JP4660000B2

JP4660000B2 - Rotating damper

Info

Publication number: JP4660000B2
Application number: JP2001104389A
Authority: JP
Inventors: 信寿織田
Original assignee: TOK Bearing Co Ltd
Current assignee: TOK Bearing Co Ltd
Priority date: 2001-04-03
Filing date: 2001-04-03
Publication date: 2011-03-30
Anticipated expiration: 2021-04-03
Also published as: JP2002295561A

Description

【０００１】
【発明の属する技術分野】
本発明は、例えば蓋、扉等の開閉に際してこれに制動力を与える回転ダンパに関する。
【０００２】
【従来の技術】
図２２に示すような従来の回転ダンパは、流体が充填される流体室を有するケーシングと、前記流体室内に収納される基部と該流体室外に突出する軸部とから成り前記ケーシングに対して相対回転自在な回転部材と、前記ケーシングに設けられ前記流体室内での前記回転部材の回転角度を限定するストッパ壁と、前記回転部材の相対回転時に前記ストッパ壁と協働してトルクを発生させるための、回転部材の基部に設けられた羽根とを有する。
【０００３】
上記従来の回転ダンパのうち、図２２(１)に示すような特開平１１−１８２６０７号公報で提案された回転ダンパの場合、回転部材が反時計方向及び時計方向のいずれの方向に回転する時にも、即ち開扉・閉扉のいずれにおいても、前記羽根の回転ストロークの終端領域で高トルクが発生するようにしている。また、図２２(２)及び(３)に示すような米国特許第４６５３１４１号明細書及び特開昭５８−５０３４２号公報で提案された回転ダンパの場合、両方向への回転ストロークの終端領域だけでなく始端領域でも高トルクが発生するようにしている。しかし、従来の回転ダンパでは、開扉時と閉扉時に発生する最大トルクの大きさを同一とせざるを得なかった。
【０００４】
上記従来の回転ダンパの場合でも、反時計方向及び時計方向のいずれかの回転方向へ回転する時にのみ有効に作用する溝をケーシングの内周面や回転部材の基部の外周面の周方向に適当な長さと、幅及び深さで形成することにより、反時計方向回転時に発生する最大トルクと時計方向回転時に発生する最大トルクとを相異なるものにすることは可能である。しかし、この方法では、前記溝の幅と深さの僅かな違いによりトルクが大きく変化してしまい、設計した最大トルクが大きく変わる恐れがある。そのため、両方向回転時に必要とする所望の最大トルクを得るためには、極めて精度の高い溝の加工が必要であり、加工コストの増大を招く。
【０００５】
反時計方向回転時に発生する最大トルクと時計方向回転時に発生する最大トルクとを相異るものにする必要がある場合には、幅又は深さが相異なる溝を備えた２種類の回転ダンパを併用することも考えられる。しかし、各回転ダンパはケーシング、回転部材、ストッパ壁、トルク発生手段等を備えているので、ダンパ装置の全体も必然的に大型化せざるを得ず、しかも高価になるという欠点があった。
【０００６】
また、前記単一の回転ダンパを用いたときはいずれの場合も、反時計方向回転時の最大トルクの発生領域と時計方向回転時の最大トルクの発生領域は、前記羽根の回転ストロークのほぼ同一角度範囲に存在する。即ち、図２２(１)に示す従来の回転ダンパでは、反時計方向回転時に発生するトルクの大きさは、前記羽根の回転ストロークの始端領域から終端領域に亘って低⇒低⇒高と変化し、一方、時計方向回転時に発生するトルクの大きさも、同様に低⇒低⇒高と変化する。また、図２２(２)及(３)に示す従来の回転ダンパでは、反時計方向回転時に発生するトルクの大きさは高⇒低⇒高と変化し、一方、時計方向回転時に発生するトルクの大きさも、同様に高⇒低⇒高と変化する。
【０００７】
また、前述したような高精度の溝加工を施した場合でも、反時計方向回転時のトルクの大きさを中⇒低⇒高に設計すれば、時計方向回転時のトルクの大きさは高⇒低⇒中とせざるを得ないため、設計の自由が大きく制限される。従って、上記の従来の回転ダンパでは、反時計方向回転時の最大トルクの発生領域と時計方向回転時の最大トルクの発生領域を夫々独立して自由に変えて設計することはできなかった。
【０００８】
【発明が解決しようとする課題】
上述したように、従来の回転ダンパは、反時計方向回転時と時計方向回転時に発生するトルクの大きさとそのトルク発生領域を自在に相異ならしめることができなかったために用途に制約があった。例えば、トイレの便座用便蓋や複写機の蓋等に使用する場合には、閉方向の終端領域、即ち該蓋の閉まる直前では、閉鎖時の衝撃を吸収するために、高トルクでブレーキをかける必要があり、一方、開方向の終端領域、即ち該蓋の最大の開状態では、あまり大きな制動力がかかると、完全に開状態にならないうちに手を離してしまう恐れがあるので、中程度のダンパ力が適当である。そのため、従来の回転ダンパはこのような用途には適切に対処できなかった。
【０００９】
また、自動販売機等の商品取り出し用蓋の場合は、該蓋の開方向の終端領域、即ち該蓋の最大の開状態で蓋が落下しない程度のトルクで十分である。一方、缶コーヒーやカップ等を慌てずに余裕を持って取り出せるようにするためには、該蓋が落下する初期の段階で高トルクを作用させて、蓋がゆっくりと閉まるように設計されているのが良い。そして、該蓋が閉鎖する途中は、ほとんど制動力は必要ではなく、低トルクで速やかに閉まれば良い。完全に閉鎖する直前は、衝撃的に閉鎖するのを防止するために、ある程度の制動力を持って閉まる必要がある。しかも、完全に閉鎖する直前の該蓋はほぼ最下方を向いている状態にありで、高トルクでブレーキをかけると該蓋が閉鎖の直前で止まってしまう恐れがあるため、完全に閉鎖する直前のトルクは小さくて良い。しかしながら、該蓋が閉鎖状態のときは、閉まった状態で風等による蓋のばたつきを防止するために、中程度のトルクが必要である。従って、従来の回転ダンパを開方向時と閉方向時に発生するトルクの大きさとその発生領域とが相異なるようにすることが望ましい上記のような蓋に使用することも適切ではない。
【００１０】
【課題を解決するための手段】
上記課題を解決するため、本発明の回転ダンパは、流体が充填される流体室を有するケーシングと、前記流体室内に収納される基部と該流体室外に突出する軸部とから成り前記ケーシングに対して相対回転自在な回転部材と、前記ケーシングに設けられ前記流体室内での前記回転部材の回転角度を限定するストッパ壁と、前記回転部材の相対回転時に前記ストッパ壁と協働してトルクを発生させるトルク発生手段とを有する回転ダンパにおいて、前記ケーシングは前記流体室を第１室と第２室とに区画する仕切り壁を備え、前記回転部材は、前記第１室に位置する第１基部と前記第２室に位置する第２基部とを一体回転するように有し、該第１基部は該回転部材の第１方向への回転時に前記第１室においてトルクを発生する第１トルク発生手段を備え、該第２基部は同回転部材の第２方向への回転時に前記第２室においてトルクを発生する第２トルク発生手段を備えるようにした。
【００１１】
従来の回転ダンパのケーシング室を仕切り壁により２室に区画した構造なので、ダンパ装置は小型にでき、しかも安価である。
【００１２】
また、前記回転部材は、前記第１室に位置する第１基部と前記第２室に位置する第２基部とを一体回転するように有し、該第１基部は該回転部材の第１方向への回転時に前記第１室においてトルクを発生する第１トルク発生手段を備え、該第２基部は同回転部材の第２方向への回転時に前記第２室においてトルクを発生する第２トルク発生手段を備えるようにしたので、回転部材の反時計方向回転時と時計方向回転時のそれぞれにおいて必要とする所望の最大トルクをそれぞれの室で相互に独立して得ることができる。
【００１３】
請求項２では、前記第１室と前記第２室は容積がほぼ等しくなるように形成したので、回転部材の第１方向への回転時に第１室において第１トルク発生手段により発生する最大トルクと、第２方向への回転時に第２室において第２トルク発生手段により発生する最大トルクを容易にほぼ等しくすることができる。
【００１４】
請求項３では、前記回転部材の第１トルク発生手段は、前記第１室において前記第１基部の外周面に軸方向に沿って前記第１室の前記ケーシング内周面まで突出するように形成された少なくとも１つの第１羽根から成り、該第１羽根は前記回転部材の前記第１方向への回転時に前記第１室内の流体の抵抗を受ける第１受圧面を有し、前記第２トルク発生手段は、前記第２室において前記第２基部の外周面に軸方向に沿って前記第２室の前記ケーシング内周面まで突出するように形成された少なくとも１つの第２羽根から成り、該第２羽根は前記回転部材の前記第２方向への回転時に前記第２室内の流体の抵抗を受ける第２受圧面を有し、前記第１受圧面の面積と前記第２受圧面の面積をほぼ等しくした。これにより、回転部材の第１方向への回転時に第１室において第１トルク発生手段により発生する最大トルクと、第２方向への回転時に第２室において第２トルク発生手段により発生する最大トルクを容易にほぼ等しくすることができる。
【００１５】
請求項４では、前記第１室と前記第２室は容積が相異なるように形成したので、回転部材の第１方向への回転時に第１室において第１トルク発生手段により発生する最大トルクと、第２方向への回転時に第２室において前記第２トルク発生手段により発生する最大トルクを容易に相異なるようにすることができる。。
