JP4529059B2 - Rotating damper - Google Patents

Rotating damper Download PDF

Info

Publication number
JP4529059B2
JP4529059B2 JP2000317458A JP2000317458A JP4529059B2 JP 4529059 B2 JP4529059 B2 JP 4529059B2 JP 2000317458 A JP2000317458 A JP 2000317458A JP 2000317458 A JP2000317458 A JP 2000317458A JP 4529059 B2 JP4529059 B2 JP 4529059B2
Authority
JP
Japan
Prior art keywords
torque
drive shaft
rotary damper
cam member
chamber
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.)
Expired - Fee Related
Application number
JP2000317458A
Other languages
Japanese (ja)
Other versions
JP2001187934A (en
Inventor
謙次 高橋
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
TOK Bearing Co Ltd
Original Assignee
TOK Bearing Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by TOK Bearing Co Ltd filed Critical TOK Bearing Co Ltd
Priority to JP2000317458A priority Critical patent/JP4529059B2/en
Priority to DE10122077A priority patent/DE10122077A1/en
Priority to US09/852,886 priority patent/US6729448B2/en
Publication of JP2001187934A publication Critical patent/JP2001187934A/en
Application granted granted Critical
Publication of JP4529059B2 publication Critical patent/JP4529059B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Description

【０００１】
【発明の属する技術分野】
本発明は、回転部材を構成するスライド部材を基部に沿って径方向にスライド可能とし、該スライド部材の外面とハウジング内部の室の内周面との間の間隔を調節することによって、発生するトルクの大きさを調整可能とした回転ダンパ、ならびに、駆動軸の回転によって生じる一定以上の力によって揺動する揺動部材の外面と室の内周面との間隔を狭めることによりトルクを発生させる回転ダンパに関する。
【０００２】
【従来の技術】
従来、開放されている吊り戸等が閉じる際に、急激な閉戸動作によってドア枠に戸が衝突することにより、衝突音が発生したり戸やドア枠が破損する等の問題があった。このような急激な閉戸動作を防止するために、閉戸動作を制動するための種々のダンパが提案されている。
【０００３】
例えば図１４に示すように、特開平８−９３３１２号公報には、制動シャフト３３に固着した回転ドラム３４と、筐体３１の蓋体部３１Ｂに固着された基体部３１Ａに螺着する調整ネジ３５と、この調整ネジ３５に螺合すると共に蓋体部３１Ｂの溝３１Ｃに沿って移動可能な可動ドラム３６と、制動シャフト３３に一方向のみの回転動作を伝達する一方向クラッチ３７とからなるドアクローザ用流体摩擦抵抗型ダンパ装置が開示されている。
【０００４】
さらに図１５に示すように、このようなダンパ装置を引き戸に取付け、戸枠側のガイドレール部材１１に固設したラック１２に、制動シャフト３３に取付けたピニオン１３を噛合する構成としている。閉戸動作が行なわれる場合にはクラッチ３７によってピニオン１３の回転動作が制動シャフト３３に伝達されて閉戸動作が制動され、一方、開戸動作が行なわれる場合にはクラッチ３７によってピニオン１３の回転動作が制動シャフト３３に伝達されるのが阻止されるようになっている。
【０００５】
しかしながら、このようなダンパ装置では、可動ドラム３６を筐体３１内で軸方向に沿って移動させることによって、可動ドラム３６の外周面と回転ドラム３４の内周面との接触・摺動面積を変化させて、発生トルクの大きさを調整するようになっている。したがって、発生トルクを小さく調整する場合は、前記両面の接触・摺動面積を小さくする必要がある。このような場合には、可動ドラム３６と回転ドラム３４の径方向の面が大きく離間する必要があり、その結果、ダンパ本体の軸方向長さを短くできない不都合があった。
【０００６】
さらに、手で戸を急激に閉じるような場合には一時的に極めて高い負荷が戸に作用するが、ダンパ装置によって発生するトルクの大きさは一定なので、前記高負荷を吸収しきれず十分なダンパ効果が得られない。その結果、閉戸動作が制動されず、戸枠等に戸が衝突することによる衝突音の発生や戸の破損を回避できない問題もあった。
【０００７】
【発明が解決しようとする課題】
そこで、軸方向長さの短いコンパクトなダンパや、急激に戸が閉まるような場合において一時的に作用する極めて高い負荷を吸収可能なダンパが望まれていた。
【０００８】
【課題を解決するための手段】
上記課題を解決するための第１の発明に係る回転ダンパは、請求項１において、内部に室を備えたハウジングと、該室内に基端側が収容された駆動軸と、該駆動軸に軸支されて前記室内に収容された回転部材と、前記室内に充填された粘性流体とを備え、前記回転部材の回転によりトルクを発生する回転ダンパにおいて、
前記回転部材が、前記駆動軸と一体回転自在に軸支された基部と、前記駆動軸に対して固定関係を持ちつつ一定以上の外部力の作用により相対移動可能なトルク調整体と、径方向に移動可能に配置され、かつ前記室の内周面の一部と相補的な外面を有するスライド部材と、該スライド部材を前記トルク調整体に対して付勢するバネ手段とを備え、
前記駆動軸に対して前記トルク調整体を相対移動させることにより、前記スライド部材を前記基部に沿って径方向にスライドさせて該スライド部材の外面と前記室の内周面との間の径方向の間隔を変化させることによって前記回転部材の回転トルクを変化させるようにしたことを特徴とする。
【０００９】
スライド部材を基部に沿って径方向にスライドさせることによってその外面と室の内周面との間に形成される径方向における間隔を制御することにより、この隙間に存在する粘性流体の剪断抵抗に基づいて発生するトルクを変化させることができるので、ダンパ本体の軸方向長さに関する制約を受けることがない。
【００１０】
請求項２では、前記トルク調整体が、前記回転部材の基部に一体回転自在に取付けられた調整リングと、該調整リングの外周に取付けられたカム部材とからなり、前記調整リングの外周と前記カム部材の中央孔の内周とは一方に形成された凹部と他方に形成された凸部とにより係合し、一定以上の外部力が前記カム部材に作用すると、前記カム部材が前記調整リング及び前記駆動軸に対して所定角度相対回動することを許容するように、前記凹部と凸部とを構成した。これにより、駆動軸に対してトルク調整体を所定角度をもって確実に配置することができる。
【００１１】
請求項３では、前記トルク調整体のカム部材の外周を楕円形としたことにより、スライド部材とカム部材との各接触部のカム部材中心からの距離を連続的に変位することができる。
【００１２】
請求項４では、カム部材がハウジング外に突出した軸方向突起部を有するようにし、トルク調整体を駆動軸に対して所定角度相対回動させるための作動部をカム部材の前記突起部に設けるようにした。これにより、トルク調整体を該所定角度の位置まで容易に回動することができる。
【００１３】
請求項５では、前記トルク調整体が、前記回転部材の基部に一体回転自在かつ軸方向移動自在に取付けられたカム部材と、該カム部材と係合する調整部材とからなり、前記カム部材は、外周に傾斜面からなるカム面と、軸方向一側に前記回転部材に連結された連結部と、軸方向他端に形成された壁部とを有し、前記調整部材は、軸方向内端部に前記カム部材の壁部と係合する作動面を有し、前記カム面と作動面とは、一定以上の外部力が前記調整部材に作用すると、前記作動面の前記カム部材の前記壁部と係合する部位の位置が軸方向に移動し、もって前記カム部材が前記駆動軸に沿って移動することを許容するように構成した。これにより、駆動軸に沿ってカム部材を所定距離をもって確実に配置することができる。
【００１４】
請求項６では、調整部材がハウジング外に突出した外端部を有するようにし、カム部材を駆動軸に沿って移動させるための作動部を前記外端部に設けるようにした。これにより、カム部材を駆動軸に沿った所定位置まで容易に移動することができる。
【００１５】
請求項７では、前記バネ手段の付勢力を、回転ダンパの回転によって前記スライド部材に作用する所定の遠心力であって、例えば、吊り戸等に一時的に高負荷が作用して駆動軸の回転数が急激に増加した際に発生する遠心力より小さくなるようにした。
このようにして発生する遠心力がバネ手段の付勢力を上回るようにしたので、スライド部材はバネ手段の付勢力に抗してトルク調整体に付勢された状態から互いに離間し合う。その結果、スライド部材の外面と室の内周面との間に形成される径方向における間隔を一時的にさらに狭くすることができるので、このような一時的な高負荷に対してもこれを吸収して吊り戸等に十分な制動力を作用させることが可能となる。
さらに、駆動軸の回転数が元に戻ると、スライド部材はバネ手段によりトルク調整体に再び付勢され、元の設定されたトルクを発生できる状態に復帰する。
【００１６】
請求項８では、スライド部材を、室の径方向においてトルク調整体を介した両側にそれぞれ配置された一対の部材からなるようにした。室の内周面に対面するスライド部材の外面の総面積を大きくとれるので、発生トルクを大きくすることが可能となる。
また、請求項９では、スライド部材を、室の径方向においてトルク調整体の一側に配置された単一部材からなるようにした。室の内周面に対面するスライド部材の外面の総面積を小さくしたので、発生トルクを小さくすることができる。
【００１７】
第２の発明に係る回転ダンパは、請求項１０において、内部に室を備えたハウジングと、該室内に基端側が収容された駆動軸と、該駆動軸に軸支されて前記室内に収容された回転部材と、前記室内に充填された粘性流体とを備え、前記回転部材の回転によりトルクを発生する回転ダンパにおいて、
前記回転部材が、前記駆動軸に一体回転自在に軸支された基部と、該基部に揺動可能に取付けられ、かつ前記室の内周面の一部と相補的な外面を有する揺動部材と、該揺動部材と前記基部間に介設され、一定以上の力が揺動部材に作用したときに揺動部材の揺動を許容するバネ手段とを備え、
前記駆動軸の回転により生じる前記一定以上の力によって前記揺動部材を前記基部に対して揺動させて該揺動部材の外面と前記室の内周面との隙間を狭めることによってトルクを発生させるようにしたことを特徴とする。
【００１８】
駆動軸の回転による粘性流体の剪断抵抗力がバネ手段の抗力以上になると、揺動部材が揺動して回転トルクが発生する。駆動軸の回転速度が一時的に速くなった場合に直ちに高トルクが得られ、その後、回転速度の減少にしたがってトルクを減衰できる。
【００１９】
請求項１１では、前記基部を前記駆動軸による軸支部分から径方向の両側に延出させ、前記揺動部材を、該基部の両端にそれぞれ取付けられた一対の部材からなるようにした。揺動部材が揺動する際に室の内周面に近接する該部材の外面の総面積を大きくとれるので、発生トルクを大きくすることが可能となる。
また、請求項１２では、前記基部を前記駆動軸による軸支部分から径方向の一側に延出させ、前記揺動部材を、該基部の外側端に取付けられた単一部材からなるようにした。揺動部材が揺動する際に室の内周面に近接する該部材の外面の総面積を小さくできるので、発生トルクを小さくすることが可能である。
【００２０】
【発明の実施の形態】
本発明の第１発明に係る回転ダンパの第１構成例について添付した図面に基づき説明する。図１は本回転ダンパの分解斜視図、図２は右側面図、図３は図２において蓋を取外した内部説明図、図４は図３のＡ−Ａ断面図である。
【００２１】
図１、図３及び図４に示すように、本発明の回転ダンパ１は、ハウジング２の内部の室３内に駆動軸４の基端側４ａを収容し、この基端側４ａに回転部材５を軸支し、さらに、室３内に粘性流体１０を充填した構造を有し、ハウジング２に対して回転部材５を相対的に回転可能としたものである。
【００２２】
ここで、回転部材５は、駆動軸４の基端側４ａを軸孔６ａに挿入して軸支された略小判形の基部６と、この基部６の一方の面に設けられた円形突出部６ｂに取付けられたトルク調整体７と、このトルク調整体７に接触しつつこれを介して対向する位置に配置された一対のスライド部材８、８と、これら一対のスライド部材８、８をトルク調整体７に付勢する一対の引張バネ手段９、９とから構成される。なお、トルク調整体７は、円形突出部６ｂに取付けられる内側の調整リング７１と、この調整リング７１の外周に取付けられてこれと係合する外側の楕円状カム部材７２と、調整ツマミ７３とから構成される。
【００２３】
基部６の一方の面には円形突出部６ｂが設けられ、この突出部６ｂの外面に形成された二つの係合凸部（不図示）に、調整リング７１の内面に形成された二つの係合凹部７１ａ、７１ａをそれぞれ係合することによって、調整リング７１が基部６に回転不能に取付けられる。
【００２４】
調整リング７１とカム部材７２とは、調整リングの外周とカム部材中央孔の内周の一方に形成した凹部と他方に形成した凸部とにより係合するように構成される。
例えば、図１に示すように、調整リング７１の外面に軸方向に沿った二つの凸部７１ｂ、７１ｂを設け、カム部材７２の内面に軸方向に沿った複数の突起７２ａを形成した構造が採用される。調整リング７１を介してカム部材７２を駆動軸４に対して回転させると、カム部材７２の突起７２ａが調整リング７１の凸部７１ｂを次々に乗り越え、回転の停止により突起７２ａ、７２ａ間の凹部７２ｂに凸部７１ｂが噛合った状態となる。
このような構造に代わって、調整リング７１の外面に軸方向に沿った凹部を設け、カム部材７２の内面に軸方向に沿った複数の凸部を形成した構造とし、駆動軸の回転の停止により、調整リング７１の外面の凹部にカム部材７２内面の凸部が噛合うようにしてもよい。
【００２５】
図１及び図４に示すように、カム部材７２の軸７２ｃの端部には作動部としての調整ツマミ７３が嵌合されている。調整ツマミ７３は、リング状の本体と、該本体の径方向に沿ったネジ孔７３ｂと、これに螺合するネジ７３ａとからなり、ネジ孔７３ｂにネジ７３ａを螺合させつつネジ７３ａの端面をカム部材７２の軸７２ｃの外面に圧接させることにより、調整ツマミ７３をカム部材７２に固定するものである。調整ツマミ７３を回すことによって、カム部材７２を基部６に対して容易に回転させることができる。
【００２６】
作動部としての調整ツマミ７３をカム部材の軸７２ｃの端部に固定する方法としては、上述のもの他に例えば図３３及び図３４示すような方法を採用してもよい。
図３３に示す例では、調整ツマミ７３のリング状本体の径方向に沿って、孔７３ｃ、７３ｃが設けられる。２つの孔７３ｃはリング状本体の中心に対して対向する位置に配置され、これら２つの孔の中心軸は一直線上にある。一方、カム部材の軸７２ｃの端部にも孔７２ｆが設けられる。２つの孔７３ｃと孔７２ｆの中心軸が一直線上に揃うように、カム部材の軸７２ｃの端部に調整ツマミ７３のリング状本体が嵌合される。２つの孔７３ｃ及び孔７２ｆ内に波形スプリング等の圧入ピン７３ｄを挿入することにより、調整ツマミ７３をカム部材の軸７２ｃの端部に固定する。なお、圧入ピンとして、波形スプリングの他にマツバピンやダルマピン等を用いてもよい。
【００２７】
図３４に示す例では、カム部材の軸７２ｃの端部に軸方向に沿ったカット面７２ｅ、７２ｅが設けられると共に、カットされていない部分の周面に周方向に沿った溝７２ｆ、７２ｆが設けられる。一方、調整ツマミ７３のリング状本体には、軸７２ｃの端部と相補的形状をなす孔７３ｅが設けられる。溝７２ｆ、７２ｆが孔７３ｅから外部に突出するように軸７２ｃの端部を孔７３ｅに嵌入し、溝７２ｆ、７２ｆに止め輪７３ｆを装着する。
調整ツマミ７３はカム部材の軸７２ｃに対して、回り止め状態にあると共に抜け止め状態にあり、これによって、調整ツマミ７３がカム部材の軸７２ｃの端部に固定される。
【００２８】
各スライド部材８は、円形突出部６ｂが設けられている側の基部６面上に沿って径方向にスライドする滑動部８ａと、滑動部８ａの径方向の外端に取付けられた外壁８ｂとから構成され、外壁８ｂは室３の内周面３ａと相補的な形状をなす外面８ｃを有する。各スライド部材８の滑動部８ａ、８ａには、基部６の長手方向の両端部に形成された孔６ｃ、６ｃにそれぞれ対応する長孔８ｄ、８ｄが設けられている。孔６ｃと長孔８ｄとに押えピン１１を通すことにより、各スライド部材８は長孔８ｄのクリアランスの範囲内において室３内を径方向に移動可能である。
【００２９】
各スライド部材８の滑動部８ａの径方向における内端部には、一対の孔８ｅ、８ｅがその両端付近に設けられている。一方の滑動部８ａの孔８ｅ、８ｅと、これらに対向する他方の滑動部８ａの孔８ｅ、８ｅとが、引張バネ手段９、９によってそれぞれ連結されている。引張バネ手段９の張力によって、一対のスライド部材８、８がトルク調整体７のカム部材７２に接するように付勢されている。
【００３０】
次ぎに、このように構成された回転ダンパ１の作用等について説明する。
このような回転ダンパ１は、例えば、ハウジング２を吊り戸に固定し、上記駆動軸４の他端側４ｂをピニオン等を介して吊り戸のガイドレールと平行なラックに係合することによって使用される。
【００３１】
吊り戸が閉じる際に、吊り戸の回転動作が回転ダンパ１の駆動軸４に伝達され、駆動軸４の回転と共に回転部材５が回転する。ここで、一対のスライド部材８、８の外面８ｃ、８ｃと室３の内周面３ａとの間には所定の間隔を有する隙間が形成されているので、スライド部材８の回転により前記隙間に存在する粘性流体１０に剪断力が作用して回転トルクが発生し、これによって回転によるトルクを制動力として発生させるものである。
【００３２】
駆動軸を回転しないように固定しておき、調整ツマミ７３を廻すことにより駆動軸４に対してカム部材７２を所定角度まで回転することによって所望の回転トルクが得られる。
【００３３】
すなわち、カム部材７２の内面の突起７２ａが調整リング７１の外面の凸部７１ｂを次々に乗り越えるようにして回転すると、カム部材７２の外面は両スライド部材８、８に接しつつスライド部材８、８同士を径方向に離間又は近接させる。そこで、スライド部材８の外面８ｃと室３の内周面３ａとの間に形成される隙間が所望の間隔を与えるところでカム部材７２の回転を停止する。このように、駆動軸４に対してカム部材７２を所定の角度まで相対回動させることによって、回転部材が回転する際に発生するトルクを所望の大きさに設定できる。
【００３４】
本回転ダンパ１では、カム部材７２の内面の突起７２ａ間の凹部７２ｂに、調整リング７１の外面の凸部７１ｂが噛合った状態でカム部材７２が停止しているので、駆動軸４に対してトルク調整体７のカム部材７２を所定角度に確実に配置することができる。
【００３５】
ところで、カム部材７２は楕円形状をなすので、カム部材７２の回転に伴って、スライド部材８とカム部材７２との各接触部１２、１２のカム部材７２中心からの距離（以下「中心距離」と記す）を連続的に変化させることができる。したがって、回転により発生するトルク値を連続値として設定できるので、制動力の微調整が可能となる。
なお、カム７２は、その回転に伴って中心距離が変化するものであれば楕円形状に限定されるものではなく、カム７２の回転に伴って、中心距離の所望の変化が得られるような形状としてもよい。
【００３６】
発生トルクを増大させるには、カム部材７２の回転により中心距離を当初のものより増加させ、スライド部材８の外面８ｃと室３の内周面３ａとの間に形成される隙間の間隔をより狭くする。逆に、中心距離を当初のものより減少させると、スライド部材８の外面８ｃと室３の内周面３ａとの間に形成される隙間の間隔がより広くなり、その結果、回転によって発生するトルクが減少する。
【００３７】
また、回転ダンパ１を取付けた戸等に一時的に高負荷が作用するような場合には、駆動軸４の回転数が急激に増加して戸等の急激な閉戸動作が生起する。このとき、各スライド部材８には駆動軸４の回転数に応じた大きな遠心力が一時的に作用する。
本発明に係る回転ダンパ１では、引張りバネ９の引張り力をこのような急激な閉戸動作に基づく遠心力より小さく設定してあるので、たとえ斯かる急激な閉戸動作が生起したとしても、引張りバネ９の引張り力に抗してそれを上回る遠心力によって各スライド部材８をトルク調整体７から離間させつつ基部６に沿って室３の径方向外方に一時的に移動させる。その結果、各スライド部材８の各外面８ｃと室３の内周面３ａとの間に形成される径方向における間隔を一時的にさらに狭くして極めて高いトルクを発生させることが可能となる。
このように、一時的な高負荷が作用して急激な閉戸動作が生起しても、その後直ちにこのような急激な動作を吸収する十分な制動力を作用させることができる。
【００３８】
そして、このような制動力の作用によって駆動軸４が通常の回転数に戻ると、各スライド部材８はトルク調整体７に接するように引張りバネ９により再び付勢され、通常の設定トルクを発生する状態に復帰する。
【００３９】
図４に示すように、駆動軸４の他端側４ｂは内側からスライダー３３、ハウジング２、Ｏ−リング１５、プレート１７をこの順に嵌装し、最後にベアリング１８を軸支してハウジング外に突出させ、例えばピニオン等に連結される(不図示)。ハウジング２の他方の側（図中右側）は、トルク調整体７のカム部材７２との間に粘性流体１０の漏洩防止用のＯ−リング１４及びブッシュ３２を介装しつつ蓋１３によって閉じられる。カム部材７２と駆動軸４との間のＯ−リング３４、ハウジング２と駆動軸４との間のＯ−リング１５、ならびに、ハウジング２と蓋１３との間のＯ−リング１６もまた、室３からの粘性流体１０の漏洩を防止するためのものである。
【００４０】
次ぎに、第１発明の他の構成例にかかる回転ダンパを以下に示す。これらの構成例では、上記第１構成例と異なる部分についてのみ説明する。
まず、図５〜図８に基づいて第２構成例にかかる回転ダンパに関し説明する。なお、図５〜図８は第１構成例を示す図１〜４にそれぞれ対応し、図８は図７のＢ−Ｂ断面図である。この構成例では、カム部材７２の軸部７２ｃの端面には作動部としての調節溝７２ｄが設けられており、例えば、マイナスドライバーの先端をこの調節溝７２ｄに差し込んで廻すことによって、カム部材７２を基部６に対して容易に回転させることができる。
図８に示すように、駆動軸４の他端側４ｂは第１構成例と同様に、内側からスライダー３３、Ｏ−リング１５、ハウジング２、プレート１７、ベアリング１８がこの順に嵌装されている。ハウジング２の他方の側（図中右側）は、トルク調整体７のカム部材７２との間に粘性流体１０の漏洩防止用のＯ−リング１４及びスライダー３２を介装しつつ蓋１３によって閉じられる。ハウジング２と駆動軸４との間のＯ−リング１５、ならびに、ハウジング２と蓋１３との間のＯ−リング１６もまた、室３からの粘性流体１０の漏洩を防止するためのものである。
【００４１】
次ぎに、図９に基づいて第３構成例にかかる回転ダンパに関し説明する。この構成例では、基部６に対してトルク調整体７のカム部材７２を所定位置に配置する手段として、凹部７２ｂと凸部７１ｂとの噛合いに代わってＯ−リングの摩擦力を利用する。
【００４２】
この構成例では、駆動軸４を中空軸とし、この中空部分にカム部材７２と一体の調整軸７２ｄを貫通させて、カム部材７２の内面と基部６の円形突出部６ａの外面との間にＯ−リング３９を介装する。この場合には、調整軸７２ｄの外端部をDカット７２ｅとし、駆動軸４を回転しないように固定しておいて、Dカット７２ｅ部分をペンチ等によって回動することにより駆動軸４に対してカム部材７２を所定角度まで回動する。
Ｏ−リング３９はある程度押し潰されているので、カム部材７２の停止状態をほぼ確実に維持することが可能であり、カム部材７２を基部６に対して極めて簡易に係合できる利点を有する。
【００４３】
次ぎに、第４及び第５の構成例に係る回転ダンパは、スライド部材を、室の径方向においてカム部材の一側に配置された単一部材からなるように構成したものである。
まず、図１６に基づいて第４構成例にかかる回転ダンパに関し説明する。この構成例は、第１構成例において、一対のスライド部材の一方を基部に固定し他方のスライド部材のみを径方向に移動可能としたものであり、この他は第１構成例と同じである。
図１６に示すように、図中下方に位置するスライド部材８２は基部６に一体化され、その外面８２ｃが室３の内周面３ａに当接しない程度に近接して配置されている。一方、図中上方に位置するスライド部材８１の滑動部８１ａの孔８１ｅ、８１ｅは、引張りバネ９、９を介してスライド部材８２に設けられた孔８２ｅ、８２ｅにそれぞれ連結され、スライド部材８１がカム部材７２に付勢される。カム部材７２の回転中において、カム部材７２の外周面が固定スライド部材８２の内面８２ｇに接触しないように、固定スライド部材８２がカム部材７２から離間して配置される。
【００４４】
次ぎに、図１７に基づいて第５構成例にかかる回転ダンパに関し説明する。この構成例は、第１構成例において、一対のスライド部材の一方を固定部材に代え他方のスライド部材のみを径方向に移動可能としたものであり、その他は第１構成例と同じである。
図１７に示すように、固定部材８２は基部６に一体化され、その外面８２ｃと室３の内周面３ａの間に隙間が存在するように配置される。一方、図中上方に位置するスライド部材８１の滑動部８１ａの孔８１ｅ、８１ｅは、引張りバネ９、９を介して固定部材８２に設けられた孔８２ｅ、孔８２ｅにそれぞれ連結され、スライド部材８１がカム部材７２に付勢される。カム部材７２の回転中において、カム部材７２の外周面が固定部材８２の内面８２ｇに接触しないように、固定部材８２がカム部材７２から離間して配置される。
【００４５】
なお、上記中心距離を変化させる方法としては上述の第１〜５構成例ようなトルク調整体を用いるものに限定されるものではない。例えば、以下に説明するようなカム部材とこれに係合する調整部材からなるトルク調整体を用いる方法を採用してもよく、このような方法を採用した第６構成例に係る回転ダンパについて、図２６〜３２に基づいて説明する。ここで、図２６はカム部材の斜視図、図２７は調整部材の斜視図、図２８及び図２９は回転ダンパの軸方向に沿った断面図を示す。
【００４６】
図２６に示すように、カム部材７４は、一方側に壁部を有する円形基体７４ａと、該円形基体７４ａの他方側にあって外周を円錐面７４ｆとする中空状の円錐台７４ｂとからなる。上記壁部面７４ｇには半球突起７４ｃが設けられている。円錐台７４ｂの開口７４ｄには係合溝７４ｅが形成されている。
図２７に示すように、調整部材７５は、一方の面７５ｂが軸方向に対して傾斜面を形成する楕円形で他方の面７５ｃが円形となるように軸方向の厚さδを連続的に変化させた円形基体７５ａと、円形面７５ｃから軸方向に延出するバー７５ｄとを備える。調整部材７５の傾斜面７５ｂは、カム部材７４の半球突起７４ｃが当接して外部力が作用する作動面を構成する。
【００４７】
図２８及び図２９に示すように、円錐台７４ｂの開口７４ｄは基部６との連結部であって、開口７４ｄ内に基部６の円形突出部６ｂを挿入して、カム部材７４が基部６に取付けられる。なお、円錐台７４ｂの開口７４ｄに設けられた係合溝７４ｅに基部６の係合突起（不図示）を係合することにより、カム部材７４が基部６に対して回転不能に連結される。
調整部材７５はバー７５ｄにＯ−リング１４を介装してハウジング２に取付けられ、バー７５ｄの他端部には作動部としての調整ツマミ７６が嵌合されている。調整ツマミ７６は、リング状の本体と、該本体の径方向に沿ったネジ孔７８と、これに螺合するネジ７７とからなり、ネジ孔７８にネジ７７を螺合させつつネジ７７の端面を調整部材７５のバー７５ｄの外面に圧接させることにより、調整ツマミ７６を調整部材７５に固定するものである。
【００４８】
引張バネ手段９、９によって、スライド部材８の滑動部８ａの端面８ａ１がカム部材７４のカム面である円錐面７４ｆに付勢されている。この付勢力の駆動軸４の軸方向への分力によって、カム部材７４の半球突起７４ｃが調整部材７５の作動面７５ｂに当接するように、カム部材７４が調整部材７５に付勢される。
【００４９】
スライド部材８の外面８ｃと室３の内周面３ａとの間の径方向の距離である上記中心距離を狭めるには、上記付勢力の分力に抗して調整ツマミ７６を回すことによってバー７５ｄを中心として調整部材７５の作動面７５ｂを回転させ、カム部材７４の半球突起７４ｃと接する作動面７５ｂの部位の位置を変化させる。この際、半球突起７４ｃと接する位置における円形基体７５の軸方向厚さδが増加するようにカム部材を図中左側に移動させつつ、スライド部材８の外面８ｃを室３の内周面３ａに近づけて所望の中心距離を与えるところで調整ツマミ７６の回転を止める。
一方、上記中心距離を広くするには、上記付勢力の分力が作用する方向に調整ツマミ７６を回すことによってバー７５ｄを中心として調整部材７５の作動面７５ｂを回転させ、カム部材７４の半球突起７４ｃと接する作動面７５ｂの位置を変化させる。この際、半球突起７４ｃと接する位置における円形基体７５の軸方向厚さδが減少するようにカム部材を図中右側に移動させつつ、スライド部材８の外面８ｃを室３の内周面３ａから遠ざけて所望の中心距離を与えるところで調整ツマミ７６の回転を止める。
【００５０】
以上のように、回転部材の回転による所望のトルクを与えるための中心距離を得るために、カム部材７４の半球突起７４ｃと接する調整部材７５の作動面７５ｂの位置を連続的に変化させることによって駆動軸４に沿ってカム部材７４を所定距離だけ確実に移動させることができる。
【００５１】
なお、図３０に示すように、カム部材７４と調整部材７５の係合方法としては上記例とは逆に、カム部材７４の壁部面７４ｇを軸方向に対して傾斜する面とし、調整部材７５の作動面７５ｂに半球突起７５ｅを設けるようにしてもよい。引張バネ手段９、９による付勢力の駆動軸４の軸方向への分力によって、カム部材７４の壁部面７４ｇが調整部材７５の作動面７５ｂに設けた半球突起７５ｅに当接するように、カム部材７４が調整部材７５に付勢されるものである。
【００５２】
さらに、図３１に示すように、カム部材７４の壁部面７４ｇを軸方向に対して垂直とし、調整部材７５のバー７５ｄの端面７５ｂを作動面としてもよい。引張バネ手段９、９による付勢力の駆動軸４の軸方向への分力によって、カム部材７４の壁部面７４ｇが調整部材７５のバー７５ｄの端面７５ｂに当接するように、カム部材７４が調整部材７５に付勢されるものである。この例では、ケーシング２内に設けたネジ孔７９とバー７５ｄの外周面に設けたネジ部７５ｆとを螺合し、調整ツマミ７６の回動によってバー７５ｄをネジ孔７９に沿って出し入れすることにより、駆動軸４に沿ってカム部材７４を移動するものである。
【００５３】
また、カム部材７４の基体７４ａは、その一方側においてスライド部材８の滑動部８ａの端面８ａ１から駆動軸４の軸方向への分力が得られるような付勢力が作用するような構造であればよい。したがって、一方側の外面全体が円錐面７４ｆから構成される構造に限定されるものではない。例えば図３２に示すように、カム部材７４全体を方形状とし、スライド部材８の滑動部８ａの端面８ａ１と接するカム面のみを傾斜面７４ｆとしてもよい。
【００５４】
以上説明した本発明の第１発明に係る回転ダンパ１は、回転部材がいずれの方向に回転しても制動トルクを発生させる両方向性ダンパであるため、このような回転ダンパを吊り戸に適用する際には、以下に詳述するように、戸を開くときに制動トルクを発生させないために、ハウジングから外部に突出する駆動軸に一方向クラッチ等を介してピニオンを取り付ける必要がある。
【００５５】
次ぎに、第２発明に係る回転ダンパを以下に示すが、上記第１発明に係る回転ダンパと異なる部分についてのみ説明する。
まず、図１８〜図２２に基づいて第７構成例にかかる回転ダンパに関し説明する。図１８は本回転ダンパの分解斜視図、図１９は内部説明図、図２０は図１９のＣ−Ｃ断面図である。図２１及び２２は、駆動軸の回転によって揺動部材が揺動する状態を示す説明図である。なお、図１８〜２２に示す回転ダンパの各部材において、第１発明に係る回転ダンパと同じ部材には同じ符号を付した。
【００５６】
回転部材５は、駆動軸４の基端側４ａを軸孔６ａに挿入して軸支した略小判形の基部６と、基部６に揺動可能に取付けられた揺動部材４０と、揺動部材４０と基部６間に介設されたバネ手段４１とから構成される。
【００５７】
揺動部材４０は、半月板４０ａと、半月板４０ａの円周部と底辺の両端部に設けられた壁部材４０ｂ、４０ｂからなる。各壁部材４０ｂの底辺の両端部には側溝４０ｄ、４０ｄが形成され、半月板４０ａの略中心部には孔４０ｃが形成されている。円周部における壁部材４０ｂの外面４０ｂ２は、室３の内周面３ａの一部と相補的な形状を有する。
基部６の小判形状の各円形部分の全体にわたって、面６ｅに平行な溝６ｆ、６ｆが形成され、各円形部分の略中心部には、孔６ｄ、６ｄがそれぞれ形成されている。
【００５８】
上記バネ手段としての線バネ４１の両端が、各壁部材４０ｂの底辺部分に形成された側溝４０ｄ、４０ｄ内にそれぞれ挿入される。なお、バネ手段としては線バネの他に板バネを用いてもよい。このように線バネ４１が装着された各揺動部材４０は、その半月板４０ａ部分が基部６の溝６ｆ内に挿入されて孔４０ｃと孔６ｄにピン４２を通すことにより基部６に取付けられる。線バネ４１の中央部分は、基部６に設けられた凸状の支持部材４３の上面によって、室３の径方向外方に向けて押圧されている。このようにしてに取付けられた各揺動部材４０は、各壁部材４０ｂの底辺部分に一定以上の力を受けることによってピン４２を中心として振り子のように揺動する。
【００５９】
このような回転ダンパ１は、第１発明に係る回転ダンパと同様に、ハウジング２を吊り戸に固定し、駆動軸４の他端側４ｂをピニオン等を介して吊り戸のガイドレールと平行なラックに係合することによって使用される。
【００６０】
吊り戸が閉じる際には、吊り戸の回転動作が駆動軸４に伝達されて駆動軸４が回転する。図２１に示すように、駆動軸４が図中時計回りに回転すると、駆動軸４に軸支された基部６も駆動軸４と一体回転する。このとき、揺動部材４０の図中右側の壁部材４０ｂの底辺部分４０ｂ１、ならびに、半月板４０ａの底辺部分のうち図に示す中心から右側部分４０ａ１が、粘性流体１０による剪断抵抗力を受ける。このような剪断抵抗力が線バネ４１の抗力以上になると、支持部材４３上面の両端４３ａ、４３ｂを支点として支持されていた状態から支持部材４３上面の一方端４３ａで支持される状態へと、線バネ４１の支点が移行し、その結果、揺動部材４０がピン４２を中心として図中反時計回りに揺動する。
【００６１】
このような剪断抵抗力は駆動軸４の回転速度と共に大きくなるが、予め設定されている線バネ４１の抗力よりも剪断抵抗力が小さい場合には揺動部材４０は揺動しない。駆動軸４が一定の回転速度以上になり、それに伴って粘性流体１０による剪断抵抗力が線バネ４１の抗力以上になると、揺動部材４０がピン４２を中心として揺動するようになる。
【００６２】
図２１は、剪断抵抗力が上記設定値以上となった状態を示すもので、揺動部材４０がピン４２を中心として図中反時計回りに揺動し、壁部材４０ｂの円周部の外面４０ｂ２が室３の内周面３ａに当接しない程度に近接する。その結果、壁部材４０ｂの円周部の外面４０ｂ２と室３の内周面３ａとの間の隙間が狭まりこの隙間に存在する粘性流体１０の剪断抵抗力が高まるので高回転トルクが発生し、吊り戸等の移動に対して制動力が作用する。
【００６３】
このような高回転トルクにより駆動軸４の回転速度が減衰するにつれ、粘性流体よる剪断抵抗力も減少する。そして、剪断抵抗力が線バネ４１の抗力以下になると、線バネ４１がその復帰力によって、支持部材４３上面の一方端４３ａを支点として支持されていた状態から、支持部材４３上面の両端４３ａ、４３ｂを支点として支持される状態に移行し、その結果、揺動部材４０がピン４２を中心として図中時計回りに揺動して元の位置に復帰する。
このように揺動部材４０が元の位置に復帰すると、壁部材４０ｂの円周部の外面４０ｂ２と室３の内周面３ａとの間の隙間も元の状態に復帰して広くなり回転トルクが減衰し、吊り戸等の移動に対する制動力も減衰する。
【００６４】
なお、図２２に示すように、図２１に示すのとは逆に駆動軸４が図中反時計回りに回転する場合には、揺動部材４０がピン４２を中心として図中時計回りに揺動し、壁部材４０ｂの円周部の外面４０ｂ２が室３の内周面３ａに当接しない程度に近接する。その後、剪断抵抗力が減少すると、線バネ４１の復帰力によって、揺動部材４０がピン４２を中心として図中反時計回りに揺動して元の位置に復帰する。
【００６５】
以上のように、第７構成例に係る回転ダンパでは、ダンパを取付けた吊り戸等の閉戸動作が一時的に速くなった場合に、粘性流体よる剪断抵抗力が増大して高回転トルクを発生させ、吊り戸等の移動に対する制動力が直ちに作用して急激な動作を十分に吸収できる。
【００６６】
次ぎに、上記第７構成例の変更例である第８構成例に係る回転ダンパに関して、図２３に基づいて説明する。この構成例の回転ダンパは、基部６を駆動軸４による軸支持部分から室３の径方向の一側にのみ延出するように配設し、基部６の外側端に揺動部材４０を取付けた構造を有する。すなわち、単一の揺動部材が用いられる。
第７構成例と比べて、揺動部材４０が揺動する際に、室３の内周面３ａに近接する壁部材４０ｂの外面４０ｂ２の面積が半分となることから、それ程大きな回転トルクを必要としない場合に好適に用いられる。
【００６７】
さらに、上記第７構成例の変更例である第９構成例に係る回転ダンパに関して、図２４に基づいて説明する。第７構成例で用いた各揺動部材４０が、ピン４２、４２の軸支部分を通る直線に対して左右対称であるのに対して、この構成例の各揺動部材４０は同直線に対して片側にのみ位置する部分から構成され、かつ、各揺動部材４０は駆動軸４に対して対称となる位置に配設される。
この回転ダンパでは、駆動軸４が図中反時計回りに回転する場合に高回転トルクが発生して吊り戸等の閉戸動作に対して制動力が作用し、駆動軸４が図中時計回りに回転する場合には高回転トルクが得られないので、一方向性の回転ダンパとして使用できる。
【００６８】
次ぎに、以上説明した回転ダンパを利用した、本発明の第３発明に係るスライドして開閉する吊り戸用制動装置の一実施形態について添付した図面に基づき説明する。このような吊り戸用制動装置は、上述した第１又は第２発明に係る回転ダンパを主構成要素とするもので、自重によってスライドしながら自閉する吊り戸に取付けて使用するものである。図１０は吊り戸制動用の回転ダンパの断面図、図１１はこのような制動装置を吊り戸に適用した例を示す正面図、図１２は同側面図である。
【００６９】
