tip and is fixed to one end portion 17 of the rotatable shaft 14. The accelerator pedal arm 3 rotates around the support frame 2 in the R direction via the rotatable shaft 14. It is supported freely.
[0028]
In this example, the spring means 4 comprises a coil spring, particularly preferably a torsion coil spring 18. One end 19 engages with the side wall 15 of the support frame 2, and the other end 20 engages with the accelerator pedal arm 3. In FIG. 2, the accelerator pedal arm 3 is always elastically biased counterclockwise in the R direction. The spring means 4 may be a compression spring, particularly a compression coil spring, instead of the torsion coil spring 18.
[0029]
The damper 5 is disposed in a damper main body 22 fixed to the side wall portion 15 of the support frame 2 with bolts 21 and the like, and in the damper main body 22, immovably disposed in the axis A direction and the R direction with respect to the damper main body 22. On the one hand, the non-moving body 23 faces the non-moving body 23, and on the other hand, a rotating body 26 that is in contact with the fixed surface 25 of the damper main body 22 on the annular surface 24 so as to be slidably rotatable in the R direction. Friction resistance force generating means 27 for generating a friction resistance force that gradually increases as a resistance force in the rotation of the body 26 in the R direction is provided.
[0030]
The damper body 22 includes a cylindrical portion 31 having a cylindrical inner peripheral surface 30, a flange portion 32 formed integrally with one end surface of the cylindrical portion 31, and a radially inner portion on the inner peripheral surface 30 of the cylindrical portion 31. And an annular plate portion 33 integrally formed so as to protrude in the direction.
[0031]
The flange portion 32 has through holes 35 and 36 at both ends in the major axis direction, and the damper main body 22 is fixed to the side wall portion 15 in the flange portion 32 by bolts 21 and the like passing through the through holes 35 and 36. A cylindrical portion 39 of a rotating body main body 38 to be described later is rotatably inserted into the central through hole 37 of the annular plate portion 33.
[0032]
As shown in detail in FIG. 4, the non-moving body 23 is integrally protruded in the direction of the axis A on the outer peripheral side of one surface 43 of the annular plate portion 33 facing the annular surface 42 of the movable body main body 41 described later. The non-moving body 23 of this example formed of the protrusions 44 is fixed in the axis A direction and the R direction. The protrusions 44 are arranged at equiangular intervals in the R direction. A recess 46 is formed in the surface 43 so as to be connected to the protrusion 44 so as to define the step 45.
[0033]
The rotator 26 includes a rotator body 38 and a movable body 51 that is movable in the direction of the axis A with respect to the rotator body 38 and rotated together with the rotation of the rotator body 38 in the R direction.
[0034]
The rotator main body 38 is screwed to a cylindrical portion 39, a flange portion 55 formed integrally with one end of the cylindrical portion 39 in the radially outward direction, and a screw portion 56 on the outer peripheral surface of one end of the cylindrical portion 39. And a fixed bottomed cylindrical spring receiver 57.
[0035]
The movable body 51 has, on the outer peripheral surface of the cylindrical portion 39, a plurality of spline protrusions 62 that are fitted in the plurality of spline grooves 61 that extend in the axial direction and are arranged parallel to each other in the R direction. The outer peripheral surface of the cylindrical portion 39 is slidable in the direction of the axis A by spline coupling to the outer peripheral surface of the cylindrical portion 39 and rotated with the rotation of the cylindrical portion 39 in the R direction. As shown in particular detail in FIG. 7, an annular movable body main body 41 mounted on the surface of the movable body main body 41 protrudes toward the projection 44 that is the non-moving body 23 in the direction of the axis A. Three protrusions 63 integrally formed on the outer peripheral side are provided, and the protrusions 63 are arranged on one surface 42 of the movable body main body 41 at equal angular intervals in the R direction. A recess 65 is formed in the surface 42 so as to be connected to the protrusion 63 so as to define the stepped portion 64.
[0036]
The other end portion 70 of the rotatable shaft 14 is fixedly inserted into the cylindrical portion 39. The cylindrical portion 39, the flange portion 55 formed integrally with the cylindrical portion 39, and the cylindrical portion Each of the spring receiving body 57 fixed to 39, the movable body main body 41 splined to the cylindrical portion 39, and the protrusion 63 formed integrally with the movable body main body 41, together with the rotation of the rotatable shaft 14 in the R direction, Similarly, it is rotated in the R direction.