【００１６】
請求項５では、前記回転部材の前記第１トルク発生手段は、前記第１室において前記第１基部の外周面に軸方向に沿って前記第１室の前記ケーシング内周面まで突出するように形成された少なくとも１つの第１羽根から成り、該第１羽根は前記回転部材の前記第１方向への回転時に前記第１室内の流体の抵抗を受ける第１受圧面を有し、前記第２トルク発生手段は、前記第２室において前記第２基部の外周面に軸方向に沿って前記第２室の前記ケーシング内周面まで突出するように形成された少なくとも１つの第２羽根から成り、該第２羽根は前記回転部材の前記第２方向への回転時に前記第２室内の流体の抵抗を受ける第２受圧面を有し、前記第１受圧面の面積と前記第２受圧面の面積を相異なるようにした。これにより、回転部材の第１方向への回転時に第１室において第１トルク発生手段により発生する最大トルクと、第２方向への回転時に第２室において前記第２トルク発生手段により発生する最大トルクを容易に相異なるようにすることができる。
【００１７】
請求項６では、前記第１トルク発生手段の前記第１羽根と前記第２トルク発生手段の前記第２羽根の数を相異ならしたことにより、前記回転部材の前記第１方向への回転時に前記第１室において前記第１トルク発生手段により発生する最大トルクと、前記回転部材の前記第２方向への回転時に前記第２室において前記第２トルク発生手段により発生する最大トルクを容易に相異なるようにすることができる。
【００１８】
請求項７では、前記回転ダンパは、前記第１室において、前記回転部材の前記第２方向への回転時に前記第１方向への回転時に発生するトルクに比して発生トルクを低減させる第１トルク制御手段と、前記第２室において、前記回転部材の前記第１方向への回転時に前記第２方向への回転時に発生するトルクに比して発生トルクを低減させる第２トルク制御手段とを有するようにした。これにより、回転部材の第１方向への回転時に第１室においてのみ高トルクを発生し、第２方向への回転時に第２室においてのみ高トルクを発生するような回転ダンパが得られる。
【００１９】
請求項８では、前記第１トルク制御手段は、前記第１羽根の先端と前記第１室の内周面との間に設けられた第１弁体から成り、該第１弁体は前記回転部材の前記第２方向への回転時に流体通路を開口し、前記第２トルク制御手段は、前記第２羽根の先端と前記第２室の内周面との間に設けられた第２弁体から成り、該第２弁体は前記回転部材の前記第１方向への回転時に流体通路を開口するようにした。これにより、回転部材の第１方向への回転時に第１室においてのみ発生する最大トルクの大きさと、第２方向への回転時に第２室においてのみ発生する最大トルクの大きさを夫々自在に設計可能な回転ダンパが得られる。
【００２０】
請求項９では、前記第１トルク制御手段は、前記第１室の内周面に形成された第１ストッパ壁の先端と前記回転部材の第１基部の外周面との間に設けられた第３弁体から成り、該第３弁体は前記回転部材の前記第２方向への回転時に流体通路を開口し、前記第２トルク制御手段は、前記第２室の内周面に形成された第２ストッパ壁の先端と前記回転部材の第２基部の外周面との間に設けられた第４弁体から成り、該第４弁体は前記回転部材の前記第１方向への回転時に流体通路を開口するようにした。これにより、回転部材の第１方向への回転時に第１室においてのみ発生する最大トルクの大きさと、第２方向への回転時に第２室においてのみ発生する最大トルクの大きさを夫々自在に設計可能な回転ダンパが得られる。
【００２１】
請求項１０では、前記回転ダンパは、前記回転部材の前記第１方向への回転時に、前記第１室において前記第１羽根の回転ストローク中に発生するトルクの高低及び高トルクないし低トルクの発生領域を制御する第３トルク制御手段と、前記回転部材の前記第２方向への回転時に、前記第２室において前記第２羽根の回転ストローク中に発生するトルクの高低及び高トルクないし低トルクの発生領域を制御する第４トルク制御手段とを有するようにした。これにより、回転部材の第１方向への回転時に第１室においてのみ発生するトルクの大きさ及びそのトルク発生領域と、第２方向への回転時に第２室においてのみ発生するトルクの大きさ及びそのトルク発生領域を夫々自在に設計可能な回転ダンパが得られる。
【００２２】
請求項１１では、前記第３トルク制御手段は、前記第１室を画設する壁面又は前記第１基部の外周面の少なくとも一部に周方向に沿って形成された溝から成り、前記第４トルク制御手段は、前記第２室を画設する壁面又は前記第２基部の外周面の少なくとも一部に周方向に沿って形成された溝から成るようにした。これにより、回転部材の第１方向への回転時に第１室においてのみ発生するトルクの所望する大きさ及びそのトルク発生領域と、第２方向への回転時に第２室においてのみ発生するトルクの所望する大きさ及びそのトルク発生領域を夫々容易かつ自在に設計可能な回転ダンパが得られる。
【００２３】
請求項１２では、前記第１室と第２室は前記ケーシングの中心軸を横断する方向に伸びる前記仕切り壁を介して連設されるようにし、請求項１４では、前記第１室と第２室は前記回転部材の軸方向に伸びる前記仕切り壁を介して並設されるようにしているので、従来の回転ダンパのケーシング室を軸方向又は径方向に区画することにより２室構造の回転ダンパを容易に得ることができる。
【００２４】
請求項１３では、前記ケーシングの中空軸を横断する方向に伸びる前記仕切り壁に流体の連通路を形成したことにより、本発明の回転ダンパの組立てに際し、前記第１室と第２室の間に流体の移動が可能なケーシング室の構造であるために、１回の流体注入工程で各室に流体を充填でき、組立てが極めて容易になる。
【００２５】
【発明の実施の形態】
本発明の実施の形態について添付した図面に基づき説明する。図１〜図１２は本発明の回転ダンパの第１構成例、図１３〜図１６は第２構成例、図１７〜図１９は第３構成例、図２０〜図２１は第４構成例をそれぞれ示す。
【００２６】
まず、本発明の回転ダンパの基本構成を示す第１構成例について説明する。図１は本発明の第１構成例の縦断面図、図２(a)及び(b)は図１のＡ−Ａ線及びＢ-Ｂ線に沿う断面図をそれぞれ示す。
【００２７】
図１に示すように、この回転ダンパ１は、粘性の高いシリコンオイル等の流体が充填封入されるケーシング２の流体室３内に回転部材４の基部５が組込まれ、回転部材４の軸部６が該流体室３外に突出する構造を有する。
ケーシング２の一方の端部７は閉塞されて流体室３の一方の側壁を成す。該端部７の流体室３側の中央部に軸受凸部８が形成されている。ケーシング２の他方の端部９は開口され、該開口端部９は、流体室３の他方の側壁を成す圧力隔壁１０とＯリング１１とを介してエンドキャップ１２が嵌合固定されて封止されている。
【００２８】
回転部材４の基部５が該基部の自由端に形成された凹部に挿入されたブッシュ１３を介してケーシング２の軸受凸部８に軸承され、その軸部６が圧力隔壁１０及びエンドキャップ１２の中央部にそれぞれ形成された軸受開口１４及び１５に軸承されているので、回転部材４はケーシング２に対して相対回転自在にされている。
【００２９】
図１と図２に示すように、本発明の第１構成例は、ケーシング２の前記流体室３を仕切り壁１６により第１流体室１７と第２流体室１８に区画することを特徴とする。この構成例では、本発明の仕切り壁１６はケーシング室３の内径にほぼ等しい外径を有し、その中心部には回転部材４の基部５を軸承する軸受開口が形成されている円板から成る。該仕切り壁１６の一部は、後述するストッパ壁２１が嵌挿可能なように断面Ｖ字形に切り欠かれている。該仕切り壁１６の片面にはフランジ１６’が設けられている。
【００３０】
該仕切り壁１６は、前記圧力隔壁１０が前記開口端部９に組込まれる以前に、回転部材４の基部５に取付けられる。該仕切り壁１６はケーシング２の中心軸を横断する方向に垂直に伸びてケーシング室３内に取り付けられているので、第１室１７と第２室１８は軸方向に連設される。回転部材４の基部５も、前記仕切り壁１６により第１室１７に位置する第１基部１９と第２室１８に位置する第２基部２０に分けられている。しかし、第１基部１９と第２基部２０は一体であるので、回転部材４の回転により一緒に回転する。
【００３１】
ケーシング２の第１室１７と第２室１８の内周面を通して軸方向に沿ってストッパ壁２１が設けられている。該ストッパ壁２１は、回転部材４の回転角度を限定する機能を有するが、トルク発生の機能も併有する。回転部材４の第１基部１９と第２基部２０の夫々の外周面の一部に軸方向に沿って凸条の第１羽根２２と第２羽根２５が設けられている。第１羽根２２と第２羽根２５の先端部には夫々第１弁体２３と第２弁体２６が該先端部を跨がって可動に装着されている。
図２において、第１羽根２２及び第２羽根２５の先端部は断面円形を有し、第１弁体２３及び第２弁体２６は断面Ｃ字形を有する。
【００３２】
図２(a)において、第１羽根２２の回転方向側面の平坦部２２’と第１弁体２３の回転方向側面の平坦部２３’が一体となって第１受圧面２４を形成する。図２(a)において、回転部材４が反時計方向（矢印方向）に回転すると、該第１受圧面２４は第１流体室１７に充填された粘性流体により抵抗を受け、第１弁体２３は第１羽根２２上を時計方向（図２(a)の矢印方向とは反対方向）に回動する。第１弁体２３のケーシング２内周面に対向する面には流体通路３０’が形成されており、流体通路３０’は、第１弁体２３が、図２(a)において、時計方向に最大限回動したとき、、ケーシング２内周面と第１弁体２３との間で該通路３０’は殆ど閉鎖して、粘性流体が殆ど通流しない状態となり、第１弁体２３が反時計方向に回動した状態においては、ケーシング２内周面と第１弁体２３との間で該通路３０’は開口されて、粘性流体がここを通流するようになる。