図１０には、スライドしながら自閉する吊り戸用制動装置に、図１〜図４に示す本発明に係る第１構成例の回転ダンパ１を用いた例を示す。ここで、ハウジング２から外部に突出した駆動軸４の他端側４ｂの端部は一方向クラッチ２０の軸孔２０ａに軸支されており、一方向クラッチ２０がピニオン２１の軸孔２１ａにさらに軸支されている。一方向クラッチ２０は、ピニオン２１が一方向に回転する際に、ピニオン２１の回転動作をダンパの回転軸４に伝達し、ピニオン２１が他方向に回転する際には、ピニオン２１の回転動作が回転軸４に伝達するのを阻止する働きを有する。
【００７０】
図１１及び図１２に示すように、自重によってスライドしながら自閉する吊り戸２２の上部の任意位置にブラケット２３を取付け、このブラケット２３に上述した回転ダンパ１のハウジング２を取付けてダンパを固定する。
吊り戸２２の上部の両端付近には、周方向に沿った凹部２４ａを備えた走行車輪２４がそれぞれ取付けられている。さらに、吊り戸２２の走行部分に沿って、上部が凸条２５ａのガイドレール２５が張設されている。走行車輪２４の凹部２４ａがガイドレール２５の凸条２５ａ上を回転することにより、走行車輪２４がガイドレール２５上を走行する。なお、吊り戸２２が自重によって閉じることが可能なように、ガイドレール２５は吊り戸２２が閉じる側に沿って下方に傾斜している。
【００７１】
ガイドレール２５とこれが取付けられる壁２６との間には、ガイドレール２５の下方に傾斜した端部付近と略平行な線上に、ピニオン２１と噛合うラック２７が設けられている。
【００７２】
次ぎに、このように構成された吊り戸用制動装置１９の作用等について説明する。
図１１には、吊り戸２２が開けられている状態が示されている。この状態において、ガイドレール２５が下方に傾斜する方向（Ｘ）に吊り戸２２を押すと、走行車輪２４の凹部２４ａがガイドレール２５の凸条２５ａ上を回転してガイドレール２５上を走行しつつ、ガイドレール２５の傾斜により吊り戸２２は自重によってＸ方向に移動する。
【００７３】
このようにして吊り戸２２が移動しピニオン２１がラック２７と係合し始めると、ピニオン２１はラック２７と噛合いつつ図１１における図中時計回りに回転する。駆動軸４に取付けられた不図示の一方向クラッチは、ピニオン２１がこの方向に回転する際にピニオン２１の回転動作をダンパの回転軸４に伝達するように作動するので、ピニオン２１がラック２７と噛合い動作中においてはピニオン２１の回転動作はダンパの回転軸４に伝達される。
【００７４】
ピニオン２１の回転動作がダンパの回転軸４に伝達されると、図４に示すように、トルク調整体７が駆動軸４に対して所定角度をもって配置されつつ、駆動軸４と、基部６と、トルク調整体７と、一対のスライド部材８、８と、引張りバネ９手段とからなる回転部材５が一体的に回転する。トルク調整体７が駆動軸４に対して所定角度をもって配置されているので、一対のスライド部材８、８の外面８ｃ、８ｃと室３の内周面３ａとの間には径方向に所定の間隔を有する隙間が形成される。
したがって、スライド部材８の回転により前記隙間に存在する粘性流体１０に剪断力が作用して回転トルクが発生するので、ピニオン２１とラック２７との噛合動作中は、回転部材５の回転によるトルクを制動力として発生させることができる。
【００７５】
このようにして発生する制動力が、今度はピニオン２１とラック２７との噛合い動作に作用し、結果として吊り戸の移動に制動力が働く。したがって、ピニオン２１がラック２７と噛合い始めると、吊り戸のスライドする勢いが低減してゆっくり閉じることができる。
【００７６】
一方、このようにして吊り戸２２が閉じられた状態からこれをスライドさせて開ける際には、ガイドレール２５が上方に傾斜する方向（Ｙ）に吊り戸２２を押し上げるように移動させる。
ピニオン２１がラック２７と噛合って回転する際には、駆動軸４に取付けられた一方向クラッチ２０により、ピニオン２１の回転動作がダンパの回転軸４に伝達されないので、吊り戸２２の移動に対して制動力は作用しない。したがって、吊り戸２２の傾斜自重に基づくＸ方向に作用する力に抗して吊り戸２２をＹ方向に押し上げる力だけでこれをＹ方向に移動することができる。
【００７７】
ところで、図１１に示す吊り戸２２が開けられている状態において、例えば誤って吊り戸２２がＸ方向に非常に大きな力で押される場合には、吊り戸２２は急激にＸ方向にスライドしてピニオン２１がラック２７と係合する。このような係合の初期には、一時的に高負荷がピニオン２１に作用してピニオン２１が高速回転しこの回転が回転ダンパ１の回転軸４に伝達される。
【００７８】
しかしながら、回転ダンパ１の各スライド部材８には駆動軸４の回転数に応じた大きな遠心力が作用するが、引張りバネ９の引張り力をこのような急激な閉鎖動作に基づく遠心力より小さく設定してあるため、引張りバネ９の引張り力に抗してそれを上回る遠心力によって各スライド部材８がトルク調整体７から離間する。その結果、各スライド部材８の各外面８ｃと室３の内周面３ａとの間に形成される径方向における間隔を一時的にさらに狭くして極めて高いトルクを発生させることができ、吊り戸の一時的な急激な閉戸動作を吸収するのに十分な制動力が得られる。
【００７９】
なお、上記第１構成例の回転ダンパに代わって上記第２〜９構成例に示す回転ダンパを用いてもよい。これらを用いる場合にも、ハウジング２から外部に突出した駆動軸４の他端側４ｂの端部を上記一方向クラッチと同じ働きを有するクラッチの軸孔に軸支し、さらにこのような一方向クラッチをピニオンの軸孔に軸支して用いる。そして、このような回転ダンパを用いた場合においても、上述のような作用効果が同様に得られる。
第７構成例の回転ダンパを用いた例を図２５に示す。回転ダンパ１のハウジング２から外部に突出した駆動軸４の他端側４ｂの端部を一方向クラッチ２０の軸孔２０ａに軸支し、一方向クラッチ２０をピニオン２１の軸孔２１ａにさらに軸支して用いるものである。
【００８０】
以上説明した制動装置では、開閉方向にスライドする吊り戸に回転ダンパを取付けて用いる例について説明したが、このような例に限定されるものではない。例えば、第２構成例に係る回転ダンパ１を用いて、図４において、ハウジング２から外部に突出した駆動軸４の他端側４ｂの端部を一方向クラッチ２０の軸孔２０ａに軸支し、かつ、この一方向クラッチ２０がピニオン２１の軸孔２１ａに軸支された構成のみを採用して、回転式のドア、ならびに、各種機器や装置の蓋や戸等に適用することも可能である。図１３は、機器の回転蓋に応用した例を示す断面図である。
【００８１】
この例では、蓋２８の外枠２９内に回転ダンパ１のハウジング２が埋め込まれて固定される。また、蓋の回転軸３０内には上記ピニオン２１と噛合うギア３１が埋め込まれて固定されている。
蓋２８が閉じる方向に回転する際には、ギア３１の回転動作がピニオン２１を介して回転ダンパ１の駆動軸４に伝達される。その結果、ダンパの回転部材の回転によって回転トルクが発生し、蓋２８の回転動作に対する制動力として作用する。
一方、蓋２８が開く方向に回転する際には、ギア３１の回転動作のピニオン２１への伝達が阻止されるので、ダンパによる回転トルクが発生しない。したがって、蓋２８を楽に持ち上げて開けることができる。
【００８２】
また、開閉方向にスライドする吊り戸を用いた上記制動装置では、吊り戸が閉まる側に下方傾斜したガイドレールを設けることによって、吊り戸が自閉するようになっている。しかしながら、このような自閉機構に代えて、例えば、図３５、図３６に示すような牽引機構を採用することによって、吊り戸を閉じるようにしてもよい。
【００８３】
図３５に示す例では、吊り戸２２の上部には回転ダンパ１とこれを挟むように２つの走行車輪２４、２４が取付けられる。吊り戸２２の走行部分にはガイドレール２５が張設され、その上を走行車輪２４、２４が走行する。
ガイドレール２５の一端側が取付けられた壁８３部分には、内部にゼンマイバネ８４が収容された牽引機構８５が取付けられている。吊り戸上部の壁８３側の端部と牽引機構８５のゼンマイバネ８４との間には、ワイヤー８６が張設されている。
吊り戸２２をＸ方向に押すと、ゼンマイバネ８４が巻き上げられワイヤー８６も牽引機構内に引き込まれるので、吊り戸２２がＸ方向に移動して閉められる。ゼンマイバネ８４の張力に抗して吊り戸２２をＹ方向に引張ることによって吊り戸２２が開けられる。
【００８４】
次ぎに、図３６に示す例では、図３５の牽引機構８５に代わって、滑車８７と重り８８からなる牽引機構８９が用いられる。吊り戸上部の壁８３側の端部と牽引機構８９の重り８８との間に、滑車８７を介してワイヤー８６が張設されている。
吊り戸２２をＸ方向に押すと、吊り戸２２に作用する押力により吊り戸２２がＸ方向に移動して閉められる。重りの自重に抗して吊り戸２２をＹ方向に引張ることによって吊り戸２２が開けられる。
【００８５】
本発明の第３発明に係るスライド戸用制動装置は、以上のような構成としたことにより、吊り戸を閉じる際においては、ダンパにより発生する所望の制動力によって吊り戸を閉じることができ、かつ、吊り戸を開く際においては、制動力を受けることなく吊り戸を開けることができる。
【００８６】
また、回転ダンパのスライド部材を径方向にスライドさせることによってその外面と室の内周面との間に形成される径方向における間隔を調整して発生トルクを変化させるようにしたので、ダンパ本体の軸方向長さに関しては特に制限されないのでこれを短くできる。ダンパ本体は、壁とガイドレールとの間でこれらにほぼ直角となる方向にその軸方向を一致させるように配置されるので、壁とガイドレールとの間の距離を狭くすることができ、制動装置をコンパクトにすることができる。
【００８７】
さらに、上述のように、吊り戸に一時的に高負荷が作用して駆動軸の回転数が急激に増加した際においても、発生する遠心力をバネ手段の引張り力より小さく設定してあるので、斯かる一時的な高負荷を吸収する制動力を働くようにできる利点がある。
【００８８】
【発明の効果】
本発明の回転ダンパは、請求項１において、内部に室を備えたハウジングと、該室内に基端側が収容された駆動軸と、該駆動軸に軸支されて前記室内に収容された回転部材と、前記室内に充填された粘性流体とを備え、前記回転部材の回転によりトルクを発生する回転ダンパにおいて、
前記回転部材が、前記駆動軸と一体回転自在に軸支された基部と、前記駆動軸に対して固定関係を持ちつつ一定以上の外部力の作用により相対移動可能なトルク調整体と、径方向に移動可能に配置され、かつ前記室の内周面の一部と相補的な外面を有するスライド部材と、該スライド部材を前記トルク調整体に対して付勢するバネ手段とを備え、
前記駆動軸に対して前記トルク調整体を相対移動させることにより、前記スライド部材を前記基部に沿って径方向にスライドさせて該スライド部材の外面と前記室の内周面との間の径方向の間隔を変化させることによって前記回転部材の回転トルクを変化させるようにした。
【００８９】
スライド部材を径方向にスライドさせることによってその外面と室の内周面との間に形成される径方向における間隔を調整し、この隙間に存在する粘性流体の前記間隔に応じた剪断抵抗力に基づいて発生するトルクが得られる。したがって、発生トルクは径方向の前記間隔に依存して変化可能なので、ダンパ本体の軸方向長さを短くすることが可能となるので、軸方向長さが狭い場所にダンパを取付けなければならないような場合においてもダンパの取付けが可能である。
【００９０】
請求項２では、前記トルク調整体が、前記回転部材の基部に一体回転自在に取付けられた調整リングと、該調整リングの外周に取付けられたカム部材とからなり、前記調整リングの外周と前記カム部材の中央孔の内周とは一方に形成された凹部と他方に形成された凸部とにより係合し、該凹部と凸部が、一定以上の外部力が前記カム部材に作用すると、前記カム部材が前記調整リング及び前記駆動軸に対して所定角度相対回動することを許容するように構成した。
調整リングの外周とカム部材の中央孔の内周とが凹部と凸部によって係合することにより、駆動軸に対してトルク調整体を所定角度をもって確実に配置することができる。
【００９１】
請求項３では、前記トルク調整体のカム部材の外周を楕円形としたことにより、一対のスライド部材とカム部材との各接触部のカム部材中心からの距離を、連続的に変位することができる。したがって、得られる発生トルクも連続的に変化可能であるので、ダンパを取付ける戸や蓋等に応じた所望の制動力を選択して得ることができる。
【００９２】
請求項４では、前記トルク調整体を前記駆動軸に対して所定角度相対回動させるための作動部を、前記カム部材のハウジングから突出した軸方向突起部に設けるようにしたことにより、トルク調整体を容易に該所定角度の位置まで回動することができる。このような作動部としては、例えば、カム部材の外側端にドライバーの先端と係合可能な溝や指で操作可能なツマミ等が用いられる。
【００９３】
請求項５では、前記トルク調整体が、前記回転部材の基部に一体回転自在かつ軸方向移動自在に取付けられたカム部材と、該カム部材と係合する調整部材とからなり、前記カム部材は、外周に傾斜面からなるカム面と、軸方向一側に前記回転部材に連結された連結部と、軸方向他端に形成された壁部とを有し、前記調整部材は、軸方向内端部に前記カム部材の壁部と係合する作動面を有し、前記カム面と作動面とを、一定以上の外部力が前記調整部材に作用すると、前記作動面の前記カム部材の前記壁部と係合する部位の位置が軸方向に移動し、もって前記カム部材が前記駆動軸に沿って移動することを許容するように構成した。
回転部材の回転により所望のトルクを発生させるための、スライド部材の外面と室の内周面との間の径方向における所定の距離を得るために、調整部材の作動面と接するカム傾斜面の位置を連続的に変化させることによって駆動軸に沿ってカム部材を所定距離だけ確実に移動して配置することができる。
【００９４】
請求項６では、調整部材がハウジング外に突出した外端部を有するようにし、カム部材を駆動軸に沿って移動させるための作動部を前記外端部に設けるようにした。
このような作動部によって、カム部材を駆動軸に沿った所定位置まで容易に移動することができ、このような作動部としては、例えば、ドライバーの先端と係合可能な溝や指で操作可能なツマミが用いられる。
【００９５】
請求項７では、前記バネ手段の付勢力を、回転ダンパの回転によって前記スライド部材に作用する所定の遠心力であって、例えば、吊り戸等に一時的に高負荷が作用して駆動軸の回転数が急激に増加した際に発生する遠心力より小さくなるようにした。
【００９６】
このような高負荷の作用時にスライド部材に働く遠心力をバネ手段の付勢力を上回るように設定してあるので、この遠心力によってスライド部材はバネ手段の付勢力に抗して接していたトルク調整体から互いに離間し合うようになる。したがって、スライド部材の外面と室の内周面との間に形成される径方向における間隔を一時的に狭くでき、これに応じて極めて高いトルクを一時的に発生できる。このようにして得られる高トルクにより一時的な高負荷を吸収できるので、ダンパが取付けられた吊り戸等の急激な閉戸動作に対して十分な制動力を作用させることが可能となる。
【００９７】
さらに、駆動軸の回転数が元の低回転数に戻ると、遠心力がバネ手段の引張り力以下に低減するので、スライド部材はバネ手段の引張り力によってトルク調整体に接するように再び付勢され、所期の設定トルクを発生できる状態に復帰する。
【００９８】
請求項８では、スライド部材を、室の径方向においてトルク調整体を介した両側にそれぞれ配置された一対の部材からなるようにしたので、室の内周面に対面するスライド部材の外面の総面積を増大して大きな発生トルクを得ることができる。このような構成の回転ダンパは、比較的重量の重い吊り戸等に取付けて用いるのに適している。
請求項９では、スライド部材を、室の径方向においてのトルク調整体の一側に配置された単一部材からなるようにしたので、室の内周面に対面するスライド部材の外面の総面積を小さくして発生トルクを小さくすることができる。このような回転ダンパは、比較的重量の軽い吊り戸等に好適に用いられる。
【００９９】
第２の発明に係る回転ダンパは、請求項１０において、内部に室を備えたハウジングと、該室内に基端側が収容された駆動軸と、該駆動軸に軸支されて前記室内に収容された回転部材と、前記室内に充填された粘性流体とを備え、前記回転部材の回転によりトルクを発生する回転ダンパにおいて、
前記回転部材が、前記駆動軸に一体回転自在に軸支された基部と、該基部に揺動可能に取付けられ、かつ前記室の内周面の一部と相補的な外面を有する揺動部材と、該揺動部材と前記基部間に介設され、一定以上の力が揺動部材に作用したときに揺動部材の揺動を許容するバネ手段とを備え、
前記駆動軸の回転により生じる前記一定以上の力によって前記揺動部材を前記基部に対して揺動させて該揺動部材の外面と前記室の内周面との隙間を狭めることによってトルクを発生させるようにしたことを特徴とする。
【０１００】
駆動軸の回転によって発生する粘性流体の剪断抵抗力がバネ手段の抗力以上になると、揺動部材の揺動による回転トルクが得られる。駆動軸の回転速度が一時的に速くなって場合に直ちに高トルクが得られるので、回転ダンパを取付けた吊り戸等の急激な閉戸動作に対しても制動力が直ちに作用し、このような急激動作による一時的な高負荷を容易に吸収できる。
また、高トルクが得られた後には、駆動軸の回転速度の減衰と共に粘性流体による剪断抵抗力も減少する。その結果、バネ手段の復元力によって揺動部材が元に位置に復帰しつつトルクも減衰する。したがって、吊り戸等の急激な閉戸動作に対して制動力が作用した後に、直ちに元の正常な閉戸動作に復帰可能である。
【０１０１】
請求項１１では、前記基部を前記駆動軸による軸支部分から径方向の両側に延出させ、前記揺動部材を、該基部の両端にそれぞれ取付けられた一対の部材からなるようにした。これにより室の内周面に近接する揺動部材の外面の総面積を増大させて大きな発生トルクを得られるので、このような回転ダンパは比較的重量の重い吊り戸等に好適に用いられる。
請求項１２では、前記基部を前記駆動軸による軸支部分から径方向の一側に延出させ、前記揺動部材を、該基部の外側端に取付けられた単一部材からなるようにした。これにより室の内周面に近接する揺動部材の外面の総面積を小さくして発生トルクを小さくできるので、このような回転ダンパは比較的重量の軽い吊り戸等に対して好適に用いられる。
このように、回転ダンパを取付ける吊り戸等の重量に応じて、一対又は単一の揺動部材を用いた回転ダンパを選択できる。
【図面の簡単な説明】
【図１】本発明の第１構成例に係る回転ダンパの分解斜視図である。
【図２】同回転ダンパの右側面図である。
【図３】図２において蓋を取外した内部説明図である。
【図４】図３のＡ−Ａ断面図である。
【図５】本発明の第２構成例に係る回転ダンパの分解斜視図である。
【図６】同回転ダンパの右側面図である。
【図７】図６において蓋を取外した内部説明図である。
【図８】図７のＢ−Ｂ断面図である。
【図９】本発明の第３構成例に係る回転ダンパの断面図である。
【図１０】吊り戸制動用として用いる第１構成例に係る回転ダンパの断面図である。
【図１１】本発明に係る吊り戸用制動装置を吊り戸の開閉に適用した例を示す正面図である。
【図１２】本発明に係る吊り戸用制動装置を吊り戸の開閉に適用した例を示す側面図である。
【図１３】本発明に係る制動装置を回転式の蓋に適用した例を示す断面図である。
【図１４】従来のドアクローザ用液体摩擦抵抗型ダンパ装置を示す断面図である。
【図１５】従来のドアクローザ用液体摩擦抵抗型ダンパ装置を引き戸に適用した状態を示す側面図である。
【図１６】本発明の第４構成例に係る回転ダンパの内部説明図である。
【図１７】本発明の第５構成例に係る回転ダンパの内部説明図である。
【図１８】本発明の第７構成例に係る回転ダンパの分解斜視図である。
【図１９】同回転ダンパの内部説明図である。
【図２０】図１９のＣ−Ｃ断面図である。
【図２１】同回転ダンパにおいて、駆動軸の回転によって揺動部材が揺動する状態を示す説明図である。
【図２２】同回転ダンパにおいて、駆動軸の回転によって揺動部材が揺動する状態を示す説明図である。
【図２３】本発明の第８構成例に係る回転ダンパの内部説明図である。
【図２４】本発明の第９構成例に係る回転ダンパの分解斜視図である。
【図２５】吊り戸制動用として用いる第７構成例に係る回転ダンパの断面図である。
【図２６】本発明の第６構成例に係る回転ダンパに用いるトルク調整体のカム部材を示す斜視図である。
【図２７】本発明の第６構成例に係る回転ダンパに用いるトルク調整体の調整部材を示す斜視図である。
【図２８】最大トルクを発生させる状態にある、本発明の第６構成例に係る回転ダンパの断面図である。
【図２９】最小トルクを発生させる状態にある、本発明の第６構成例に係る回転ダンパの断面図である。
【図３０】本発明の第６構成例に係る回転ダンパに用いるトルク調整体の変更例を示す断面図である。
【図３１】本発明の第６構成例に係る回転ダンパに用いるトルク調整体の変更例を示す断面図である。
【図３２】本発明の第６構成例に係る回転ダンパに用いるトルク調整体のカム部材の変更例を示す斜視図である。
【図３３】トルク調整体の作動部の変更例を示す斜視図である。
【図３４】トルク調整体の作動部の変更例を示す斜視図である。
【図３５】本発明に係る吊り戸用制動装置を吊り戸の開閉に適用した例を示す側面図である。
【図３６】本発明に係る吊り戸用制動装置を吊り戸の開閉に適用した例を示す側面図である。
【符号の説明】
１・・回転ダンパ、２・・ハウジング、３・・室、３ａ・・内周面、４・・駆動軸、４ａ・・基端側、５・・回転部材、６・・基部、７・・トルク調整体、７１・・調整リング、７１ｂ・・凸部、７２，７４・・カム部材、７２ａ・・突起、７２ｂ・・凹部、７３，７２ｄ，７６・・作動部、７４ｃ・・突起、７４ｄ、７４ｅ・・連結部、７４ｆ・・カム面、７４ｇ・・壁部、７５・・調整部材、７５ｂ・・作動面、８・・スライド部材、８ｃ・・外面、９，４１・・バネ手段、１０・・粘性流体、１９・・吊り戸用制動装置、２０・・一方向クラッチ、２１・・ピニオン、２２・・吊り戸、２４・・走行車輪、２５ガイドレール、２７・・ラック、４０・・揺動部材。[0001]
BACKGROUND OF THE INVENTION
The present invention is generated by allowing a slide member constituting a rotating member to be slidable in a radial direction along a base portion, and adjusting a distance between an outer surface of the slide member and an inner peripheral surface of a chamber inside the housing. Torque is generated by reducing the distance between the outer surface of the swinging member that can be adjusted by the magnitude of the torque and the outer surface of the swinging member that swings by a force exceeding a certain level generated by the rotation of the drive shaft and the inner peripheral surface of the chamber. It relates to a rotary damper.
[0002]
[Prior art]
Conventionally, when an open hanging door or the like is closed, the door collides with the door frame due to an abrupt closing operation, which causes a problem that a collision sound is generated or the door or the door frame is damaged. In order to prevent such a sudden closing operation, various dampers for braking the closing operation have been proposed.
[0003]
For example, as shown in FIG. 14, Japanese Patent Application Laid-Open No. 8-93312 discloses an adjusting screw that is screwed to a rotating drum 34 fixed to a brake shaft 33 and a base portion 31A fixed to a lid portion 31B of a housing 31. 35, a movable drum 36 that is screwed to the adjustment screw 35 and is movable along the groove 31C of the lid portion 31B, and a one-way clutch 37 that transmits a rotational motion in only one direction to the brake shaft 33. A fluid friction resistance damper device for a door closer is disclosed.
[0004]
Further, as shown in FIG. 15, such a damper device is attached to the sliding door, and the pinion 13 attached to the brake shaft 33 is engaged with the rack 12 fixed to the guide rail member 11 on the door frame side. When the closing operation is performed, the rotation operation of the pinion 13 is transmitted to the braking shaft 33 by the clutch 37 to brake the closing operation. On the other hand, when the opening operation is performed, the rotation of the pinion 13 is performed by the clutch 37. Operation is prevented from being transmitted to the brake shaft 33.
[0005]
However, in such a damper device, by moving the movable drum 36 along the axial direction in the housing 31, the contact / sliding area between the outer peripheral surface of the movable drum 36 and the inner peripheral surface of the rotary drum 34 is reduced. By changing, the magnitude of the generated torque is adjusted. Therefore, when the generated torque is adjusted to be small, it is necessary to reduce the contact / sliding area of the both surfaces. In such a case, the radial surfaces of the movable drum 36 and the rotary drum 34 need to be greatly separated from each other. As a result, there is a disadvantage that the axial length of the damper main body cannot be shortened.
[0006]
Furthermore, when the door is suddenly closed by hand, a very high load temporarily acts on the door. However, since the magnitude of the torque generated by the damper device is constant, the high load cannot be absorbed and a sufficient damper is applied. The effect is not obtained. As a result, the door closing operation is not braked, and there is a problem that it is impossible to avoid the generation of a collision sound and the door damage due to the door colliding with the door frame or the like.
[0007]
[Problems to be solved by the invention]
Therefore, a compact damper having a short axial length and a damper capable of absorbing an extremely high load that temporarily acts when the door is suddenly closed have been desired.
[0008]
[Means for Solving the Problems]
According to a first aspect of the present invention, there is provided a rotary damper according to a first aspect of the present invention, wherein the housing includes a housing having a chamber therein, a drive shaft having a base end accommodated in the chamber, and a shaft support on the drive shaft. In a rotary damper comprising a rotating member housed in the chamber and a viscous fluid filled in the chamber, and generating torque by rotation of the rotating member,
A base portion that is rotatably supported integrally with the drive shaft; a torque adjusting body that has a fixed relationship with the drive shaft and is relatively movable by the action of an external force of a certain level; and a radial direction And a slide member having an outer surface complementary to a part of the inner peripheral surface of the chamber, and spring means for biasing the slide member against the torque adjusting body,
By moving the torque adjusting body relative to the drive shaft, the slide member is slid in the radial direction along the base, and the radial direction between the outer surface of the slide member and the inner peripheral surface of the chamber The rotational torque of the rotating member is changed by changing the interval.
[0009]
By controlling the distance in the radial direction formed between the outer surface of the slide member and the inner peripheral surface of the chamber by sliding the slide member in the radial direction, the shear resistance of the viscous fluid existing in the gap is reduced. Since the generated torque can be changed based on this, there is no restriction on the axial length of the damper body.
[0010]
According to a second aspect of the present invention, the torque adjustment body includes an adjustment ring that is attached to the base of the rotating member so as to be integrally rotatable, and a cam member that is attached to the outer periphery of the adjustment ring. The inner periphery of the central hole of the cam member is engaged by a concave portion formed on one side and a convex portion formed on the other side, and when a certain external force acts on the cam member, the cam member is And the said recessed part and the convex part were comprised so that it might allow a predetermined angle relative rotation with respect to the said drive shaft. Thereby, a torque adjustment body can be reliably arrange | positioned with a predetermined angle with respect to a drive shaft.
[0011]
According to a third aspect of the present invention, since the outer periphery of the cam member of the torque adjuster is elliptical, the distance from the center of the cam member of each contact portion between the slide member and the cam member can be continuously displaced.
[0012]
According to a fourth aspect of the present invention, the cam member has an axial protrusion protruding outside the housing, and an operating portion for rotating the torque adjuster relative to the drive shaft by a predetermined angle is provided on the protrusion of the cam member. I did it. Thereby, the torque adjustment body can be easily rotated to the position of the predetermined angle.
[0013]
According to a fifth aspect of the present invention, the torque adjuster includes a cam member attached to the base of the rotating member so as to be integrally rotatable and axially movable, and an adjusting member engaged with the cam member. A cam surface having an inclined surface on the outer periphery, a connecting portion connected to the rotating member on one side in the axial direction, and a wall portion formed at the other end in the axial direction, An end surface has an operation surface that engages with a wall portion of the cam member, and the cam surface and the operation surface are configured such that when a certain external force acts on the adjustment member, the cam member of the operation surface The position of the portion engaged with the wall portion is moved in the axial direction, so that the cam member is allowed to move along the drive shaft. Thereby, a cam member can be reliably arrange | positioned with a predetermined distance along a drive shaft.