[0037]
The frictional resistance generating means 27 comes into surface contact with the inclined surface 71 having an inclination angle θ with respect to the direction orthogonal to the axis A direction formed on each of the protrusions 44 and in rotation in the R direction. Are formed on each of the protrusions 63, and similarly to the inclined surface 71, the inclined surface 72 having an inclination angle θ with respect to the direction orthogonal to the direction of the axis A, and the sliding of the flange portion 55 and the annular plate portion 33 with each other. The surface 24 and the fixed surface 25 that are freely movable surfaces, the mutual sliding surface in the direction of the axis A in the spline connection of the outer peripheral surface of the cylindrical portion 39 and the inner peripheral surface of the movable body main body 41, and the movable body main body 41 are fixed. And a compression coil spring 73 that elastically urges toward 23.
[0038]
The inclined surfaces 71 and 72 are complementarily formed so as to be in surface contact with each other, and the compression coil spring 73 presses the inclined surfaces 71 and 72 and the surfaces 24 and the fixing surface 25 against each other. The spring receiving body 57 is elastically shrunk and concentric with the cylindrical portion 39 in the spring receiving body 57 and between the movable body main body 41 and the bottom 75 of the spring receiving body 57 at one end and the other end of the spring receiving body 57 at the other end. The bottom portions 75 are arranged in contact with each other.
[0039]
The inclined surfaces 71 and 72 move the movable body main body 41 away from the non-moving body 23 in the direction of the axis A against the elastic force of the coil spring 73 when the projection 63 rotates in the R direction. The friction resistance force is increased by increasing the spring reaction force of the coil spring 73.
[0040]
The respective tips of the projections 63 in the direction of the axis A fall into the respective recesses 46, and the tips of the projections 44 in the direction of the respective axes A fall into the respective recesses 65. The initial surface contact position between the inclined surface 71 and the inclined surface 72 is defined by 45 and the step portion 64.
[0041]
In a vehicle equipped with the above pedal device 1, for example, an automobile, the accelerator pedal arm 3 is rotated in the clockwise direction in the R direction in FIG. 2 against the elastic force of the coil spring 18 when the accelerator pedal is depressed. Then, fuel injection to the engine is accelerated and accelerated by an electronic control unit (not shown) including a detector that detects the rotation angle of the accelerator pedal arm 3, and conversely, when the accelerator pedal is released, the accelerator pedal arm 3 is When the coil spring 18 is rotated counterclockwise in the R direction in FIG. 2 by the elastic force of the coil spring 18, fuel injection to the engine is reduced and decelerated by an electronic control device (not shown).
[0042]
In the pedal device 1, when the rotating body 26 is rotated in the R direction by the rotation of the accelerator pedal arm 3 by the depression of the accelerator pedal, the protrusion 63 is also rotated in the R direction, and the rotation of the protrusion 63 in the R direction The movable body 51 having the protrusion 63 in surface contact with the inclined surface 71 by the inclined surface 72 is moved toward the bottom 75 against the elastic force of the coil spring 73 in the axis A direction, as shown in FIG. On the contrary, when the pedal depression is released, the accelerator pedal arm 3 is returned to the original position by the elastic force of the coil spring 18, and similarly, the movable body 51 is returned to the original position as shown in FIG. Is done.
[0043]
In the pedal device 1, the friction resistance between the inclined surface 71 and the inclined surface 72 pressed against each other by the gradually increasing elastic force of the coil spring 73, the friction resistance between the surface 24 and the fixed surface 25, and the cylindrical portion 39 and the movable body Due to the frictional resistance in the spline connection with the main body 41, as shown by the line bc in FIG. 10, an appropriate gradually increasing resistance force (reaction force) is applied to the rotation of the accelerator pedal arm 3 based on the pedal depression, Thus, it is possible to eliminate the situation where the accelerator pedal is depressed too much and consumes more fuel than necessary. In addition, when the pedal depression at the angle αef ° is released, the accelerator pedal arm 3 is moved by the elastic force of the coil spring 18. The rotation is returned to the initial position early with a small resistance.