【００３３】
そして、図２(a)において、第１弁体２３の反回動方向側（即ち、前記平坦部２３’側）の外面は第１流体室１７のケーシング２の内周面に摺接する。更に、回転部材４が反時計方向（図２(a)の矢印方向）に回転すると、粘性流体は前記第１受圧面２４により押され、ストッパ壁２１の先端と第１基部１９との間の狭い隙間等から流動する。この時、第１羽根２２と第１弁体２３は大きな抵抗を受けて回転するため、第１室１７では高トルクが得られる。
【００３４】
一方、回転部材４が反時計方向（矢印方向）に回転すると、第２室１８の第２羽根２５及び第２弁体２６も一緒に図２(a)の矢印方向に回転する。その時、第２弁体２６も第２室１８に充填された粘性流体の抵抗を受けて第２羽根２５上を時計方向（図２(a)の矢印方向とは反対方向）に回動する。そのため、第２室１８のケーシング２の内周面と第２弁体２６との間には、第２羽根２５及び第２弁体２６の反時計方向（図２(a)の矢印方向）の全回転ストロークにおいて流体通路３１’が開口されている。従って、回転部材４の反時計方向の回転中は、第２室１８ではダンパ作用がほとんどない状態となっている。
【００３５】
図２(b)において、第２羽根２５の回転方向側面の平坦部２５’と第２弁体２６の回転方向側面の平坦部２６’が一体となって第２受圧面２７を形成する。図２(b)において、回転部材４が時計方向（矢印方向とは反対方向）に回転すると、該第２受圧面２７は第２室１８に充填された粘性流体により抵抗を受け、第２弁体２６は第２羽根２５上を反時計方向（図２(b)の矢印方向とは反対方向）に回動する。第２弁体２６のケーシング２内周面に対向する面には流体通路３１’が形成されており、流体通路３１’は、第２弁体２６が、図２(b)において、反時計方向に最大限回動したとき、ケーシング２内周面と第２弁体２６との間で該通路３１’は殆ど閉鎖して、粘性流体が殆ど通流しない状態となり、第２弁体２６が時計方向に回動した状態においては、ケーシング２内周面と第２弁体２６との間で該通路３１’は開口されて、粘性流体がここを通流するようになる。
【００３６】
そして、図２(b)において、第２弁体２６の反回動方向側（即ち、前記平坦部２６’側）の外面は第２室１８のケーシング２の内周面に摺接する。更に、回転部材４が時計方向（図２(b)の矢印方向）に回転すると、粘性流体は前記第２受圧面２７により押され、ストッパ壁２１の先端と第２基部２０との間の狭い隙間等から流動する。この時、第２羽根２５と第２弁体２６は大きな抵抗を受けて回転するため、第２室１８では高トルクが得られる。
【００３７】
一方、回転部材４が時計方向（矢印方向）に回転すると、第１室１７の第１羽根２２及び第１弁体２３も一緒に図２(b)の矢印方向に回転する。その時、第１弁体２３も第１室１７に充填された粘性流体の抵抗を受けて第１羽根２２上を反時計方向（図２(b)の矢印方向とは反対方向）に回動する。そのため、第１室１７のケーシング２の内周面と第１弁体２３との間には、第１羽根２２及び第１弁体２３の時計方向（図２(b)の矢印方向）の全回転ストロークにおいて流体通路３０’が開口されている。従って、回転部材４の時計方向の回転中は、第１室１７ではダンパ作用がほとんどない状態となっている。
【００３８】
上述の本発明の第１構成例において、回転部材４が反時計方向（矢印方向）に回転する時（図２(ａ)を参照。）に第１室１７で発生する最大トルクと、回転部材４が時計方向（矢印方向）に回転する時(図２(b)を参照。)に第２室１８で発生する最大トルクとを等しくするには、図３及び図４(a)、(b)に示すように、第１基部１９の直径と第２基部２０の直径とを等しくした場合は、第１室１７の内径δと第２室１８の内径σを等しくし、且つ第１室１７の幅αと第２室１８の幅βを等しくすれば良い。図５及び図６(a)、(b)に示すように、第１基部１９の直径と第２基部２０の直径とを等しくした場合は、要は、第１室１７の容積（α×π・δ）と第２室１８の容積（β×π・σ）がほぼ等しくなるようにすれば良い。前記第１受圧面２４の面積と前記第２受圧面２７の面積をほぼ等しくしても良い。
【００３９】
上述の本発明の第１構成例において、回転部材４が反時計方向（矢印方向）に回転する時（図２(ａ)を参照。）に第１室１７で発生する最大トルクと、回転部材４が時計方向（矢印方向）に回転する時(図２(b)を参照。)に第２室１８で発生する最大トルクとを相異なるようにするには、第１基部１９の直径と第２基部２０の直径とを等しくした場合は、図１１及び図１２(a)、(b)に示すように、第１室１７の容積（α×π・δ）と第２室１８の容積（β×π・σ）が相異なるようにすれば良い。
【００４０】
即ち、第１基部１９の直径と第２基部２０の直径とを等しくした場合は、図７及び図８(a)、(b)に示すように、第１室１７の幅αと第２室１８の幅βを等しくした場合、第１室１７の内径δを第２室１８の内径σよりも大きくすれば、第１室１７で発生する最大トルクを第２室１８で発生する最大トルクよりも大きくすることができ、逆に、第１室１７の内径δを第２室１８の内径σよりも小さくすれば、第１室１７で発生する最大トルクを第２室１８で発生する最大トルクよりも小さくすることができる。また、図９及び図１０(a)、(b)に示すように、第１室１７の内径δと第２室１８の内径σを等しくした場合、第１室１７の幅αを第２室１８の幅βよりも大きくすれば、第１室１７で発生する最大トルクを第２室１８で発生する最大トルクよりも大きくすることができ、逆に、第１室１７の幅αを第２室１８の幅β―よりも小さくすれば、第１室１７で発生する最大トルクを第２室１８で発生する最大トルクよりも小さくすることができる。
【００４１】
前記第１受圧面２４の面積と前記第２受圧面２７の面積を相異なるようにしたり、第１羽根２２と第２羽根２４の数を相異ならして第１受圧面と第２受圧面の総面積を相異なるようにしても、両室１７，１８で相異なる最大トルクが容易に得られる。
その他にも、種々の方法によって、反時計回転方向の最大トルクと時計回転方向の最大トルクを等しくしたり、異なるものにしたりして、自由に設計が可能である。
【００４２】
上述の本発明の第１構成例において、前記第１弁体２３の前述した機能と同一機能を有する弁体を第１室１７に位置するストッパ壁２１の先端部に設け、前記第２弁体２６の前述した機能と同一機能を有する弁体を第２室１８に位置するストッパ壁２１の先端部に設けても、両室１７，１８で発生する最大トルクの大きさは夫々自在に設計できる。
【００４３】
次に、本発明の回転ダンパの第２構成例について説明する。図１３は、第１構成例における図２に対応する、本発明の第２構成例の断面図を示す。なお、第１構成例と同一の構成部分には同一の符号を付す。
【００４４】
図１３に示すように、本発明の第２構成例は、上述の第１構成例の回転ダンパの第１室１７に第３トルク制御手段を備え、同第２室１８に第４トルク制御手段を備えていることを特徴とする。図１３(a)では第３トルク制御手段として、第１室１７に位置する第１基部１９の外周面に周方向に沿って溝２８が設けられている。図１３(b)では第４トルク制御手段として、第２室１８に位置する第２基部２０の外周面に周方向に沿って溝２９が設けられている。各室１７、１８が位置するケーシング２の流体室内周面等に前記溝２８、２９に相当する溝を設けても良い。
該溝２８、２９は、前記基部１９、２０の周方向に沿って設けられたその箇所とその長さによって、前記室１７，１８における夫々の高トルクないし低トルクの発生領域が決定され、その幅と深さによって、前記室１７，１８における夫々の発生するトルクの大きさが決定される。
【００４５】
図１３(a)に示すように、前記溝２８は、第１羽根２２の反第１受圧面２４側の第１基部１９の外周面を始端として時計方向に回転部材の軸を中心として約１８０°の開角度で、溝深さが一定で刻設されている。一方、前記溝２９は、図１３(b)に示すように、第２羽根２５の反第２受圧面２７側の第２基部２０の外周面を始端として反時計方向に回転部材の軸を中心として約１８０°の開角度で、溝深さが一定で且つ前記溝２８とほぼ同一の深さに刻設されている。
【００４６】
次に、上記のように構成された第３及び第４トルク制御手段の作用を第１４図及び第１５図に基づいて説明する。先ず、図１４に示すように、回転部材４が反時計方向(矢印方向)に回転する場合について説明する。
【００４７】
回転部材４が反時計方向(矢印方向)に回転して図１４(１)に示す状態になると、前記第１受圧面２４は第１室１７に充填された粘性流体により抵抗を受け、第１弁体２３は第１羽根２２上を時計方向（矢印方向とは反対方向）に回動して、第１弁体２３の反回動方向側の外面は第１流体室１７のケーシング２の内周面に摺接する。更に、回転部材４が反時計方向（矢印方向）に回転すると、図１４(１)、(２)に示すように、粘性流体は前記第１受圧面２４により押され、ストッパ壁２１と第１基部１９に刻設された前記溝２８との間に形成された流体通路３０を通して矢印方向に流動する。この時、第１羽根２２と第１弁体２３は大きな抵抗を受けずにスムーズに回転する。前記溝２８の終端が第１室１７のストッパ壁２１の先端の側面に達して前記流体通路３０が閉鎖されるまでの間は、粘性流体の流動が確保されるているので、第１室１７では低トルクが維持される。
【００４８】