[0014]
According to a sixth aspect of the present invention, the adjustment member has an outer end protruding from the housing, and an operating portion for moving the cam member along the drive shaft is provided at the outer end. Thereby, the cam member can be easily moved to a predetermined position along the drive shaft.
[0015]
According to a seventh aspect of the present invention, the biasing force of the spring means is a predetermined centrifugal force that acts on the slide member by the rotation of a rotary damper. It was made to become smaller than the centrifugal force generated when the rotational speed increased rapidly.
Since the centrifugal force generated in this way exceeds the biasing force of the spring means, the slide members are separated from the state biased by the torque adjusting body against the biasing force of the spring means. As a result, the radial interval formed between the outer surface of the slide member and the inner peripheral surface of the chamber can be further narrowed temporarily. It is possible to absorb and apply a sufficient braking force to the hanging door or the like.
Further, when the rotational speed of the drive shaft returns to the original value, the slide member is again urged to the torque adjusting body by the spring means, and returns to a state where the original set torque can be generated.
[0016]
According to an eighth aspect of the present invention, the slide member is composed of a pair of members respectively disposed on both sides of the chamber in the radial direction via the torque adjuster. Since the total area of the outer surface of the slide member facing the inner peripheral surface of the chamber can be increased, the generated torque can be increased.
According to a ninth aspect of the present invention, the slide member is a single member disposed on one side of the torque adjuster in the radial direction of the chamber. Since the total area of the outer surface of the slide member facing the inner peripheral surface of the chamber is reduced, the generated torque can be reduced.
[0017]
The rotary damper according to a second aspect of the present invention is the rotary damper according to claim 10, wherein the housing is provided with a chamber therein, the drive shaft having a base end accommodated in the chamber, and supported by the drive shaft and accommodated in the chamber. A rotating damper that includes a rotating member and a viscous fluid filled in the chamber, and generates torque by rotation of the rotating member.
The rotating member has a base that is pivotally supported by the drive shaft so as to rotate integrally therewith, and a swinging member that is swingably attached to the base and has an outer surface that is complementary to a part of the inner peripheral surface of the chamber. And a spring means interposed between the swinging member and the base, and allowing the swinging member to swing when a force of a certain level or more is applied to the swinging member,
Torque is generated by narrowing the gap between the outer surface of the swinging member and the inner peripheral surface of the chamber by swinging the swinging member with respect to the base by the force above a certain level generated by the rotation of the drive shaft. It was made to let it be made to do.
[0018]
When the shear resistance force of the viscous fluid due to the rotation of the drive shaft exceeds the drag force of the spring means, the swing member swings and rotational torque is generated. When the rotational speed of the drive shaft temporarily increases, a high torque is immediately obtained, and then the torque can be attenuated as the rotational speed decreases.
[0019]
According to another aspect of the present invention, the base portion is extended from the shaft support portion by the drive shaft to both sides in the radial direction, and the swinging member is composed of a pair of members respectively attached to both ends of the base portion. Since the total area of the outer surface of the member close to the inner peripheral surface of the chamber can be increased when the swinging member swings, the generated torque can be increased.
According to a twelfth aspect of the present invention, the base portion is extended from the shaft support portion of the drive shaft to one side in the radial direction, and the swinging member is made of a single member attached to the outer end of the base portion. . Since the total area of the outer surface of the member adjacent to the inner peripheral surface of the chamber can be reduced when the swinging member swings, the generated torque can be reduced.
[0020]
DETAILED DESCRIPTION OF THE INVENTION
A first structural example of a rotary damper according to a first aspect of the present invention will be described with reference to the accompanying drawings. 1 is an exploded perspective view of the rotary damper, FIG. 2 is a right side view, FIG. 3 is an internal explanatory view with the lid removed in FIG. 2, and FIG. 4 is a cross-sectional view taken along line AA in FIG.
[0021]
As shown in FIGS. 1, 3 and 4, the rotary damper 1 of the present invention accommodates a base end side 4a of a drive shaft 4 in a chamber 3 inside a housing 2, and a rotary member on the base end side 4a. 5, the chamber 3 is filled with a viscous fluid 10, and the rotating member 5 is rotatable relative to the housing 2.
[0022]
Here, the rotating member 5 includes a substantially oval base 6 that is pivotally supported by inserting the base end side 4 a of the drive shaft 4 into the shaft hole 6 a, and a circular protrusion provided on one surface of the base 6. A torque adjusting body 7 attached to 6b, a pair of slide members 8 and 8 arranged in contact with the torque adjusting body 7 while facing each other, and a torque for the pair of slide members 8 and 8. It comprises a pair of tension spring means 9, 9 that biases the adjusting body 7. The torque adjustment body 7 includes an inner adjustment ring 71 attached to the circular protrusion 6b, an outer elliptical cam member 72 attached to the outer periphery of the adjustment ring 71 and engaged therewith, and an adjustment knob 73. Consists of
[0023]
A circular protrusion 6b is provided on one surface of the base 6, and two engagement protrusions (not shown) formed on the outer surface of the protrusion 6b are connected to two engagement protrusions formed on the inner surface of the adjustment ring 71. The adjustment ring 71 is non-rotatably attached to the base 6 by engaging the mating recesses 71a and 71a, respectively.
[0024]
The adjustment ring 71 and the cam member 72 are configured to be engaged by a recess formed on one of the outer periphery of the adjustment ring and the inner periphery of the cam member central hole and a protrusion formed on the other.
For example, as shown in FIG. 1, a structure in which two convex portions 71 b and 71 b along the axial direction are provided on the outer surface of the adjustment ring 71 and a plurality of protrusions 72 a along the axial direction are formed on the inner surface of the cam member 72. Adopted. When the cam member 72 is rotated with respect to the drive shaft 4 via the adjustment ring 71, the protrusions 72a of the cam member 72 sequentially pass over the protrusions 71b of the adjustment ring 71, and the recesses between the protrusions 72a and 72a are stopped by stopping the rotation. The projecting portion 71b is engaged with 72b.
Instead of such a structure, a concave portion along the axial direction is provided on the outer surface of the adjustment ring 71, and a plurality of convex portions along the axial direction are formed on the inner surface of the cam member 72 to stop the rotation of the drive shaft. Accordingly, the convex portion on the inner surface of the cam member 72 may be engaged with the concave portion on the outer surface of the adjustment ring 71.
[0025]
As shown in FIGS. 1 and 4, an adjustment knob 73 as an operating portion is fitted to the end portion of the shaft 72 c of the cam member 72. The adjustment knob 73 includes a ring-shaped main body, a screw hole 73b along the radial direction of the main body, and a screw 73a that is screwed into the screw hole 73b. Is pressed against the outer surface of the shaft 72 c of the cam member 72 to fix the adjustment knob 73 to the cam member 72. The cam member 72 can be easily rotated with respect to the base 6 by turning the adjustment knob 73.
[0026]
As a method of fixing the adjusting knob 73 as the operating portion to the end portion of the shaft 72c of the cam member, for example, a method as shown in FIGS.
In the example shown in FIG. 33, holes 73 c and 73 c are provided along the radial direction of the ring-shaped main body of the adjustment knob 73. The two holes 73c are arranged at positions facing the center of the ring-shaped main body, and the central axes of these two holes are in a straight line. On the other hand, a hole 72f is also provided at the end of the shaft 72c of the cam member. The ring-shaped main body of the adjusting knob 73 is fitted to the end of the shaft 72c of the cam member so that the central axes of the two holes 73c and the hole 72f are aligned. By inserting a press-fit pin 73d such as a wave spring into the two holes 73c and 72f, the adjustment knob 73 is fixed to the end of the shaft 72c of the cam member. Note that, as a press-fit pin, Matsuba pin, Dharma pin or the like may be used in addition to the wave spring.
[0027]
In the example shown in FIG. 34, cut surfaces 72e and 72e along the axial direction are provided at the end of the shaft 72c of the cam member, and grooves 72f and 72f along the circumferential direction are formed on the peripheral surface of the uncut portion. Provided. On the other hand, the ring-shaped main body of the adjustment knob 73 is provided with a hole 73e that is complementary to the end of the shaft 72c. The end of the shaft 72c is fitted into the hole 73e so that the grooves 72f and 72f protrude outside from the hole 73e, and a retaining ring 73f is attached to the grooves 72f and 72f.
The adjusting knob 73 is in a non-rotating state and in a retaining state with respect to the cam member shaft 72c, whereby the adjusting knob 73 is fixed to the end of the cam member shaft 72c.
[0028]
Each slide member 8 includes a sliding portion 8a that slides in the radial direction along the base 6 surface on the side where the circular protrusion 6b is provided, and an outer wall 8b that is attached to the radial outer end of the sliding portion 8a. The outer wall 8 b has an outer surface 8 c that is complementary to the inner peripheral surface 3 a of the chamber 3. The sliding portions 8a and 8a of each slide member 8 are provided with long holes 8d and 8d corresponding to the holes 6c and 6c formed at both ends in the longitudinal direction of the base portion 6, respectively. By passing the presser pin 11 through the hole 6c and the long hole 8d, each slide member 8 can move radially in the chamber 3 within the clearance of the long hole 8d.
[0029]
A pair of holes 8e, 8e are provided in the vicinity of both ends of the inner end portion in the radial direction of the sliding portion 8a of each slide member 8. The holes 8e and 8e of one sliding part 8a and the holes 8e and 8e of the other sliding part 8a facing each other are connected by tension spring means 9 and 9, respectively. Due to the tension of the tension spring means 9, the pair of slide members 8, 8 are urged so as to contact the cam member 72 of the torque adjuster 7.
[0030]
Next, the operation and the like of the rotary damper 1 configured as described above will be described.
Such a rotary damper 1 is used, for example, by fixing the housing 2 to a suspension door and engaging the other end 4b of the drive shaft 4 with a rack parallel to the guide rail of the suspension door via a pinion or the like. Is done.
[0031]
When the suspension door is closed, the rotation operation of the suspension door is transmitted to the drive shaft 4 of the rotary damper 1, and the rotation member 5 rotates with the rotation of the drive shaft 4. Here, a gap having a predetermined interval is formed between the outer surfaces 8c, 8c of the pair of slide members 8, 8 and the inner peripheral surface 3a of the chamber 3, so that the gap is formed by the rotation of the slide member 8. A shearing force acts on the existing viscous fluid 10 to generate a rotational torque, thereby generating a torque due to the rotation as a braking force.
[0032]
The drive shaft is fixed so as not to rotate, and the adjustment knob 73 is rotated to rotate the cam member 72 to a predetermined angle with respect to the drive shaft 4 to obtain a desired rotational torque.
[0033]
That is, when the protrusion 72 a on the inner surface of the cam member 72 rotates so as to pass over the convex portions 71 b on the outer surface of the adjustment ring 71 one after another, the outer surface of the cam member 72 is in contact with both slide members 8, 8. They are separated or close to each other in the radial direction. Therefore, the rotation of the cam member 72 is stopped when a gap formed between the outer surface 8c of the slide member 8 and the inner peripheral surface 3a of the chamber 3 gives a desired interval. Thus, by rotating the cam member 72 relative to the drive shaft 4 to a predetermined angle, the torque generated when the rotating member rotates can be set to a desired magnitude.
[0034]
In the rotary damper 1, the cam member 72 is stopped with the convex portion 71 b on the outer surface of the adjustment ring 71 engaged with the concave portion 72 b between the projections 72 a on the inner surface of the cam member 72. Thus, the cam member 72 of the torque adjusting body 7 can be reliably arranged at a predetermined angle.
[0035]
Incidentally, since the cam member 72 has an elliptical shape, the distance from the center of the cam member 72 of the contact portions 12 and 12 between the slide member 8 and the cam member 72 (hereinafter referred to as “center distance”) as the cam member 72 rotates. Can be continuously changed. Therefore, the torque value generated by the rotation can be set as a continuous value, so that the braking force can be finely adjusted.
The cam 72 is not limited to an elliptical shape as long as the center distance changes as the cam 72 rotates. The cam 72 has a shape that allows a desired change in the center distance as the cam 72 rotates. It is good.
[0036]
In order to increase the generated torque, the center distance is increased from the initial one by rotation of the cam member 72, and the gap formed between the outer surface 8c of the slide member 8 and the inner peripheral surface 3a of the chamber 3 is further increased. Narrow. Conversely, when the center distance is reduced from the initial distance, the gap formed between the outer surface 8c of the slide member 8 and the inner peripheral surface 3a of the chamber 3 becomes wider, and as a result, is generated by rotation. Torque decreases.
[0037]
Further, when a high load is temporarily applied to the door or the like to which the rotary damper 1 is attached, the rotational speed of the drive shaft 4 increases rapidly and a sudden closing operation of the door or the like occurs. At this time, a large centrifugal force according to the rotational speed of the drive shaft 4 is temporarily applied to each slide member 8.
In the rotary damper 1 according to the present invention, since the tension force of the tension spring 9 is set smaller than the centrifugal force based on such a sudden closing operation, even if such a sudden closing operation occurs, Each slide member 8 is temporarily moved radially outward of the chamber 3 along the base 6 while being separated from the torque adjuster 7 by a centrifugal force that resists and exceeds the tensile force of the tension spring 9. As a result, an extremely high torque can be generated by temporarily further narrowing the radial distance formed between each outer surface 8c of each slide member 8 and the inner peripheral surface 3a of the chamber 3.
Thus, even if a temporary high load is applied and a sudden closing operation occurs, a sufficient braking force that absorbs such a rapid operation can be applied immediately thereafter.
[0038]
When the drive shaft 4 returns to the normal rotational speed by the action of such a braking force, each slide member 8 is urged again by the tension spring 9 so as to come into contact with the torque adjusting body 7 and generates a normal set torque. It returns to the state to do.
[0039]
As shown in FIG. 4, the other end 4b of the drive shaft 4 is fitted with the slider 33, the housing 2, the O-ring 15 and the plate 17 in this order from the inside, and finally the bearing 18 is pivotally supported outside the housing. It protrudes and is connected to, for example, a pinion (not shown). The other side (right side in the figure) of the housing 2 is closed by the lid 13 while interposing an O-ring 14 and a bush 32 for preventing leakage of the viscous fluid 10 between the torque adjusting body 7 and the cam member 72. . The O-ring 34 between the cam member 72 and the drive shaft 4, the O-ring 15 between the housing 2 and the drive shaft 4, and the O-ring 16 between the housing 2 and the lid 13 are also chambers. This is to prevent the leakage of the viscous fluid 10 from 3.