[0044]
In addition, in the pedal device 1, after the pedal is depressed, for example, when the pedal depression is maintained at an angle αef ° corresponding to steady running, as shown in FIG. 10, even if the pedal depression force is decreased from Te to Tf, The pedal arm rotation angle and the pedal depression force are based on the friction resistance between the inclined surface 71 and the inclined surface 72, the friction resistance between the surface 24 and the fixed surface 25, and the friction resistance in the spline coupling between the cylindrical portion 39 and the movable body main body 41. With the hysteresis characteristic ab-ef, the rotation angle αef ° of the accelerator pedal arm 3 can be maintained, so that inconveniences such as early fatigue of the pedal foot can be eliminated. That is, in the pedal device 1, the range Te−Tf of the pedal depression force T that can keep the turning angle αef ° of the accelerator pedal arm 3 at the pedal depression amount constant according to the pedal depression amount can be increased. When the vehicle is traveling at a constant speed at each speed, the pedal depression amount can be easily maintained constant according to the speed, and inconveniences such as premature fatigue of the pedal foot can be eliminated.
[0045]
Further, according to the pedal device 1, the accelerator pedal is roughly controlled by the frictional resistance between the inclined surface 71 and the inclined surface 72, the frictional resistance between the surface 24 and the fixed surface 25, and the frictional resistance in the spline connection between the cylindrical portion 39 and the movable body 41. Since the resistance force that can be applied to the rotation of the arm 3 can be determined, reaction force adjustment with hysteresis characteristics can be performed very easily, and in addition, by setting each value as appropriate, it is extremely compact. And can be installed using a small space effectively.
In addition, according to the pedal device 1, the frictional resistance generating means 27 further includes the surface 24 and the fixed surface 25 that are slidable and rotatable surfaces in addition to the inclined surfaces 71 and 72. The resistance force can be shared and generated, and the burden on the inclined surfaces 71 and 72 can be reduced.
[0046]
Further, according to the pedal device 1, the coil spring 73 is disposed between the movable body main body 41 that does not rotate relative to each other and the bottom 75 of the spring receiving body 57. It is not twisted, and therefore there is no inconvenience such as malfunction due to twisting of the coil spring 73.
[0047]
【The invention's effect】
According to the present invention, the range of the pedal depression force that can maintain the rotation position of the pedal arm at the pedal depression amount constant according to the pedal depression amount can be increased, and more compact than the dummy cable. In addition to being able to be installed, reaction force adjustment with hysteresis characteristics can be performed very easily, and a pedal device having a damper with little characteristic change and a damper suitable for use with this pedal device can be provided.
[Brief description of the drawings]
FIG. 1 is a front sectional view of an example of a preferred embodiment of the present invention.
FIG. 2 is a left side view of the example shown in FIG.
FIG. 3 is a right side view of the damper shown in FIG. 1;
4A is a left side view of the annular plate portion of the example shown in FIG. 1, and FIG. 4B is a diagram showing protrusions, recesses and step portions formed integrally on one surface of the annular plate portion. It is explanatory drawing developed and shown.
FIG. 5 is a left side view of the movable body of the example shown in FIG.
6 is a cross-sectional view taken along line VI-VI of the movable body shown in FIG. 5 with projections and the like formed on one surface of the movable body omitted.
7A is a right side view of the movable body of the example shown in FIG. 1, and FIG. 7B is a developed view of protrusions, recesses, and steps formed integrally on one surface of the movable body. It is explanatory drawing shown.
8 is a front view of a cylindrical portion and a collar portion of the rotating body main body of the example shown in FIG.
9 is an operation explanatory diagram of the damper of the example shown in FIG. 1. FIG.
10 is a relationship diagram between the pedal arm rotation angle and the pedal depression force in the example shown in FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Motor vehicle pedal apparatus 3 Accelerator pedal arm 5 Damper 22 Damper main body 23 Non-moving body 26 Rotating body 27 Friction resistance generating means