図１４(２)と(３)の間で示される状態まで、即ち該流体通路３０が閉鎖する角度まで回転部材４が回転すると、第１羽根２２と第１弁体２３は突然大きな抵抗を受けて回転するため、第１室１７では高トルクが得られる。
【００４９】
一方、図１４(１)〜(３)に示すように、第２羽根２５及び第２弁体２６の反時計方向（矢印方向）の全回転ストロークにおいて、第２室１８のケーシング２の内周面と第２弁体２６との間及びストッパ壁２１と第２基部２０に刻設された前記溝２８との間に少なくとも一つの流体通路３１、３１’が形成されている。そのため、粘性流体は、流体通路３１、３１’を通してそれぞれ矢印方向に流動する。従って、第２室１８では常時ダンパ作用がほとんどない状態、即ち低トルクが維持される。
【００５０】
次に、図１５に示すように、回転部材４が時計方向(矢印方向)に回転する場合について説明する。
回転部材４が時計方向(矢印方向)に回転すると、第１室１７の第３トルク制御手段と第２室１８の第４トルク制御手段は、回転部材４が反時計方向に回転する上述の場合とは逆に作動する。従って、第１室１７のトルクは、回転部材４の全角度範囲に亘って、低⇒低⇒低が維持され、一方、第２室のトルクは低⇒低⇒高に変化する。
【００５１】
上記のように夫々独立して作動する２つのダンパ室１７及び１８から成る本発明の回転ダンパは、総じて、上記第２構成例の回転部材４が反時計方向に回転する場合は、その回転角度範囲に応じて低⇒低⇒高へとダンパトルクを変化し、回転部材４が時計方向に回転する場合は、その回転角度範囲に応じて低⇒低⇒高へとダンパトルクを変化することができる。
【００５２】
図１６(１)は、上述の本発明の第１構成例により発生するトルク線図を示す。更に、上記第２構成例の溝２８、２９の長さ、その刻設箇所、その幅や深さを相異ならしたりすることにより、本発明の回転トルクは、第１羽根２２及び第２羽根２５の反時計方向及び時計方向への回転ストロークにおける発生トルクの高低Ta及びTbを、図１６(２)〜(５)に示すように、回転部材４の反時計方向回転及び時計方向回転の角度範囲に応じて自在に高ないし低トルクを発生できる。
【００５３】
例えば、図１６(２)のトルク線図によれば、反時計方向及び時計方向への羽根の回転ストロークの始端領域と終端領域で、大きさがほぼ等しい高トルクを発生できるようにしたものである。図１６(３)のトルク線図によれば、反時計方向及び時計方向への回転ストロークの終端領域で相異なる大きさのトルクを発生できるようにしたものである。図１６(４)のトルク線図によれば、反時計方向及び時計方向への回転ストロークの終端領域で高トルク域を重複できるようにしたものである。図１６(５)のトルク線図によれば、反時計方向及び時計方向への回転ストロークの始端領域でほぼ同等の高トルクをできるようにしたものである。
【００５４】
しかしながら、本発明の回転ダンパは、上記トルク線図の例に限られるものではなく、刻設した上記溝２８、２９の長さ、箇所、幅及び深さののいずれかを任意に組合せることにより、その他の発生トルクの大きさとその高、中又は低トルクの発生領域とを変化することができる。
【００５５】
次に、本発明の回転ダンパの第３構成例について説明する。図１７は、本発明の仕切り壁１６の構造を示し、図１７(１)はその正面を示し、図１７(２)はその断面を示す。図１８は、前記仕切り壁１６をケーシング２の流体室３内に取付けた状態の縦断面を示す。
【００５６】
図１７に示すように、本発明の仕切り壁１６は、回転ダンパの組立ての際の第1及び第２室へのオイル注入と、組立て後のエア抜きを容易化するために、該壁１６の面にオイルの連通孔３２を設けた。該連通孔３２は、回転部材４が反時計方向及び時計方向のいずれに回転する場合でも、トルク発生に障害とならない角度範囲ｂの前記仕切り壁１６に切り欠かなければならない。即ち、図１９に示すように、回転部材４の反時計方向及び時計方向回転で低トルク域が重なる角度領域の部分ａに該孔３２を空けることが適切である。
【００５７】
次に、本発明の回転ダンパの第４構成例について説明する。図２０(１)は、本発明の上記仕切り壁１６とは別構造のものを備えた回転ダンパを縦断面で示し、図２０(２)は、そのＡ-Ａ線に沿う断面を示す。この構成例の仕切り壁は、前記仕切り壁１６の代わりに、前記回転部材４の軸方向に伸びる一対の壁３３、３３が前記ケーシング２の流体室３の内周面に突出して形成されている。この仕切り壁３３，３３を介して流体室３が第１室３４と第２室３５に区画されて径方向に並設される。そして、第１羽根と第１弁体が一体となって一側面で第１受圧面３８を形成し、第２羽根と第２弁体が一体となって一側面で第２受圧面３９を形成する。また、該第１受圧面３８と第２受圧面３９は、回転方向に対して、反対向きになっている。
【００５８】
この仕切り壁３３，３３を備えた本発明の回転ダンパは、前記仕切り壁１６を備えた第１構成例の回転ダンパよりもダンパ室幅を更に小さくできるという長所を有する。しかしながら、前記第１室３４と第２室３５に位置する基部５のそれぞれの外周面の一部に軸方向に沿って設けられる羽根の回転ストロークは、第１構成例の回転ダンパのそれよりも小さくなる。
【００５９】
図２０で示すように、この構成例では、前記第３トルク制御手段及び前記第４トルク制御手段として、それぞれ上記第１室３４及び第２室３５に位置するケーシング２の流体室内周面に溝３６及び３７が設けられている。さらに、この構成例では、ダンパ室３４及び３５の内径を相異なるようにしているので、両室で発生する最大トルクは相異なる。
【００６０】
図２１は上記ダンパ室３４及び３５の幅（奥行き）が相異なる例を示し、図２０(１)はその縦断面を示し、、図２０(２)は図２０(１)のＡ-Ａ線に沿う断面を示す。この実施例では、ダンパ室３４及び３５の幅を相異なるようにしているので、両室で発生する最大トルクは相異なる。
【００６１】
【発明の効果】
以上のように、本発明の回転ダンパは、第１構成例によれば、回転部材４の反時計方向及び時計方向回転時に発生する最大トルクを相互に独立して自在に変更でき、第２構成例によれば、更にその変更したトルクの発生領域も相互に独立して自在に設定できるという効果を有する。さらに、本発明の回転ダンパは、第３構成例によれば第１室及び第２室から成る本発明の回転ダンパの組立ての際のオイル注入を容易化し、組立て後のエア抜きを容易化するという効果を有する。さらに、本発明の回転ダンパは、ダンパ装置を小型化でき、第４構成例によれば、なお一層小型化できるという効果を有する。
【図面の簡単な説明】
【図１】本発明の第１構成例による回転ダンパを示す縦断面図。
【図２】図１の断面図で、(a)はＡ−Ａ線に沿う断面図、(b)はＢ−Ｂ線に沿う断面図。
【図３】第１構成例のトルク発生手段の変更例を示す縦断面図。
【図４】図３の断面図で、(a)はＡ−Ａ線に沿う断面図、(b)はＢ−Ｂ線に沿う断面図。
【図５】第１構成例のトルク発生手段の他の変更例を示す縦断面図。
【図６】図５の断面図で、(a)はＡ−Ａ線に沿う断面図、(b)はＢ−Ｂ線に沿う断面図。
【図７】第１構成例のトルク発生手段の他の変更例を示す縦断面図。
【図８】図７の断面図で、(a)はＡ−Ａ線に沿う断面図、(b)はＢ−Ｂ線に沿う断面図。
【図９】第１構成例のトルク発生手段の他の変更例を示す縦断面図。
【図１０】図９の断面図で、(a)Ａ−Ａ線に沿う断面図。(b)はＢ−Ｂ線に沿う断面図。
【図１１】第１構成例のトルク発生手段の他の変更例を示す縦断面図。
【図１２】図１１の断面図で、(a)はＡ−Ａ線に沿う断面図、(b)はＢ−Ｂ線に沿う断面図。
【図１３】本発明の第２構成例による回転ダンパを示す断面図。
【図１４】第２構成例のトルク制御手段の反時計方向に回転時の作用を示す断面図。
【図１５】第２構成例のトルク制御手段の時計方向に回転時の作用を示す断面図。
【図１６】第１構成例のトルク発生手段により発生するトルク線図で、(１)は第１構成例のトルク発生手段により発生するトルク線図、(２)〜(５)は第２構成例のトルク発生手段により発生するトルク線図。
【図１７】本発明の第３構成例による回転ダンパに備えた仕切り壁を示す正面図及び断面図。
【図１８】本発明の第３構成例による回転ダンパを示す縦断面図。
【図１９】第３構成例によるトルク線図。
【図２０】本発明の第４構成例による回転ダンパを示す断面図で、(１)は縦断面図、(２)は(１)のＡ−Ａ線に沿う断面図。
【図２１】第４構成例の変更例を示す断面図で、(２)は(１)のＡ−Ａ線に沿う断面図。
【図２２】従来の回転ダンパの断面図。
【符号の説明】
１…回転ダンパ、２…ケーシング、３…流体室、４…回転部材、５…基部、６…軸部、７…ケーシングの端部、８…軸受凸部、９…ケーシングの開口端部、１０…圧力隔壁、１１…Ｏリング、１２…エンドキャップ、１３…ブッシュ、１４、１５…軸受開口、１６…仕切り壁、１６’…仕切り壁のフランジ、１７…第１室、１８…第２室、１９…第１基部、２０…第２基部、２１…ストッパ壁、２２…第１羽根、２２’…第１羽根の平坦部、２３…第１弁体、２３’…第１弁体の平坦部、２４…第１受圧面、２５…第２羽根、２５’…第２羽根の平坦部、２６…第２弁体、２７…第２受圧面、２８，２９…溝、３０、３０’、３１、３１’…流体通路、３２…連通孔、３３…仕切り壁、３４…第１室、３５…第２室、３６，３７…溝、３８…第１受圧面、３９…第２受圧面。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a rotary damper that applies a braking force to a lid, a door, or the like when the lid is opened or closed.