[0040]
Next, a rotary damper according to another configuration example of the first invention is shown below. In these configuration examples, only differences from the first configuration example will be described.
First, the rotary damper according to the second configuration example will be described with reference to FIGS. 5 to 8 respectively correspond to FIGS. 1 to 4 showing the first configuration example, and FIG. 8 is a cross-sectional view taken along the line BB of FIG. In this configuration example, an adjustment groove 72d as an operating portion is provided on the end surface of the shaft portion 72c of the cam member 72. For example, the cam member 72 is inserted by turning the tip of a minus driver into the adjustment groove 72d. Can be easily rotated relative to the base 6.
As shown in FIG. 8, on the other end side 4b of the drive shaft 4, the slider 33, the O-ring 15, the housing 2, the plate 17, and the bearing 18 are fitted in this order from the inside as in the first configuration example. . The other side (right side in the figure) of the housing 2 is closed by the lid 13 while interposing the O-ring 14 and the slider 32 for preventing leakage of the viscous fluid 10 between the torque adjusting body 7 and the cam member 72. . The O-ring 15 between the housing 2 and the drive shaft 4 and the O-ring 16 between the housing 2 and the lid 13 are also for preventing leakage of the viscous fluid 10 from the chamber 3. .
[0041]
Next, a rotary damper according to a third configuration example will be described with reference to FIG. In this configuration example, as a means for disposing the cam member 72 of the torque adjuster 7 at a predetermined position with respect to the base portion 6, the frictional force of the O-ring is used instead of the engagement between the concave portion 72b and the convex portion 71b.
[0042]
In this configuration example, the drive shaft 4 is a hollow shaft, and an adjustment shaft 72d integral with the cam member 72 is passed through the hollow portion, so that the space between the inner surface of the cam member 72 and the outer surface of the circular protrusion 6a of the base portion 6 is increased. An O-ring 39 is interposed. In this case, the outer end portion of the adjustment shaft 72d is a D-cut 72e, the drive shaft 4 is fixed so as not to rotate, and the D-cut 72e portion is rotated by pliers or the like so that the drive shaft 4 is rotated. The cam member 72 is rotated to a predetermined angle.
Since the O-ring 39 is crushed to some extent, the stopped state of the cam member 72 can be maintained almost reliably, and the cam member 72 can be engaged with the base portion 6 very easily.
[0043]
Next, the rotary damper according to the fourth and fifth configuration examples is configured such that the slide member is composed of a single member arranged on one side of the cam member in the radial direction of the chamber.
First, the rotary damper according to the fourth configuration example will be described with reference to FIG. This configuration example is the same as the first configuration example except that one of the pair of slide members is fixed to the base and only the other slide member is movable in the radial direction in the first configuration example. .
As shown in FIG. 16, the slide member 82 located at the lower side in the figure is integrated with the base portion 6 and is disposed so close that the outer surface 82 c does not contact the inner peripheral surface 3 a of the chamber 3. On the other hand, the holes 81e and 81e of the sliding portion 81a of the slide member 81 located at the upper side in the figure are connected to holes 82e and 82e provided in the slide member 82 via the tension springs 9 and 9, respectively. The cam member 72 is biased. The fixed slide member 82 is disposed away from the cam member 72 so that the outer peripheral surface of the cam member 72 does not contact the inner surface 82g of the fixed slide member 82 while the cam member 72 is rotating.
[0044]
Next, a rotary damper according to a fifth configuration example will be described with reference to FIG. This configuration example is the same as the first configuration example except that one of the pair of slide members is replaced with a fixed member and only the other slide member is movable in the radial direction in the first configuration example.
As shown in FIG. 17, the fixing member 82 is integrated with the base portion 6 and is disposed such that a gap exists between the outer surface 82 c and the inner peripheral surface 3 a of the chamber 3. On the other hand, the holes 81e and 81e of the sliding portion 81a of the slide member 81 located at the upper side in the figure are connected to the holes 82e and 82e provided in the fixing member 82 via the tension springs 9 and 9, respectively. Is biased by the cam member 72. The fixing member 82 is disposed away from the cam member 72 so that the outer peripheral surface of the cam member 72 does not contact the inner surface 82g of the fixing member 82 while the cam member 72 is rotating.
[0045]
The method of changing the center distance is not limited to the method using the torque adjuster as in the first to fifth configuration examples described above. For example, a method using a torque adjusting body composed of a cam member and an adjusting member engaged with the cam member as described below may be adopted, and the rotary damper according to the sixth configuration example adopting such a method, This will be described with reference to FIGS. Here, FIG. 26 is a perspective view of the cam member, FIG. 27 is a perspective view of the adjustment member, and FIGS. 28 and 29 are cross-sectional views along the axial direction of the rotary damper.
[0046]
As shown in FIG. 26, the cam member 74 includes a circular base 74a having a wall portion on one side and a hollow truncated cone 74b on the other side of the circular base 74a and having an outer periphery having a conical surface 74f. . A hemispherical projection 74c is provided on the wall surface 74g. An engagement groove 74e is formed in the opening 74d of the truncated cone 74b.
As shown in FIG. 27, the adjustment member 75 has an axial thickness δ continuously such that one surface 75b is an ellipse that forms an inclined surface with respect to the axial direction and the other surface 75c is circular. A changed circular base body 75a and a bar 75d extending in the axial direction from the circular surface 75c are provided. The inclined surface 75b of the adjusting member 75 constitutes an operating surface on which an external force is applied when the hemispherical projection 74c of the cam member 74 abuts.
[0047]
As shown in FIGS. 28 and 29, the opening 74 d of the truncated cone 74 b is a connecting portion with the base 6, and the circular protrusion 6 b of the base 6 is inserted into the opening 74 d so that the cam member 74 is connected to the base 6. Mounted. The cam member 74 is non-rotatably connected to the base 6 by engaging an engagement protrusion (not shown) of the base 6 with an engagement groove 74e provided in the opening 74d of the truncated cone 74b.
The adjustment member 75 is attached to the housing 2 with the O-ring 14 interposed in the bar 75d, and an adjustment knob 76 as an operating part is fitted to the other end of the bar 75d. The adjustment knob 76 includes a ring-shaped main body, a screw hole 78 extending in the radial direction of the main body, and a screw 77 screwed into the screw hole 78, and an end surface of the screw 77 while screwing the screw 77 into the screw hole 78. Is pressed against the outer surface of the bar 75d of the adjustment member 75 to fix the adjustment knob 76 to the adjustment member 75.
[0048]
By the tension spring means 9, the end surface 8 a 1 of the sliding portion 8 a of the slide member 8 is biased to the conical surface 74 f that is the cam surface of the cam member 74. The cam member 74 is urged by the adjustment member 75 so that the hemispherical projection 74 c of the cam member 74 abuts against the operating surface 75 b of the adjustment member 75 by the component force of the urging force in the axial direction of the drive shaft 4.
[0049]
In order to reduce the center distance, which is the radial distance between the outer surface 8c of the slide member 8 and the inner peripheral surface 3a of the chamber 3, the bar is formed by turning the adjusting knob 76 against the component force of the urging force. The operating surface 75b of the adjustment member 75 is rotated about 75d, and the position of the portion of the operating surface 75b that contacts the hemispherical protrusion 74c of the cam member 74 is changed. At this time, the outer surface 8c of the slide member 8 is moved to the inner peripheral surface 3a of the chamber 3 while moving the cam member to the left in the drawing so that the axial thickness δ of the circular base body 75 at the position in contact with the hemispherical protrusion 74c increases. The rotation of the adjusting knob 76 is stopped at a position where the desired center distance is provided.
On the other hand, in order to increase the center distance, the operating surface 75b of the adjusting member 75 is rotated around the bar 75d by turning the adjusting knob 76 in the direction in which the component of the urging force acts, and the hemisphere of the cam member 74 is rotated. The position of the operating surface 75b in contact with the protrusion 74c is changed. At this time, the outer surface 8c of the slide member 8 is moved from the inner peripheral surface 3a of the chamber 3 while moving the cam member to the right side in the drawing so that the axial thickness δ of the circular base body 75 at the position in contact with the hemispherical protrusion 74c decreases. The rotation of the adjusting knob 76 is stopped at a position where the desired center distance is given away.
[0050]
As described above, in order to obtain the center distance for giving a desired torque by the rotation of the rotating member, the position of the operating surface 75b of the adjusting member 75 that contacts the hemispherical protrusion 74c of the cam member 74 is continuously changed. The cam member 74 can be reliably moved by a predetermined distance along the drive shaft 4.
[0051]
As shown in FIG. 30, as an engagement method of the cam member 74 and the adjustment member 75, the wall surface 74 g of the cam member 74 is inclined with respect to the axial direction, contrary to the above example, and the adjustment member A hemispherical protrusion 75e may be provided on the 75 operation surfaces 75b. The wall surface 74g of the cam member 74 abuts on the hemispherical protrusion 75e provided on the operating surface 75b of the adjusting member 75 by the component force in the axial direction of the drive shaft 4 of the urging force by the tension spring means 9, 9. The cam member 74 is urged by the adjustment member 75.
[0052]
Furthermore, as shown in FIG. 31, the wall surface 74g of the cam member 74 may be perpendicular to the axial direction, and the end surface 75b of the bar 75d of the adjustment member 75 may be the operating surface. The cam member 74 is arranged such that the wall surface 74g of the cam member 74 abuts against the end surface 75b of the bar 75d of the adjusting member 75 due to the component force in the axial direction of the drive shaft 4 of the urging force by the tension spring means 9, 9. It is biased by the adjustment member 75. In this example, the screw hole 79 provided in the casing 2 and the screw part 75f provided on the outer peripheral surface of the bar 75d are screwed together, and the bar 75d is moved in and out along the screw hole 79 by the rotation of the adjustment knob 76. Thus, the cam member 74 is moved along the drive shaft 4.
[0053]
Further, the base 74a of the cam member 74 has a structure in which an urging force is applied so that a component force in the axial direction of the drive shaft 4 can be obtained from the end surface 8a1 of the sliding portion 8a of the slide member 8 on one side thereof. That's fine. Therefore, the entire outer surface on one side is not limited to the structure constituted by the conical surface 74f. For example, as shown in FIG. 32, the entire cam member 74 may be rectangular, and only the cam surface in contact with the end surface 8a1 of the sliding portion 8a of the slide member 8 may be the inclined surface 74f.
[0054]
Since the rotary damper 1 according to the first invention of the present invention described above is a bidirectional damper that generates a braking torque regardless of which direction the rotary member rotates, such a rotary damper is applied to a suspension door. In this case, as will be described in detail below, in order not to generate a braking torque when the door is opened, it is necessary to attach a pinion to the drive shaft protruding outward from the housing via a one-way clutch or the like.
[0055]
Next, the rotary damper according to the second aspect of the present invention will be described below, but only parts different from the rotary damper according to the first aspect of the present invention will be described.
First, a rotary damper according to a seventh configuration example will be described with reference to FIGS. 18 is an exploded perspective view of the rotary damper, FIG. 19 is an internal explanatory view, and FIG. 20 is a sectional view taken along the line CC in FIG. 21 and 22 are explanatory views showing a state in which the swinging member swings due to the rotation of the drive shaft. In addition, in each member of the rotary damper shown in FIGS. 18-22, the same code | symbol was attached | subjected to the same member as the rotary damper which concerns on 1st invention.
[0056]
The rotating member 5 includes a substantially oval base 6 that is pivotally supported by inserting the base end side 4a of the drive shaft 4 into the shaft hole 6a, a swinging member 40 that is swingably attached to the base 6, and a swinging member. It comprises spring means 41 interposed between the member 40 and the base portion 6.
[0057]
The swing member 40 includes a meniscus 40a and wall members 40b and 40b provided at both ends of the circumference and the bottom of the meniscus 40a. Side grooves 40d and 40d are formed at both ends of the bottom of each wall member 40b, and a hole 40c is formed at a substantially central portion of the meniscus 40a. The outer surface 40 b 2 of the wall member 40 b in the circumferential portion has a shape complementary to a part of the inner peripheral surface 3 a of the chamber 3.
Grooves 6f and 6f that are parallel to the surface 6e are formed over the entire oval circular portion of the base 6, and holes 6d and 6d are formed at substantially the center of each circular portion.
[0058]
Both ends of the wire spring 41 serving as the spring means are inserted into side grooves 40d and 40d formed in the bottom portion of each wall member 40b. As the spring means, a leaf spring may be used in addition to the wire spring. Each swinging member 40 to which the wire spring 41 is mounted in this way is attached to the base portion 6 by inserting the meniscus 40a portion into the groove 6f of the base portion 6 and passing the pins 42 through the holes 40c and 6d. . The central portion of the wire spring 41 is pressed outward in the radial direction of the chamber 3 by the upper surface of the convex support member 43 provided on the base 6. Each swinging member 40 attached in this way swings like a pendulum about the pin 42 by receiving a force of a certain level or more at the bottom portion of each wall member 40b.
[0059]
Similar to the rotary damper according to the first invention, such a rotary damper 1 fixes the housing 2 to the suspension door, and the other end 4b of the drive shaft 4 is parallel to the guide rail of the suspension door via a pinion or the like. Used by engaging the rack.
[0060]
When the suspension door is closed, the rotation operation of the suspension door is transmitted to the drive shaft 4 and the drive shaft 4 rotates. As shown in FIG. 21, when the drive shaft 4 rotates clockwise in the figure, the base portion 6 supported by the drive shaft 4 also rotates integrally with the drive shaft 4. At this time, the bottom portion 40b1 of the right wall member 40b of the swing member 40 and the right portion 40a1 from the center of the bottom portion of the meniscus 40a are subjected to the shear resistance force by the viscous fluid 10. When such a shear resistance is equal to or greater than the drag force of the wire spring 41, the state in which the both ends 43a and 43b of the upper surface of the support member 43 are supported as fulcrums is changed to the state of being supported by one end 43a of the upper surface of the support member 43 The fulcrum of the wire spring 41 moves, and as a result, the swinging member 40 swings counterclockwise in the figure around the pin 42.
[0061]