Claims

The damper includes a damper that imparts a gradually increasing resistance force to the rotation of the pedal arm. The rotating body that faces the non-moving body and receives the rotation of the pedal arm and rotates in the direction around the axis, and the frictional resistance force that gradually increases as the resistance force in the rotation of the rotating body. And a rotating body that includes a rotating body main body and a movable body that is rotated by the rotation of the rotating body and that is movable in the axial direction. The force generating means includes an inclined surface formed on one surface of the movable body facing the non-moving body, an inclined surface formed on one surface of the non-moving body facing the movable body and in surface contact with the inclined surface, Elastically bias the movable body toward the non-moving body The rotating body body includes a cylindrical portion and a spring receiving portion formed integrally with the cylindrical portion, and the movable body includes: It has a movable body attached to the cylindrical part so as to be movable in the axial direction and rotated with the rotation of the cylindrical part, and the spring means contacts the spring receiving part at one end and the movable body at the other end, respectively. An automobile pedal device comprising a compression coil spring disposed between the spring receiving portion and the movable body main body.

The non-moving body includes a protrusion that protrudes in the axial direction and is integrally formed with the damper body. The movable body protrudes toward the non-moving body in the axial direction and is integrally formed with the movable body. The automobile pedal device according to claim 1, wherein each of the inclined surfaces is formed on each of the protrusions.

The rotating body has a flange part that is slidably rotatable in contact with the damper main body, and the frictional resistance generating means further includes a mutually slidable rotatable surface between the damper body and the flange part. The pedal device for an automobile according to claim 1 or 2, wherein the spring means presses the mutually slidable and rotatable surfaces between the damper main body and the flange portion.

The pedal device for an automobile according to any one of claims 1 to 3, wherein the rotation of the pedal arm is transmitted to the rotating body via a rotatable shaft.

The pedal device for an automobile according to any one of claims 1 to 4, wherein the pedal arm is an accelerator pedal arm.

Damper main body, non-moving body arranged immovably around and around the axis of the damper main body, a rotating body facing the non-moving body and transmitting the rotation of the pedal arm, and the rotation A frictional resistance generating means for generating a frictional resistance that gradually increases during the rotation of the body. The rotating body is rotated by the rotation of the rotating body and is movable in the axial direction. The frictional resistance generating means is formed on an inclined surface formed on one surface of the movable body facing the non-moving body and on one surface of the non-moving body facing the movable body. An inclined surface that is in surface contact with the inclined surface; and a spring means that elastically biases the movable body toward the non-moving body and presses the inclined surfaces to each other. And a spring receiving portion formed integrally with the cylindrical portion. The movable body includes a movable body main body mounted on the cylindrical portion so as to be movable in the axial direction and rotated with the rotation of the cylindrical portion, and the spring means has one end at the spring receiving portion and the other end. And a damper comprising a compression coil spring that is in contact with the movable body main body and disposed between the spring receiving portion and the movable body main body.

The non-moving body includes a protrusion that protrudes in the axial direction and is integrally formed with the damper body. The movable body protrudes toward the non-moving body in the axial direction and is integrally formed with the movable body. The damper according to claim 6, wherein each of the inclined surfaces is formed on each of the protrusions.

The rotating body has a flange part that is slidably rotatable in contact with the damper main body, and the frictional resistance generating means further includes a mutually slidable rotatable surface between the damper body and the flange part. The damper according to claim 6 or 7, wherein the spring means presses the mutually slidable and rotatable surfaces between the damper main body and the flange portion.