[0002]
[Prior art]
A conventional rotary damper as shown in FIG. 22 includes a casing having a fluid chamber filled with a fluid, a base portion accommodated in the fluid chamber, and a shaft portion projecting outside the fluid chamber. A rotatable rotating member; a stopper wall provided in the casing for limiting a rotation angle of the rotating member in the fluid chamber; and for generating torque in cooperation with the stopper wall during relative rotation of the rotating member. And a blade provided at the base of the rotating member.
[0003]
Among the conventional rotary dampers described above, in the case of the rotary damper proposed in Japanese Patent Laid-Open No. 11-182607 as shown in FIG. 22 (1), when the rotary member rotates in either the counterclockwise direction or the clockwise direction. In other words, in both the opening and closing, high torque is generated in the terminal region of the rotation stroke of the blade. Further, in the case of the rotary damper proposed in US Pat. No. 4,653,141 and Japanese Patent Laid-Open No. 58-50342 as shown in FIGS. 22 (2) and (3), only the end region of the rotational stroke in both directions is used. High torque is generated even in the start end region. However, in the conventional rotary damper, the magnitude of the maximum torque generated when the door is opened and when the door is closed has to be the same.
[0004]
Even in the case of the conventional rotary damper described above, a groove that works effectively only when rotating in either the counterclockwise direction or the clockwise direction is suitable for the inner peripheral surface of the casing or the outer peripheral surface of the base of the rotating member. It is possible to make the maximum torque generated during counterclockwise rotation different from the maximum torque generated during clockwise rotation by forming a long length, a width and a depth. However, in this method, the torque changes greatly due to a slight difference in the width and depth of the groove, and the designed maximum torque may change significantly. For this reason, in order to obtain the desired maximum torque required during the bi-directional rotation, it is necessary to process the groove with extremely high accuracy, resulting in an increase in processing cost.
[0005]
When it is necessary to make the maximum torque generated during counterclockwise rotation different from the maximum torque generated during clockwise rotation, two types of rotary dampers with grooves having different widths or depths are used. It can also be used in combination. However, since each rotary damper is provided with a casing, a rotating member, a stopper wall, torque generating means, etc., the entire damper device inevitably has to be increased in size and has a drawback of becoming expensive.
[0006]
Further, in any case where the single rotary damper is used, the maximum torque generation region during counterclockwise rotation and the maximum torque generation region during clockwise rotation are substantially the same as the rotation stroke of the blade. Exists in the angular range. That is, in the conventional rotary damper shown in FIG. 22 (1), the magnitude of the torque generated during the counterclockwise rotation varies from low to low to high from the start end region to the end region of the blade rotation stroke. On the other hand, the magnitude of torque generated during clockwise rotation also changes from low to low to high. Further, in the conventional rotary damper shown in FIGS. 22 (2) and (3), the magnitude of the torque generated during the counterclockwise rotation changes from high ⇒ low ⇒ high, while the torque generated during the clockwise rotation Similarly, the size varies from high to low to high.
[0007]
In addition, even when high-precision grooving as described above is performed, if the torque magnitude during counterclockwise rotation is designed as medium ⇒ low ⇒ high, the torque magnitude during clockwise rotation will be high ⇒ Low ⇒ Medium, so design freedom is greatly limited. Therefore, the conventional rotary damper described above cannot be designed by independently changing the maximum torque generation region during counterclockwise rotation and the maximum torque generation region during clockwise rotation independently of each other.
[0008]
[Problems to be solved by the invention]
As described above, conventional rotary dampers have limited applications because the magnitude of torque generated during counterclockwise rotation and clockwise rotation and the torque generation region thereof cannot be freely varied. For example, when it is used as a toilet lid for a toilet seat or a lid of a copying machine, the brake is applied with a high torque in order to absorb the impact at the end of the closing direction, that is, immediately before the lid is closed. On the other hand, in the end region in the opening direction, that is, in the maximum open state of the lid, if too much braking force is applied, there is a risk that the hand will be released before it is fully opened. A moderate damper force is appropriate. Therefore, the conventional rotary damper has not been able to properly cope with such applications.
[0009]
Further, in the case of a product takeout lid such as a vending machine, a torque sufficient to prevent the lid from falling in the maximum opening state of the lid, that is, the maximum opening state of the lid is sufficient. On the other hand, in order to be able to take out canned coffee or cups without having to squeeze it, it is designed so that the lid closes slowly by applying high torque at the initial stage when the lid falls. Is good. During the closing of the lid, almost no braking force is required, and it should be closed quickly with low torque. Immediately before complete closing, it is necessary to close with a certain degree of braking force in order to prevent shocking closing. In addition, the lid just before it is completely closed is in a state of being almost directed downward, and if the brake is applied with high torque, there is a possibility that the lid may stop immediately before closing. The torque of can be small. However, when the lid is in a closed state, a moderate torque is required to prevent the lid from flapping due to wind or the like in the closed state. Therefore, it is not appropriate to use the conventional rotary damper for the lid as described above in which it is desirable that the magnitude of the torque generated in the opening direction and the closing direction be different from each other.
[0010]
[Means for Solving the Problems]
In order to solve the above problems, a rotary damper according to the present invention comprises a casing having a fluid chamber filled with a fluid, a base portion accommodated in the fluid chamber, and a shaft portion projecting outside the fluid chamber. A rotating member that is relatively rotatable, a stopper wall that is provided in the casing and limits a rotation angle of the rotating member in the fluid chamber, and generates torque in cooperation with the stopper wall during relative rotation of the rotating member. In the rotary damper having torque generating means, the casing includes a partition wall that divides the fluid chamber into a first chamber and a second chamber, and the rotating member includes a first base portion located in the first chamber; Integrated with the second base located in the second chamber To rotate The first base includes first torque generating means for generating torque in the first chamber when the rotating member rotates in the first direction, and the second base extends in the second direction of the rotating member. The second torque generating means for generating torque in the second chamber at the time of rotation is provided.
[0011]
Since the casing chamber of the conventional rotary damper is divided into two chambers by a partition wall, the damper device can be reduced in size and is inexpensive.
[0012]
In addition, the rotating member integrally includes a first base located in the first chamber and a second base located in the second chamber. To rotate The first base includes first torque generating means for generating torque in the first chamber when the rotating member rotates in the first direction, and the second base extends in the second direction of the rotating member. Since the second torque generating means for generating the torque in the second chamber at the time of rotation of the rotating member is provided, the desired maximum torque required for each of the rotating member rotating in the counterclockwise direction and rotating clockwise is set. In the chamber can be obtained independently of each other.