Such a shear resistance increases with the rotational speed of the drive shaft 4, but the swing member 40 does not swing when the shear resistance is smaller than the preset resistance of the wire spring 41. When the drive shaft 4 exceeds a certain rotational speed, and the shear resistance force by the viscous fluid 10 exceeds the drag force of the wire spring 41, the swing member 40 swings about the pin 42.
[0062]
FIG. 21 shows a state in which the shear resistance is equal to or greater than the set value. The swing member 40 swings counterclockwise around the pin 42 in the drawing, and the outer surface of the circumferential portion of the wall member 40b. 40b2 is close enough not to contact the inner peripheral surface 3a of the chamber 3. As a result, the clearance between the outer surface 40b2 of the circumferential portion of the wall member 40b and the inner peripheral surface 3a of the chamber 3 is narrowed, and the shear resistance force of the viscous fluid 10 existing in this clearance is increased, so that a high rotational torque is generated. A braking force acts on the movement of the suspension door or the like.
[0063]
As the rotational speed of the drive shaft 4 is attenuated by such high rotational torque, the shear resistance force due to the viscous fluid also decreases. When the shear resistance is equal to or less than the drag force of the wire spring 41, the wire spring 41 is supported by the return force from the one end 43a on the upper surface of the support member 43 as a fulcrum. As a result, the swinging member 40 swings clockwise around the pin 42 and returns to its original position.
When the swinging member 40 returns to the original position in this way, the gap between the outer surface 40b2 of the circumferential portion of the wall member 40b and the inner peripheral surface 3a of the chamber 3 also returns to the original state and becomes wider, and the rotational torque Is attenuated, and the braking force against the movement of the hanging door is also attenuated.
[0064]
As shown in FIG. 22, when the drive shaft 4 rotates counterclockwise in the figure as opposed to that shown in FIG. 21, the swinging member 40 swings clockwise around the pin 42 in the figure. The outer surface 40b2 of the circumferential part of the wall member 40b moves so close that it does not contact the inner peripheral surface 3a of the chamber 3. Thereafter, when the shear resistance is reduced, the swinging member 40 swings counterclockwise around the pin 42 by the restoring force of the wire spring 41 and returns to the original position.
[0065]
As described above, in the rotary damper according to the seventh configuration example, when the closing operation of the suspension door or the like to which the damper is attached temporarily increases, the shear resistance force due to the viscous fluid increases and the high rotational torque is increased. The braking force against the movement of the suspension door or the like immediately acts and can absorb the rapid motion sufficiently.
[0066]
Next, a rotary damper according to an eighth configuration example, which is a modification of the seventh configuration example, will be described with reference to FIG. In the rotary damper of this configuration example, the base 6 is disposed so as to extend from the shaft support portion by the drive shaft 4 only to one side in the radial direction of the chamber 3, and the swing member 40 is attached to the outer end of the base 6. Has a structure. That is, a single rocking member is used.
Compared to the seventh configuration example, when the swing member 40 swings, the area of the outer surface 40b2 of the wall member 40b adjacent to the inner peripheral surface 3a of the chamber 3 is halved, so that a large rotational torque is required. It is preferably used when not.
[0067]
Further, a rotary damper according to a ninth configuration example, which is a modification of the seventh configuration example, will be described with reference to FIG. Each swing member 40 used in the seventh configuration example is symmetrical with respect to a straight line passing through the shaft support portions of the pins 42 and 42, whereas each swing member 40 in this configuration example is the same straight line. On the other hand, it is composed of a portion located only on one side, and each swinging member 40 is disposed at a position symmetrical to the drive shaft 4.
In this rotary damper, when the drive shaft 4 rotates counterclockwise in the figure, a high rotational torque is generated, and a braking force acts on the closing operation of the hanging door, etc., and the drive shaft 4 rotates clockwise in the figure. In the case of rotation, since a high rotational torque cannot be obtained, it can be used as a unidirectional rotational damper.
[0068]
Next, an embodiment of a braking device for a sliding door that slides and opens according to the third invention of the present invention using the rotary damper described above will be described with reference to the accompanying drawings. Such a braking device for a sliding door has the rotary damper according to the first or second invention described above as a main component, and is used by being attached to a sliding door that is self-closing while sliding by its own weight. FIG. 10 is a sectional view of a rotary damper for hanging door braking, FIG. 11 is a front view showing an example in which such a braking device is applied to a hanging door, and FIG. 12 is a side view thereof.
[0069]
FIG. 10 shows an example in which the rotary damper 1 of the first configuration example according to the present invention shown in FIGS. Here, the end portion of the other end side 4b of the drive shaft 4 protruding outside from the housing 2 is pivotally supported by the shaft hole 20a of the one-way clutch 20, and the one-way clutch 20 is further supported by the shaft hole 21a of the pinion 21. It is pivotally supported. When the pinion 21 rotates in one direction, the one-way clutch 20 transmits the rotation operation of the pinion 21 to the rotating shaft 4 of the damper, and when the pinion 21 rotates in the other direction, the rotation operation of the pinion 21 is performed. It has a function of preventing transmission to the rotating shaft 4.
[0070]
As shown in FIGS. 11 and 12, a bracket 23 is attached to an arbitrary position on the upper part of the hanging door 22 that is self-closed while sliding by its own weight, and the damper 2 is fixed to the bracket 23 by attaching the housing 2 of the rotary damper 1 described above. To do.
Near the both ends of the upper part of the suspension door 22, traveling wheels 24 each having a recess 24 a along the circumferential direction are attached. Furthermore, a guide rail 25 having a ridge 25a at the top is stretched along the traveling portion of the suspension door 22. The traveling wheel 24 travels on the guide rail 25 as the recess 24 a of the traveling wheel 24 rotates on the ridge 25 a of the guide rail 25. The guide rail 25 is inclined downward along the side where the suspension door 22 is closed so that the suspension door 22 can be closed by its own weight.
[0071]
Between the guide rail 25 and the wall 26 to which the guide rail 25 is attached, a rack 27 that meshes with the pinion 21 is provided on a line that is substantially parallel to the vicinity of the end inclined downward of the guide rail 25.
[0072]
Next, the operation and the like of the suspension door braking device 19 configured as described above will be described.
FIG. 11 shows a state in which the suspension door 22 is opened. In this state, when the suspension door 22 is pushed in the direction (X) in which the guide rail 25 is inclined downward, the recess 24a of the traveling wheel 24 rotates on the ridge 25a of the guide rail 25 and travels on the guide rail 25. However, the suspension door 22 moves in the X direction by its own weight due to the inclination of the guide rail 25.
[0073]
When the suspension door 22 moves in this way and the pinion 21 starts to engage with the rack 27, the pinion 21 rotates in the clockwise direction in FIG. 11 while meshing with the rack 27. The one-way clutch (not shown) attached to the drive shaft 4 operates so as to transmit the rotation of the pinion 21 to the rotation shaft 4 of the damper when the pinion 21 rotates in this direction. During the meshing operation, the rotation operation of the pinion 21 is transmitted to the rotary shaft 4 of the damper.
[0074]
When the rotational movement of the pinion 21 is transmitted to the rotating shaft 4 of the damper, the torque adjusting body 7 is disposed at a predetermined angle with respect to the driving shaft 4 as shown in FIG. The rotating member 5 comprising the torque adjusting body 7, the pair of slide members 8, 8 and the tension spring 9 means rotates integrally. Since the torque adjuster 7 is disposed at a predetermined angle with respect to the drive shaft 4, there is a predetermined radial direction between the outer surfaces 8 c, 8 c of the pair of slide members 8, 8 and the inner peripheral surface 3 a of the chamber 3. A gap having an interval is formed.
Accordingly, since the rotational force is generated by the shearing force acting on the viscous fluid 10 existing in the gap by the rotation of the slide member 8, the torque generated by the rotation of the rotating member 5 is generated during the meshing operation of the pinion 21 and the rack 27. It can be generated as a braking force.
[0075]
The braking force thus generated acts on the meshing operation between the pinion 21 and the rack 27, and as a result, the braking force acts on the movement of the suspension door. Therefore, when the pinion 21 starts to mesh with the rack 27, the sliding momentum of the suspension door is reduced and the pinion 21 can be closed slowly.
[0076]
On the other hand, when the suspension door 22 is slid and opened from the closed state in this way, the suspension door 22 is moved to push up in the direction (Y) in which the guide rail 25 is inclined upward.
When the pinion 21 meshes with the rack 27 and rotates, the rotational motion of the pinion 21 is not transmitted to the rotary shaft 4 of the damper by the one-way clutch 20 attached to the drive shaft 4. On the other hand, braking force does not act. Therefore, it is possible to move the suspension door 22 in the Y direction only by the force that pushes the suspension door 22 in the Y direction against the force acting in the X direction based on the tilting weight of the suspension door 22.
[0077]
By the way, in the state where the suspension door 22 shown in FIG. 11 is opened, for example, when the suspension door 22 is accidentally pushed with a very large force in the X direction, the suspension door 22 suddenly slides in the X direction. The pinion 21 engages with the rack 27. At the initial stage of such engagement, a high load temporarily acts on the pinion 21 to rotate the pinion 21 at a high speed, and this rotation is transmitted to the rotating shaft 4 of the rotary damper 1.
[0078]
However, a large centrifugal force corresponding to the rotational speed of the drive shaft 4 acts on each slide member 8 of the rotary damper 1, but the tensile force of the tension spring 9 is set smaller than the centrifugal force based on such a sudden closing operation. Therefore, each slide member 8 is separated from the torque adjusting body 7 by a centrifugal force that resists and exceeds the tensile force of the tension spring 9. As a result, the radial distance formed between each outer surface 8c of each slide member 8 and the inner peripheral surface 3a of the chamber 3 can be temporarily further reduced to generate extremely high torque. Sufficient braking force can be obtained to absorb the temporary sudden closing operation.
[0079]
Instead of the rotary damper of the first configuration example, the rotary damper shown in the second to ninth configuration examples may be used. Also in the case of using these, the end of the other end side 4b of the drive shaft 4 protruding outward from the housing 2 is supported by the shaft hole of the clutch having the same function as the one-way clutch. The clutch is used while being pivotally supported in the shaft hole of the pinion. Even when such a rotary damper is used, the above-described operational effects can be obtained in the same manner.
An example using the rotary damper of the seventh configuration example is shown in FIG. The end of the other end 4b of the drive shaft 4 projecting outward from the housing 2 of the rotary damper 1 is pivotally supported by the shaft hole 20a of the one-way clutch 20, and the one-way clutch 20 is further pivoted on the shaft hole 21a of the pinion 21. It is intended to be used.
[0080]
In the brake device described above, the example in which the rotary damper is attached to the suspension door that slides in the opening / closing direction has been described. However, the present invention is not limited to such an example. For example, by using the rotary damper 1 according to the second configuration example, in FIG. 4, the end of the other end side 4 b of the drive shaft 4 protruding from the housing 2 to the outside is supported by the shaft hole 20 a of the one-way clutch 20. In addition, by adopting only the configuration in which the one-way clutch 20 is pivotally supported by the shaft hole 21a of the pinion 21, it can be applied to a rotary door, and a lid or door of various devices or apparatuses. is there. FIG. 13 is a cross-sectional view showing an example applied to a rotating lid of a device.
[0081]
In this example, the housing 2 of the rotary damper 1 is embedded and fixed in the outer frame 29 of the lid 28. A gear 31 that meshes with the pinion 21 is embedded and fixed in the rotation shaft 30 of the lid.
When the lid 28 rotates in the closing direction, the rotation operation of the gear 31 is transmitted to the drive shaft 4 of the rotary damper 1 through the pinion 21. As a result, rotation torque is generated by the rotation of the rotating member of the damper, and acts as a braking force against the rotation operation of the lid 28.
On the other hand, when the lid 28 rotates in the opening direction, transmission of the rotation operation of the gear 31 to the pinion 21 is prevented, so that no rotational torque is generated by the damper. Therefore, the lid 28 can be easily lifted and opened.
[0082]
Moreover, in the braking device using the suspension door that slides in the opening / closing direction, the suspension door is self-closed by providing a guide rail inclined downward on the side where the suspension door is closed. However, instead of such a self-closing mechanism, the suspension door may be closed by adopting a traction mechanism as shown in FIGS. 35 and 36, for example.
[0083]
In the example shown in FIG. 35, the rotary damper 1 and two traveling wheels 24, 24 are attached to the upper part of the suspension door 22 so as to sandwich the rotary damper 1. A guide rail 25 is stretched on the traveling portion of the suspension door 22, and traveling wheels 24, 24 travel on the guide rail 25.
A traction mechanism 85 in which a mainspring 84 is accommodated is attached to the wall 83 portion to which one end side of the guide rail 25 is attached. A wire 86 is stretched between the end of the upper part of the suspension door on the wall 83 side and the mainspring spring 84 of the pulling mechanism 85.
When the suspension door 22 is pushed in the X direction, the mainspring 84 is wound up and the wire 86 is also drawn into the traction mechanism, so that the suspension door 22 moves in the X direction and is closed. The suspension door 22 is opened by pulling the suspension door 22 in the Y direction against the tension of the spring spring 84.
[0084]
Next, in the example shown in FIG. 36, a traction mechanism 89 including a pulley 87 and a weight 88 is used instead of the traction mechanism 85 in FIG. A wire 86 is stretched through a pulley 87 between an end of the upper part of the suspension door on the wall 83 side and a weight 88 of the traction mechanism 89.
When the suspension door 22 is pushed in the X direction, the suspension door 22 is moved in the X direction and closed by the pressing force acting on the suspension door 22. The suspension door 22 is opened by pulling the suspension door 22 in the Y direction against the weight of the weight.
[0085]
When the sliding door braking device according to the third invention of the present invention is configured as described above, when closing the suspension door, the suspension door can be closed by a desired braking force generated by the damper, In addition, when opening the suspension door, the suspension door can be opened without receiving a braking force.
[0086]
In addition, since the sliding member of the rotary damper is slid in the radial direction, the generated torque is changed by adjusting the radial distance formed between the outer surface and the inner peripheral surface of the chamber. Since there is no particular limitation on the axial length, the length can be shortened. The damper body is arranged between the wall and the guide rail so that its axial direction coincides with the direction substantially perpendicular to them, so that the distance between the wall and the guide rail can be reduced and braking is performed. The device can be made compact.
[0087]
Furthermore, as described above, even when a high load is temporarily applied to the suspension door and the rotational speed of the drive shaft increases rapidly, the generated centrifugal force is set smaller than the tensile force of the spring means. There is an advantage that a braking force that absorbs such a temporary high load can be applied.
[0088]
【The invention's effect】
The rotary damper according to the present invention includes a housing having a chamber therein, a drive shaft having a base end accommodated in the chamber, and a rotating member supported by the drive shaft and accommodated in the chamber. And a viscous damper filled in the chamber, and a rotary damper that generates torque by the rotation of the rotating member,
A base portion that is rotatably supported integrally with the drive shaft; a torque adjusting body that has a fixed relationship with the drive shaft and is relatively movable by the action of an external force of a certain level; and a radial direction And a slide member having an outer surface complementary to a part of the inner peripheral surface of the chamber, and spring means for biasing the slide member against the torque adjusting body,
By moving the torque adjusting body relative to the drive shaft, the slide member is slid in the radial direction along the base, and the radial direction between the outer surface of the slide member and the inner peripheral surface of the chamber The rotational torque of the rotating member is changed by changing the interval.
[0089]
By sliding the slide member in the radial direction, the radial interval formed between the outer surface of the slide member and the inner peripheral surface of the chamber is adjusted, and the shear resistance force according to the interval of the viscous fluid existing in the gap is adjusted. Based on this, the torque generated can be obtained. Accordingly, since the generated torque can be changed depending on the radial interval, the axial length of the damper body can be shortened, so that the damper must be mounted in a place where the axial length is narrow. Even in such cases, it is possible to mount the damper.
[0090]
According to a second aspect of the present invention, the torque adjustment body includes an adjustment ring that is attached to the base of the rotating member so as to be integrally rotatable, and a cam member that is attached to the outer periphery of the adjustment ring. The inner periphery of the central hole of the cam member is engaged by a concave portion formed on one side and a convex portion formed on the other side, and when the concave portion and the convex portion are subjected to a certain external force on the cam member, The cam member is configured to allow relative rotation with respect to the adjustment ring and the drive shaft by a predetermined angle.
Since the outer periphery of the adjustment ring and the inner periphery of the central hole of the cam member are engaged by the concave portion and the convex portion, the torque adjusting body can be reliably arranged at a predetermined angle with respect to the drive shaft.
[0091]
According to a third aspect of the present invention, the outer circumference of the cam member of the torque adjusting body is made elliptical, whereby the distance from the center of the cam member of each contact portion between the pair of slide members and the cam member can be continuously displaced. it can. Accordingly, since the generated torque obtained can be continuously changed, a desired braking force can be selected and obtained according to a door, a lid, or the like to which the damper is attached.
[0092]
According to a fourth aspect of the present invention, the torque adjusting body is provided with an operating portion for rotating the torque adjusting body at a predetermined angle relative to the drive shaft on an axial protrusion protruding from the housing of the cam member. The body can be easily rotated to the position of the predetermined angle. As such an operating part, for example, a groove that can be engaged with the tip of the driver at the outer end of the cam member, a knob that can be operated with a finger, or the like is used.
[0093]
According to a fifth aspect of the present invention, the torque adjuster includes a cam member attached to the base of the rotating member so as to be integrally rotatable and axially movable, and an adjusting member engaged with the cam member. A cam surface having an inclined surface on the outer periphery, a connecting portion connected to the rotating member on one side in the axial direction, and a wall portion formed at the other end in the axial direction, An operating surface that engages the wall of the cam member at the end, and when an external force of a certain level or more acts on the adjustment member, the cam surface of the cam member of the operating surface The position of the portion engaged with the wall portion is moved in the axial direction, so that the cam member is allowed to move along the drive shaft.
In order to obtain a predetermined radial distance between the outer surface of the slide member and the inner peripheral surface of the chamber in order to generate a desired torque by the rotation of the rotating member, the cam inclined surface in contact with the operating surface of the adjusting member By continuously changing the position, the cam member can be reliably moved by a predetermined distance along the drive shaft.
[0094]
According to a sixth aspect of the present invention, the adjustment member has an outer end protruding from the housing, and an operating portion for moving the cam member along the drive shaft is provided at the outer end.
With such an operating part, the cam member can be easily moved to a predetermined position along the drive shaft. Such an operating part can be operated with a groove or a finger that can be engaged with the tip of the driver, for example. A knob is used.
[0095]
According to a seventh aspect of the present invention, the biasing force of the spring means is a predetermined centrifugal force that acts on the slide member by the rotation of a rotary damper. It was made to become smaller than the centrifugal force generated when the rotational speed increased rapidly.
[0096]
Since the centrifugal force acting on the slide member at the time of such high load is set to exceed the biasing force of the spring means, the torque that the slide member is in contact with against the biasing force of the spring means by this centrifugal force The adjustment bodies are separated from each other. Therefore, the radial gap formed between the outer surface of the slide member and the inner peripheral surface of the chamber can be temporarily reduced, and extremely high torque can be temporarily generated accordingly. Since the temporary high load can be absorbed by the high torque thus obtained, a sufficient braking force can be applied to the abrupt closing operation of a suspension door or the like to which a damper is attached.
[0097]
Further, when the rotational speed of the drive shaft returns to the original low rotational speed, the centrifugal force is reduced below the tensile force of the spring means, so the slide member is urged again so as to come into contact with the torque adjusting body by the tensile force of the spring means. Then, it returns to the state where the desired set torque can be generated.
[0098]
According to the eighth aspect of the present invention, since the slide member is composed of a pair of members respectively arranged on both sides of the chamber in the radial direction of the chamber, the total outer surface of the slide member facing the inner peripheral surface of the chamber A large generated torque can be obtained by increasing the area. The rotary damper having such a configuration is suitable for use by being attached to a relatively heavy hanging door or the like.
In claim 9, since the slide member is made of a single member arranged on one side of the torque adjuster in the radial direction of the chamber, the total area of the outer surface of the slide member facing the inner peripheral surface of the chamber The generated torque can be reduced by reducing the. Such a rotary damper is preferably used for a relatively light weight hanging door or the like.
[0099]
The rotary damper according to a second aspect of the present invention is the rotary damper according to claim 10, wherein the housing is provided with a chamber therein, the drive shaft having a base end accommodated in the chamber, and supported by the drive shaft and accommodated in the chamber. A rotating damper that includes a rotating member and a viscous fluid filled in the chamber, and generates torque by rotation of the rotating member.
The rotating member has a base that is pivotally supported by the drive shaft so as to rotate integrally therewith, and a swinging member that is swingably attached to the base and has an outer surface that is complementary to a part of the inner peripheral surface of the chamber. And a spring means interposed between the swinging member and the base, and allowing the swinging member to swing when a force of a certain level or more is applied to the swinging member,
Torque is generated by narrowing the gap between the outer surface of the swinging member and the inner peripheral surface of the chamber by swinging the swinging member with respect to the base by the force above a certain level generated by the rotation of the drive shaft. It was made to let it be made to do.
[0100]
When the shear resistance force of the viscous fluid generated by the rotation of the drive shaft exceeds the drag force of the spring means, a rotational torque due to the swinging of the swinging member is obtained. Since a high torque can be obtained immediately when the rotational speed of the drive shaft temporarily increases, the braking force immediately acts even when the door closes suddenly such as a hanging door with a rotary damper attached. Temporary high loads due to sudden movement can be easily absorbed.
Further, after the high torque is obtained, the shear resistance force due to the viscous fluid decreases as the rotational speed of the drive shaft decreases. As a result, the torque is attenuated while the swinging member returns to the original position by the restoring force of the spring means. Therefore, it is possible to immediately return to the original normal closing operation after the braking force is applied to the abrupt closing operation of the hanging door or the like.
[0101]
According to another aspect of the present invention, the base portion is extended from the shaft support portion by the drive shaft to both sides in the radial direction, and the swinging member is composed of a pair of members respectively attached to both ends of the base portion. As a result, the total area of the outer surface of the swinging member adjacent to the inner peripheral surface of the chamber can be increased to obtain a large generated torque. Therefore, such a rotary damper is preferably used for a relatively heavy suspension door or the like.
According to a twelfth aspect of the present invention, the base portion is extended to one side in the radial direction from a shaft support portion by the drive shaft, and the swing member is made of a single member attached to the outer end of the base portion. As a result, the total area of the outer surface of the swinging member adjacent to the inner peripheral surface of the chamber can be reduced and the generated torque can be reduced. Therefore, such a rotary damper is preferably used for a relatively light weight hanging door or the like. .
In this manner, a rotary damper using a pair or a single swing member can be selected according to the weight of a hanging door or the like to which the rotary damper is attached.
[Brief description of the drawings]
FIG. 1 is an exploded perspective view of a rotary damper according to a first configuration example of the present invention.
FIG. 2 is a right side view of the rotary damper.
FIG. 3 is an internal explanatory view with a lid removed in FIG. 2;
4 is a cross-sectional view taken along the line AA in FIG. 3;
FIG. 5 is an exploded perspective view of a rotary damper according to a second configuration example of the present invention.
FIG. 6 is a right side view of the rotary damper.
7 is an internal explanatory view with the lid removed in FIG. 6. FIG.
8 is a cross-sectional view taken along the line BB in FIG.
FIG. 9 is a cross-sectional view of a rotary damper according to a third configuration example of the present invention.
FIG. 10 is a cross-sectional view of a rotary damper according to a first configuration example used for hanging door braking.
FIG. 11 is a front view showing an example in which the hanging door braking device according to the present invention is applied to opening and closing of a hanging door.
FIG. 12 is a side view showing an example in which the hanging door braking device according to the present invention is applied to the opening and closing of the hanging door.
FIG. 13 is a cross-sectional view showing an example in which the braking device according to the present invention is applied to a rotary lid.
FIG. 14 is a cross-sectional view showing a conventional liquid frictional resistance damper device for a door closer.
FIG. 15 is a side view showing a state in which a conventional liquid friction resistance damper device for a door closer is applied to a sliding door.
FIG. 16 is an internal explanatory view of a rotary damper according to a fourth configuration example of the present invention.
FIG. 17 is an explanatory diagram of the inside of a rotary damper according to a fifth configuration example of the present invention.
FIG. 18 is an exploded perspective view of a rotary damper according to a seventh configuration example of the present invention.
FIG. 19 is an explanatory diagram of the inside of the rotary damper.
20 is a cross-sectional view taken along the line CC of FIG.
FIG. 21 is an explanatory diagram showing a state in which the swing member swings due to the rotation of the drive shaft in the rotary damper.
FIG. 22 is an explanatory diagram showing a state in which the swing member swings due to the rotation of the drive shaft in the rotary damper.
FIG. 23 is an internal explanatory view of a rotary damper according to an eighth configuration example of the present invention.
FIG. 24 is an exploded perspective view of a rotary damper according to a ninth configuration example of the present invention.
FIG. 25 is a sectional view of a rotary damper according to a seventh configuration example used for hanging door braking.
FIG. 26 is a perspective view showing a cam member of a torque adjuster used in a rotary damper according to a sixth configuration example of the present invention.
FIG. 27 is a perspective view showing an adjustment member of a torque adjustment body used in a rotary damper according to a sixth configuration example of the present invention.
FIG. 28 is a cross-sectional view of a rotary damper according to a sixth configuration example of the present invention in a state where maximum torque is generated.
FIG. 29 is a cross-sectional view of a rotary damper according to a sixth configuration example of the present invention in a state where a minimum torque is generated.
FIG. 30 is a cross-sectional view showing a modified example of the torque adjuster used in the rotary damper according to the sixth configuration example of the present invention.
FIG. 31 is a cross-sectional view showing a modified example of the torque adjuster used in the rotary damper according to the sixth configuration example of the present invention.
FIG. 32 is a perspective view showing a modified example of the cam member of the torque adjustment body used in the rotary damper according to the sixth configuration example of the present invention.
FIG. 33 is a perspective view showing a modified example of the operating portion of the torque adjuster.
FIG. 34 is a perspective view showing a modified example of the operating portion of the torque adjuster.
FIG. 35 is a side view showing an example in which the suspension device for a hanging door according to the present invention is applied to opening and closing of a hanging door.
FIG. 36 is a side view showing an example in which the hanging door braking device according to the present invention is applied to the opening and closing of the hanging door.
[Explanation of symbols]
Rotating damper, 2 housing, 3 chamber, 3a, inner peripheral surface, 4 drive shaft, 4a, base end side, 5 rotating member, 6 base Torque adjustment body, 71 ... Adjusting ring, 71b ... Projection, 72, 74 ... Cam member, 72a ... Projection, 72b ... Recess, 73, 72d, 76 ... Actuation part, 74c ... Projection, 74d 74e..Connecting portion, 74f..Cam surface, 74g..Wall portion, 75..Adjustment member, 75b..Operating surface, 8..Sliding member, 8c..Outer surface, 9, 41..Spring means, 10 .... Viscous fluid, 19 .... Brake device for suspension door, 20 .... One-way clutch, 21 ... Pinion, 22 .... Suspension door, 24 ... Running wheel, 25 Guide rail, 27 ... Rack, 40 ...・ Oscillating member.