[0013]
According to claim 2, since the first chamber and the second chamber are formed so as to have substantially the same volume, the maximum torque generated by the first torque generating means in the first chamber when the rotating member rotates in the first direction. The maximum torque generated by the second torque generating means in the second chamber when rotating in the second direction can be easily made substantially equal.
[0014]
According to a third aspect of the present invention, the first torque generating means of the rotating member is formed so as to protrude from the outer peripheral surface of the first base portion along the axial direction to the inner peripheral surface of the casing of the first chamber in the first chamber. The first blade has a first pressure receiving surface that receives the resistance of the fluid in the first chamber when the rotating member rotates in the first direction, and the second torque The generating means includes at least one second blade formed in the second chamber so as to protrude on the outer peripheral surface of the second base portion along the axial direction to the inner peripheral surface of the casing of the second chamber, The second blade has a second pressure receiving surface that receives the resistance of the fluid in the second chamber when the rotating member rotates in the second direction, and determines the area of the first pressure receiving surface and the area of the second pressure receiving surface. Almost equal. Accordingly, the maximum torque generated by the first torque generating means in the first chamber when the rotating member rotates in the first direction, and the maximum torque generated by the second torque generating means in the second chamber when rotated in the second direction. Can easily be made approximately equal.
[0015]
In claim 4, since the first chamber and the second chamber are formed to have different volumes, the maximum torque generated by the first torque generating means in the first chamber when the rotating member rotates in the first direction The maximum torque generated by the second torque generating means in the second chamber when rotating in the second direction can be easily made different. .
[0016]
According to a fifth aspect of the present invention, the first torque generating means of the rotating member protrudes from the outer peripheral surface of the first base portion along the axial direction to the inner peripheral surface of the casing of the first chamber in the first chamber. The first blade is formed of at least one first blade, and the first blade has a first pressure receiving surface that receives the resistance of the fluid in the first chamber when the rotating member rotates in the first direction, and the second blade The torque generating means includes at least one second blade formed in the second chamber so as to protrude along the axial direction on the outer peripheral surface of the second base portion to the casing inner peripheral surface of the second chamber, The second blade has a second pressure receiving surface that receives the resistance of the fluid in the second chamber when the rotating member rotates in the second direction, and the area of the first pressure receiving surface and the area of the second pressure receiving surface. Were made different. Thus, the maximum torque generated by the first torque generating means in the first chamber when the rotating member rotates in the first direction and the maximum torque generated by the second torque generating means in the second chamber when rotating in the second direction. The torque can be easily made different.
[0017]
According to a sixth aspect of the present invention, the number of the first blades of the first torque generating means and the number of the second blades of the second torque generating means are different, so that the rotation member is rotated in the first direction. The maximum torque generated by the first torque generating means in the first chamber easily differs from the maximum torque generated by the second torque generating means in the second chamber when the rotating member rotates in the second direction. Can be.
[0018]
According to a seventh aspect of the present invention, the rotating damper reduces the generated torque in the first chamber compared to the torque generated when the rotating member rotates in the second direction compared to the torque generated when the rotating member rotates in the first direction. Torque control means, and second torque control means for reducing the generated torque in the second chamber as compared to the torque generated when the rotating member rotates in the first direction compared to the torque generated when the rotating member rotates in the second direction. To have. As a result, a rotary damper is obtained that generates high torque only in the first chamber when the rotating member rotates in the first direction and generates high torque only in the second chamber when rotated in the second direction.
[0019]
According to an eighth aspect of the present invention, the first torque control means includes a first valve body provided between a tip end of the first blade and an inner peripheral surface of the first chamber. A fluid passage is opened when the member rotates in the second direction, and the second torque control means is a second valve body provided between the tip of the second blade and the inner peripheral surface of the second chamber. The second valve element opens a fluid passage when the rotating member rotates in the first direction. As a result, the maximum torque generated only in the first chamber when the rotating member rotates in the first direction and the maximum torque generated only in the second chamber when rotated in the second direction can be freely designed. A possible rotary damper is obtained.
[0020]
In a ninth aspect of the present invention, the first torque control means is provided between a tip end of a first stopper wall formed on an inner peripheral surface of the first chamber and an outer peripheral surface of the first base portion of the rotating member. The third valve body opens a fluid passage when the rotating member rotates in the second direction, and the second torque control means is formed on the inner peripheral surface of the second chamber. A fourth valve body is provided between the tip of the second stopper wall and the outer peripheral surface of the second base portion of the rotating member, and the fourth valve body is fluid when the rotating member rotates in the first direction. The passage was opened. As a result, the maximum torque generated only in the first chamber when the rotating member rotates in the first direction and the maximum torque generated only in the second chamber when rotated in the second direction can be freely designed. A possible rotary damper is obtained.
[0021]
According to a tenth aspect of the present invention, the rotary damper generates a high and low torque and a high torque or a low torque generated during the rotation stroke of the first blade in the first chamber when the rotary member rotates in the first direction. A third torque control means for controlling a region; and a level of torque generated during a rotation stroke of the second blade in the second chamber and a high torque or a low torque when the rotating member rotates in the second direction. And fourth torque control means for controlling the generation region. Thereby, the magnitude of the torque generated only in the first chamber when the rotating member rotates in the first direction and the torque generation region thereof, the magnitude of the torque generated only in the second chamber when rotated in the second direction, and A rotary damper that can freely design the torque generation region can be obtained.
[0022]
According to an eleventh aspect, the third torque control means includes a groove formed along a circumferential direction on at least a part of a wall surface defining the first chamber or an outer peripheral surface of the first base, and The torque control means includes a groove formed along a circumferential direction on at least a part of a wall surface defining the second chamber or an outer peripheral surface of the second base portion. Accordingly, the desired magnitude of the torque generated only in the first chamber when the rotating member rotates in the first direction and the torque generation region thereof, and the desired torque generated only in the second chamber when rotated in the second direction. Thus, it is possible to obtain a rotary damper whose size and torque generation region can be designed easily and freely.
[0023]
In claim 12, the first chamber and the second chamber are connected to each other via the partition wall extending in a direction crossing the central axis of the casing. In claim 14, the first chamber and the second chamber are connected to each other. Since the chambers are arranged side by side through the partition wall extending in the axial direction of the rotating member, a rotary damper having a two-chamber structure can be obtained by dividing the casing chamber of the conventional rotating damper in the axial direction or the radial direction. Can be easily obtained.
[0024]
According to a thirteenth aspect of the present invention, a fluid communication passage is formed in the partition wall extending in a direction crossing the hollow shaft of the casing, so that when the rotary damper according to the present invention is assembled, the fluid is connected between the first chamber and the second chamber. Because of the structure of the casing chamber capable of moving the fluid, each chamber can be filled with fluid in a single fluid injection step, and assembly becomes extremely easy.
[0025]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described with reference to the accompanying drawings. 1 to 12 are a first configuration example of the rotary damper of the present invention, FIGS. 13 to 16 are a second configuration example, FIGS. 17 to 19 are a third configuration example, and FIGS. 20 to 21 are a fourth configuration example. Each is shown.
[0026]
First, a first configuration example showing the basic configuration of the rotary damper of the present invention will be described. 1 is a longitudinal sectional view of a first configuration example of the present invention, and FIGS. 2A and 2B are sectional views taken along lines AA and BB in FIG. 1, respectively.
[0027]
As shown in FIG. 1, the rotary damper 1 includes a base portion 5 of a rotary member 4 incorporated in a fluid chamber 3 of a casing 2 filled with a fluid such as silicon oil having high viscosity, and a shaft portion of the rotary member 4. 6 has a structure protruding outside the fluid chamber 3.
One end 7 of the casing 2 is closed to form one side wall of the fluid chamber 3. A bearing projection 8 is formed at the center of the end 7 on the fluid chamber 3 side. The other end 9 of the casing 2 is opened, and the open end 9 is sealed by fitting and fixing an end cap 12 via a pressure bulkhead 10 and an O-ring 11 forming the other side wall of the fluid chamber 3. Has been.
[0028]
The base portion 5 of the rotating member 4 is supported by the bearing convex portion 8 of the casing 2 via a bush 13 inserted in a concave portion formed at the free end of the base portion, and the shaft portion 6 is connected to the pressure bulkhead 10 and the end cap 12. Since it is supported by bearing openings 14 and 15 formed in the center, the rotating member 4 is rotatable relative to the casing 2.
[0029]
As shown in FIGS. 1 and 2, the first configuration example of the present invention is characterized in that the fluid chamber 3 of the casing 2 is partitioned into a first fluid chamber 17 and a second fluid chamber 18 by a partition wall 16. . In this configuration example, the partition wall 16 of the present invention has an outer diameter substantially equal to the inner diameter of the casing chamber 3, and is formed from a disc in which a bearing opening for bearing the base portion 5 of the rotating member 4 is formed at the center. Become. A part of the partition wall 16 is notched in a V-shaped cross section so that a stopper wall 21 described later can be inserted. A flange 16 ′ is provided on one side of the partition wall 16.
[0030]
The partition wall 16 is attached to the base 5 of the rotating member 4 before the pressure partition 10 is assembled into the open end 9. Since the partition wall 16 extends perpendicularly in a direction crossing the central axis of the casing 2 and is mounted in the casing chamber 3, the first chamber 17 and the second chamber 18 are connected in the axial direction. The base 5 of the rotating member 4 is also divided into a first base 19 located in the first chamber 17 and a second base 20 located in the second chamber 18 by the partition wall 16. However, since the first base 19 and the second base 20 are integrated, they rotate together by the rotation of the rotating member 4.
[0031]
A stopper wall 21 is provided along the axial direction through the inner peripheral surfaces of the first chamber 17 and the second chamber 18 of the casing 2. The stopper wall 21 has a function of limiting the rotation angle of the rotating member 4, but also has a function of generating torque. Convex first blades 22 and second blades 25 are provided along part of the outer peripheral surfaces of the first base portion 19 and the second base portion 20 of the rotating member 4 along the axial direction. A first valve body 23 and a second valve body 26 are movably mounted on the tip portions of the first blade 22 and the second blade 25 so as to straddle the tip portions.
In FIG. 2, the front-end | tip part of the 1st blade | wing 22 and the 2nd blade | wing 25 has a circular cross section, and the 1st valve body 23 and the 2nd valve body 26 have a C-shaped cross section.
[0032]
In FIG. 2A, the flat portion 22 ′ on the side surface in the rotational direction of the first blade 22 and the flat portion 23 ′ on the side surface in the rotational direction of the first valve body 23 are integrated to form a first pressure receiving surface 24. In FIG. 2A, when the rotating member 4 rotates counterclockwise (arrow direction), the first pressure receiving surface 24 receives resistance by the viscous fluid filled in the first fluid chamber 17, and the first valve body 23. Rotates on the first blade 22 in the clockwise direction (the direction opposite to the arrow direction in FIG. 2A). A fluid passage 30 ′ is formed on a surface of the first valve body 23 facing the inner peripheral surface of the casing 2, and the fluid passage 30 ′ is formed so that the first valve body 23 is clockwise in FIG. When fully rotated, the passage 30 ′ is almost closed between the inner peripheral surface of the casing 2 and the first valve body 23, so that the viscous fluid hardly flows and the first valve body 23 is counteracted. In the state of rotating in the clockwise direction, the passage 30 ′ is opened between the inner peripheral surface of the casing 2 and the first valve body 23 so that the viscous fluid flows therethrough.
[0033]
In FIG. 2A, the outer surface of the first valve body 23 on the counter-rotating direction side (that is, the flat portion 23 ′ side) is in sliding contact with the inner peripheral surface of the casing 2 of the first fluid chamber 17. Further, when the rotating member 4 rotates counterclockwise (the arrow direction in FIG. 2 (a)), the viscous fluid is pushed by the first pressure receiving surface 24, and between the tip of the stopper wall 21 and the first base portion 19 is pressed. It flows from a narrow gap. At this time, since the first blade 22 and the first valve body 23 receive a large resistance and rotate, a high torque is obtained in the first chamber 17.
[0034]
On the other hand, when the rotating member 4 rotates counterclockwise (arrow direction), the second blade 25 and the second valve body 26 of the second chamber 18 also rotate together in the arrow direction of FIG. At that time, the second valve body 26 also receives the resistance of the viscous fluid filled in the second chamber 18 and rotates on the second blade 25 in the clockwise direction (the direction opposite to the arrow direction in FIG. 2A). Therefore, between the inner peripheral surface of the casing 2 of the 2nd chamber 18 and the 2nd valve body 26, the 2nd blade | wing 25 and the 2nd valve body 26 are counterclockwise (arrow direction of Fig.2 (a)). The fluid passage 31 'is opened during the entire rotation stroke. Therefore, during the counterclockwise rotation of the rotating member 4, the second chamber 18 is in a state where there is almost no damper action.
[0035]
In FIG. 2 (b), the flat portion 25 ′ on the side surface in the rotational direction of the second blade 25 and the flat portion 26 ′ on the side surface in the rotational direction of the second valve body 26 form a second pressure receiving surface 27. In FIG. 2B, when the rotating member 4 rotates in the clockwise direction (the direction opposite to the arrow direction), the second pressure receiving surface 27 receives resistance by the viscous fluid filled in the second chamber 18, and the second valve The body 26 rotates on the second blade 25 in the counterclockwise direction (the direction opposite to the arrow direction in FIG. 2B). A fluid passage 31 ′ is formed on the surface of the second valve body 26 facing the inner peripheral surface of the casing 2, and the fluid passage 31 ′ is formed in the counterclockwise direction in FIG. When the maximum rotation is made, the passage 31 ′ is almost closed between the inner peripheral surface of the casing 2 and the second valve body 26, so that the viscous fluid hardly flows. In the state rotated in the direction, the passage 31 ′ is opened between the inner peripheral surface of the casing 2 and the second valve body 26, and the viscous fluid flows therethrough.
[0036]
In FIG. 2 (b), the outer surface of the second valve body 26 on the counter-rotating direction side (that is, the flat portion 26 ′ side) is in sliding contact with the inner peripheral surface of the casing 2 of the second chamber 18. Further, when the rotating member 4 rotates in the clockwise direction (the arrow direction in FIG. 2B), the viscous fluid is pushed by the second pressure receiving surface 27, and the space between the tip of the stopper wall 21 and the second base 20 is narrow. It flows from the gap. At this time, since the second blade 25 and the second valve body 26 are rotated by receiving a large resistance, a high torque is obtained in the second chamber 18.
[0037]
On the other hand, when the rotating member 4 rotates clockwise (arrow direction), the first blade 22 and the first valve body 23 of the first chamber 17 also rotate together in the arrow direction of FIG. At that time, the first valve body 23 also receives the resistance of the viscous fluid filled in the first chamber 17 and rotates on the first blade 22 in the counterclockwise direction (the direction opposite to the arrow direction in FIG. 2B). . Therefore, between the inner peripheral surface of the casing 2 of the first chamber 17 and the first valve body 23, all the first blades 22 and the first valve body 23 in the clockwise direction (the arrow direction in FIG. 2B). The fluid passage 30 'is opened in the rotation stroke. Accordingly, during the clockwise rotation of the rotating member 4, the first chamber 17 is in a state where there is almost no damper action.
[0038]
In the first configuration example of the present invention described above, the maximum torque generated in the first chamber 17 when the rotating member 4 rotates counterclockwise (arrow direction) (see FIG. 2A), and the rotating member In order to equalize the maximum torque generated in the second chamber 18 when 4 rotates clockwise (in the direction of the arrow) (see FIG. 2B), FIG. 3 and FIGS. ), When the diameter of the first base 19 and the diameter of the second base 20 are made equal, the inner diameter δ of the first chamber 17 and the inner diameter σ of the second chamber 18 are made equal, and the first chamber 17 And the width β of the second chamber 18 may be made equal. As shown in FIGS. 5 and 6 (a) and 6 (b), when the diameter of the first base portion 19 and the diameter of the second base portion 20 are equal, the volume (α × π) of the first chamber 17 is important. It is sufficient that δ) and the volume (β × π · σ) of the second chamber 18 are substantially equal. The area of the first pressure receiving surface 24 and the area of the second pressure receiving surface 27 may be substantially equal.
[0039]
In the first configuration example of the present invention described above, the maximum torque generated in the first chamber 17 when the rotating member 4 rotates counterclockwise (arrow direction) (see FIG. 2A), and the rotating member In order to make the maximum torque generated in the second chamber 18 different when the 4 rotates clockwise (in the direction of the arrow) (see FIG. 2B), the diameter of the first base 19 and the first torque When the diameters of the two base portions 20 are equal, as shown in FIGS. 11 and 12A and 12B, the volume of the first chamber 17 (α × π · δ) and the volume of the second chamber 18 ( (β × π · σ) may be different from each other.
[0040]
That is, when the diameter of the first base portion 19 and the diameter of the second base portion 20 are equal, the width α of the first chamber 17 and the second chamber are set as shown in FIGS. 7 and 8A and 8B. 18 having the same width β, if the inner diameter δ of the first chamber 17 is larger than the inner diameter σ of the second chamber 18, the maximum torque generated in the first chamber 17 is greater than the maximum torque generated in the second chamber 18. Conversely, if the inner diameter δ of the first chamber 17 is made smaller than the inner diameter σ of the second chamber 18, the maximum torque generated in the first chamber 17 is increased to the maximum torque generated in the second chamber 18. Can be made smaller. 9 and 10A and 10B, when the inner diameter δ of the first chamber 17 is equal to the inner diameter σ of the second chamber 18, the width α of the first chamber 17 is set to the second chamber. If the width β is larger than the width β of the first chamber 17, the maximum torque generated in the first chamber 17 can be made larger than the maximum torque generated in the second chamber 18. If the width is smaller than the width β− of the chamber 18, the maximum torque generated in the first chamber 17 can be made smaller than the maximum torque generated in the second chamber 18.
[0041]
The area of the first pressure receiving surface 24 and the area of the second pressure receiving surface 27 are made different from each other, or the number of the first blades 22 and the second blades 24 is made different from each other. Even if the total areas are different, different maximum torques can be easily obtained in the two chambers 17 and 18.