Claims (7)

内部に室を備えたハウジングと、該室内に基端側が収容された駆動軸と、該駆動軸に軸支されて前記室内に収容された回転部材と、前記室内に充填された粘性流体とを備え、前記回転部材の回転により生ずる該回転部材と前記室の内周面との間の粘性流体の剪断抵抗力によりトルクを発生する回転ダンパにおいて、
前記回転部材が、前記駆動軸と一体回転自在に軸支された基部と、該基部上に設けられ、該基部に対して固定関係を持ちつつ、一定以上の外部力の作用により前記基部に対して相対回転可能なトルク調整体と、前記トルク調整体を介して対向する位置に径方向に移動可能に配置され、前記室の内周面の一部と相補的な外面を有する一対のスライド部材と、該一対のスライド部材間において前記トルク調整体を介して対向する位置に配置され、各スライド部材を前記トルク調整体に対して付勢する各スライド部材に共通の一対のバネ手段とを備え、
前記駆動軸に対して前記トルク調整体を相対移動させることにより、前記スライド部材を前記基部に沿って径方向にスライドさせて該スライド部材の外面と前記室の内周面との間の径方向の間隔を変化させ、これによって前記回転部材の回転トルクを変化させるようにしたことを特徴とする回転ダンパ。A housing having a chamber therein, a drive shaft having a proximal end accommodated in the chamber, a rotating member supported by the drive shaft and accommodated in the chamber, and a viscous fluid filled in the chamber; A rotary damper that generates torque by the shear resistance force of the viscous fluid between the rotating member and the inner peripheral surface of the chamber generated by the rotation of the rotating member ;
The rotating member is pivotally supported by the drive shaft so as to rotate together with the drive shaft, and is provided on the base. The rotating member has a fixed relationship with the base, and is applied to the base by an action of a certain external force. relative rotatable torque adjustment member Te, through said torque adjusting member movably disposed radially at opposing pair of slide members having complementary outer surface part of the inner peripheral surface of the chamber When, it is disposed in a position facing via the torque adjustment member between the pair of slide members, and a common pair of spring means in each slide member for biasing each slide member relative to the torque adjustor ,
By moving the torque adjusting body relative to the drive shaft, the slide member is slid in the radial direction along the base, and the radial direction between the outer surface of the slide member and the inner peripheral surface of the chamber The rotation damper is characterized in that the rotation torque of the rotation member is changed by changing the interval of the rotation. 前記トルク調整体が、前記回転部材の基部に一体回転自在に取付けられた調整リングと、該調整リングの外周に取付けられたカム部材とからなり、前記調整リングの外周と前記カム部材の中央孔の内周とは、一方に形成された凹部と他方に形成された凸部とにより係合し、該凹部と凸部は、一定以上の外部力が前記カム部材に作用すると、前記カム部材が前記調整リング及び前記駆動軸に対し所定角度相対回動することを許容するように構成されている、請求項１に記載の回転ダンパ。  The torque adjustment body includes an adjustment ring attached to the base of the rotating member so as to be integrally rotatable, and a cam member attached to the outer periphery of the adjusting ring, and the outer periphery of the adjusting ring and the central hole of the cam member Is engaged with a concave portion formed on one side and a convex portion formed on the other side, and when the external force of a certain level or more acts on the cam member, the cam member The rotary damper according to claim 1, wherein the rotary damper is configured to allow relative rotation with respect to the adjustment ring and the drive shaft by a predetermined angle. 前記カム部材は楕円形の外周を有する、請求項２に記載の回転ダンパ。  The rotary damper according to claim 2, wherein the cam member has an elliptical outer periphery. 前記カム部材は前記ハウジング外に突出した軸方向突起部を有し、前記トルク調整体を前記駆動軸に対して所定角度相対回動させるための作動部を前記突起部の先端に設けた、請求項２又は請求項３に記載の回転ダンパ。  The cam member has an axial protrusion protruding out of the housing, and an operating portion for rotating the torque adjusting body by a predetermined angle relative to the drive shaft is provided at a tip of the protrusion. The rotary damper according to claim 2 or claim 3. 前記トルク調整体が、前記回転部材の基部に一体回転自在かつ軸方向移動自在に取付けられたカム部材と、該カム部材と係合する調整部材とからなり、前記カム部材は、外周に傾斜面からなるカム面と、軸方向一側に前記回転部材に連結された連結部と、軸方向他端に形成された壁部とを有し、前記調整部材は、軸方向内端部に前記カム部材の壁部と係合する作動面を有し、前記カム面と作動面とは、一定以上の外部力が前記調整部材に作用すると、前記作動面の前記カム部材の前記壁部と係合する部位の位置が軸方向に移動し、もって前記カム部材が前記駆動軸に沿って移動することを許容するように構成されている、請求項１に記載の回転ダンパ。  The torque adjusting body includes a cam member attached to a base portion of the rotating member so as to be integrally rotatable and axially movable, and an adjusting member engaged with the cam member, and the cam member is inclined on an outer periphery. A connecting portion connected to the rotating member on one side in the axial direction, and a wall portion formed at the other end in the axial direction, and the adjusting member has the cam at the inner end in the axial direction. An operating surface that engages with a wall portion of the member, and the cam surface and the operating surface engage with the wall portion of the cam member of the operating surface when a certain external force acts on the adjusting member. 2. The rotary damper according to claim 1, wherein the position of the part to be moved is moved in the axial direction, so that the cam member is allowed to move along the drive shaft. 前記調整部材は前記ハウジング外に突出した外端部を有し、前記カム部材を前記駆動軸に沿って移動させるための作動部を前記調整部材の前記外端部に設けた、請求項５に記載の回転ダンパ。  6. The adjustment member according to claim 5, wherein the adjustment member has an outer end protruding outside the housing, and an operating portion for moving the cam member along the drive shaft is provided at the outer end of the adjustment member. The described rotary damper. 前記バネ手段の付勢力を、回転ダンパの回転によって前記スライド部材に作用する所定の遠心力より小さくした、請求項１〜請求項６のいずれか一項に記載の回転ダンパ。  The rotary damper according to any one of claims 1 to 6, wherein an urging force of the spring means is made smaller than a predetermined centrifugal force acting on the slide member by rotation of the rotary damper.
JP2000317458A 1999-10-19 2000-10-18 Rotating damper Expired - Fee Related JP4529059B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2000317458A JP4529059B2 (en) 1999-10-19 2000-10-18 Rotating damper
DE10122077A DE10122077A1 (en) 2000-10-18 2001-05-07 rotary damper
US09/852,886 US6729448B2 (en) 2000-10-18 2001-05-10 Rotary damper

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP11-296893 1999-10-19
JP29689399 1999-10-19
JP2000317458A JP4529059B2 (en) 1999-10-19 2000-10-18 Rotating damper

Related Child Applications (1)

Application Number Title Priority Date Filing Date
JP2000346783A Division JP2001193347A (en) 1999-10-19 2000-11-14 Rotary damper, overhang door braking device using rotary damper and overhang door provided with braking device

Publications (2)

Publication Number Publication Date
JP2001187934A JP2001187934A (en) 2001-07-10
JP4529059B2 true JP4529059B2 (en) 2010-08-25

Family

ID=26560891

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2000317458A Expired - Fee Related JP4529059B2 (en) 1999-10-19 2000-10-18 Rotating damper

Country Status (1)

Country Link
JP (1) JP4529059B2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020135375A1 (en) * 2018-12-27 2020-07-02 青岛海尔洗衣机有限公司 Upper cover damper of washing machine, and washing machine

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4278143B2 (en) 2003-09-12 2009-06-10 株式会社ニフコ Rotating damper
JP4601503B2 (en) * 2005-07-08 2010-12-22 株式会社ムラコシ精工 Shock absorber, switchgear
JP4709096B2 (en) * 2006-08-07 2011-06-22 不二ラテックス株式会社 Rotating damper device
AU2012302795A1 (en) * 2011-08-31 2014-04-17 Sugatsune Kogyo Co., Ltd. Rotary damper and hinge device with damper
WO2013031250A1 (en) 2011-08-31 2013-03-07 スガツネ工業株式会社 Hinge device
KR101544302B1 (en) 2011-08-31 2015-08-21 스가쓰네 고우교 가부시키가이샤 Hinge device with damper
US9657790B2 (en) * 2015-01-14 2017-05-23 Nelson Irrigation Corporation Viscous rotational speed control device
KR101976281B1 (en) * 2017-11-20 2019-08-28 유순기 Gear system assembled orifice viscosity damper having free-zone

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5459572A (en) * 1977-10-20 1979-05-14 Tokico Ltd Hydraulic shock absorber
JPS62113926A (en) * 1985-11-12 1987-05-25 Mitsubishi Heavy Ind Ltd Hydraulic braking device
JPH0712166A (en) * 1993-06-24 1995-01-17 Kitagawa Ind Co Ltd Hydraulic damper
JP4026192B2 (en) * 1997-03-26 2007-12-26 オイレス工業株式会社 Variable damping force damper
US5851165A (en) * 1998-06-03 1998-12-22 Wei; Mike Wheel-type resistance device for a bicycle exerciser

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020135375A1 (en) * 2018-12-27 2020-07-02 青岛海尔洗衣机有限公司 Upper cover damper of washing machine, and washing machine

Also Published As

Publication number Publication date
JP2001187934A (en) 2001-07-10

Similar Documents

Publication Publication Date Title
US6729448B2 (en) Rotary damper
JP5475883B2 (en) Tensioner
JP4529059B2 (en) Rotating damper
JPH0581709B2 (en)
KR20110086688A (en) Retaining clip for an actuator of a furniture flap
JP2006232262A (en) Hinge device of console lid, and console having the same
JP2015105490A (en) Resistance generating device
US5135083A (en) Input responsive damper
JP3410386B2 (en) Retarder device
JP2003514703A (en) Drive mechanism of seat height adjustment device for vehicle seat
JP2008038417A (en) Braking device for opening part closing member and opening part closing member having it
JP2001193347A (en) Rotary damper, overhang door braking device using rotary damper and overhang door provided with braking device
JPH0814304B2 (en) Speed governor such as toilet bowl
JPH0740625Y2 (en) Overload prevention door closer
JP2005299312A (en) Spring unit with damper and opening/closing device
JPH02164993A (en) Closer for sliding door
JP4453499B2 (en) Vehicle door opening / closing position holding device
JP2006311964A (en) Opening/closing assisting device and furniture
JP4424150B2 (en) Damper for automobile seat and automobile seat equipped with this damper
JP2004189009A (en) Opening and closing mechanism of trunk lid
JPH01295989A (en) Vertically opening or closing door
JPH07116084A (en) Speed governing device for toilet stool or the like
JPH0450390Y2 (en)
JPH0536053Y2 (en)
JP2003093789A (en) Inner lid locking device for spin-drying tub

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20071012

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20071121

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20091112

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20091208

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20100205

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20100427

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20100526

R150 Certificate of patent or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130618

Year of fee payment: 3

LAPS Cancellation because of no payment of annual fees