In addition, the maximum torque in the counterclockwise direction and the maximum torque in the clockwise direction can be made equal to or different from each other by various methods.
[0042]
In the first configuration example of the present invention described above, a valve body having the same function as the function of the first valve body 23 described above is provided at the distal end portion of the stopper wall 21 located in the first chamber 17, and the second valve body Even if a valve body having the same function as that described above is provided at the tip of the stopper wall 21 located in the second chamber 18, the magnitude of the maximum torque generated in both the chambers 17 and 18 can be designed freely. .
[0043]
Next, a second configuration example of the rotary damper according to the present invention will be described. FIG. 13 shows a cross-sectional view of a second configuration example of the present invention corresponding to FIG. 2 in the first configuration example. In addition, the same code | symbol is attached | subjected to the component same as a 1st structural example.
[0044]
As shown in FIG. 13, the second configuration example of the present invention includes the third torque control means in the first chamber 17 of the rotary damper of the first configuration example described above, and the fourth torque control means in the second chamber 18. It is characterized by having. In FIG. 13A, as the third torque control means, a groove 28 is provided along the circumferential direction on the outer peripheral surface of the first base 19 located in the first chamber 17. In FIG. 13B, a groove 29 is provided along the circumferential direction on the outer peripheral surface of the second base portion 20 located in the second chamber 18 as the fourth torque control means. Grooves corresponding to the grooves 28 and 29 may be provided on the circumferential surface of the fluid chamber of the casing 2 where the chambers 17 and 18 are located.
The grooves 28 and 29 have their respective high torque or low torque generation regions in the chambers 17 and 18 determined by their locations and lengths provided along the circumferential direction of the bases 19 and 20. The magnitude of the torque generated in each of the chambers 17 and 18 is determined by the width and depth.
[0045]
As shown in FIG. 13 (a), the groove 28 is approximately 180 around the axis of the rotating member in the clockwise direction with the outer peripheral surface of the first base 19 on the side opposite to the first pressure receiving surface 24 of the first blade 22 as the starting end. The groove depth is engraved at an open angle of °. On the other hand, as shown in FIG. 13B, the groove 29 is centered on the axis of the rotating member in the counterclockwise direction starting from the outer peripheral surface of the second base portion 20 on the side opposite to the second pressure receiving surface 27 of the second blade 25. The groove depth is constant and the same depth as that of the groove 28 at an open angle of about 180 °.
[0046]
Next, the operation of the third and fourth torque control means configured as described above will be described with reference to FIGS. First, as shown in FIG. 14, the case where the rotating member 4 rotates counterclockwise (arrow direction) will be described.
[0047]
When the rotating member 4 rotates counterclockwise (arrow direction) and enters the state shown in FIG. 14 (1), the first pressure receiving surface 24 receives resistance from the viscous fluid charged in the first chamber 17, and The valve body 23 rotates clockwise on the first blade 22 (the direction opposite to the arrow direction), and the outer surface of the first valve body 23 on the counter-rotating direction side is the inside of the casing 2 of the first fluid chamber 17. Touch the surface. Further, when the rotating member 4 rotates counterclockwise (arrow direction), the viscous fluid is pushed by the first pressure receiving surface 24 as shown in FIGS. It flows in the direction of the arrow through a fluid passage 30 formed between the groove 28 formed in the base 19. At this time, the 1st blade | wing 22 and the 1st valve body 23 rotate smoothly, without receiving big resistance. Since the end of the groove 28 reaches the side surface at the tip of the stopper wall 21 of the first chamber 17 and the fluid passage 30 is closed, the flow of the viscous fluid is ensured. Then, low torque is maintained.
[0048]
When the rotating member 4 rotates to the state shown between FIGS. 14 (2) and 14 (3), that is, the angle at which the fluid passage 30 is closed, the first blade 22 and the first valve body 23 are suddenly subjected to a large resistance. Therefore, high torque is obtained in the first chamber 17.
[0049]
On the other hand, as shown in FIGS. 14 (1) to (3), the inner circumference of the casing 2 of the second chamber 18 in the full rotation stroke of the second blade 25 and the second valve body 26 in the counterclockwise direction (arrow direction). At least one fluid passage 31, 31 ′ is formed between the surface and the second valve body 26 and between the stopper wall 21 and the groove 28 formed in the second base 20. Therefore, the viscous fluid flows in the direction of the arrow through the fluid passages 31 and 31 ′. Therefore, in the second chamber 18, a state where there is almost no damper action, that is, a low torque is maintained.
[0050]
Next, as shown in FIG. 15, the case where the rotating member 4 rotates clockwise (arrow direction) will be described.
When the rotating member 4 rotates clockwise (in the direction of the arrow), the third torque control means of the first chamber 17 and the fourth torque control means of the second chamber 18 have the above-described case where the rotating member 4 rotates counterclockwise. Operates in reverse. Therefore, the torque of the first chamber 17 is maintained from low to low to low over the entire angle range of the rotating member 4, while the torque of the second chamber changes from low to low to high.
[0051]
As described above, the rotary damper of the present invention composed of the two damper chambers 17 and 18 that operate independently of each other generally has a rotation angle when the rotary member 4 of the second configuration example rotates counterclockwise. When the damper torque is changed from low to low to high according to the range and the rotating member 4 rotates in the clockwise direction, the damper torque can be changed from low to low to high according to the rotation angle range.
[0052]
FIG. 16 (1) shows a torque diagram generated by the above-described first configuration example of the present invention. Furthermore, the rotational torque of the present invention can be obtained by making the lengths of the grooves 28 and 29 of the second configuration example, the engraving locations, the widths and the depths of the grooves different from each other. As shown in FIGS. 16 (2) to (5), the generated torque levels Ta and Tb in the counterclockwise and clockwise rotation strokes of 25 are angles of counterclockwise rotation and clockwise rotation of the rotating member 4, as shown in FIGS. High or low torque can be generated freely according to the range.
[0053]
For example, according to the torque diagram in FIG. 16 (2), high torques having substantially the same magnitude can be generated in the start and end regions of the rotation stroke of the blades in the counterclockwise and clockwise directions. is there. According to the torque diagram of FIG. 16 (3), different torques can be generated in the end regions of the counterclockwise and clockwise rotation strokes. According to the torque diagram of FIG. 16 (4), the high torque region can be overlapped in the end region of the counterclockwise and clockwise rotation strokes. According to the torque diagram of FIG. 16 (5), substantially the same high torque can be generated in the start end region of the counterclockwise and clockwise rotation strokes.
[0054]
However, the rotary damper of the present invention is not limited to the example of the torque diagram, and any combination of the length, location, width, and depth of the grooves 28 and 29 that are engraved is possible. Thus, the magnitude of other generated torque and the generation area of the high, medium or low torque can be changed.
[0055]
Next, a third configuration example of the rotary damper according to the present invention will be described. FIG. 17 shows the structure of the partition wall 16 of the present invention, FIG. 17 (1) shows the front thereof, and FIG. 17 (2) shows its cross section. FIG. 18 shows a longitudinal section in a state where the partition wall 16 is mounted in the fluid chamber 3 of the casing 2.
[0056]
As shown in FIG. 17, the partition wall 16 of the present invention is provided with a wall 16 for facilitating the oil injection into the first and second chambers during the assembly of the rotary damper and the air bleeding after the assembly. An oil communication hole 32 was provided on the surface. The communication hole 32 must be cut out in the partition wall 16 in the angular range b that does not hinder torque generation regardless of whether the rotating member 4 rotates counterclockwise or clockwise. That is, as shown in FIG. 19, it is appropriate to open the hole 32 in a portion a in an angular region where the low torque region overlaps when the rotating member 4 rotates counterclockwise and clockwise.
[0057]
Next, a fourth configuration example of the rotary damper according to the present invention will be described. FIG. 20 (1) shows a rotary damper having a structure different from that of the partition wall 16 of the present invention in a longitudinal section, and FIG. 20 (2) shows a section along the line AA. In the partition wall of this configuration example, a pair of walls 33, 33 extending in the axial direction of the rotating member 4 are formed on the inner peripheral surface of the fluid chamber 3 of the casing 2 instead of the partition wall 16. . The fluid chamber 3 is partitioned into a first chamber 34 and a second chamber 35 through the partition walls 33 and 33 and is arranged in parallel in the radial direction. The first blade and the first valve body are integrated to form a first pressure receiving surface 38 on one side, and the second blade and the second valve body are integrated to form a second pressure receiving surface 39 on one side. To do. Further, the first pressure receiving surface 38 and the second pressure receiving surface 39 are opposite to the rotation direction.
[0058]
The rotary damper of the present invention including the partition walls 33 and 33 has an advantage that the damper chamber width can be further reduced as compared with the rotary damper of the first configuration example including the partition wall 16. However, the rotational stroke of the blades provided along the axial direction on a part of the outer peripheral surface of each of the base portions 5 located in the first chamber 34 and the second chamber 35 is larger than that of the rotary damper of the first configuration example. Get smaller.
[0059]
As shown in FIG. 20, in this configuration example, as the third torque control means and the fourth torque control means, grooves are formed in the fluid chamber circumferential surface of the casing 2 located in the first chamber 34 and the second chamber 35, respectively. 36 and 37 are provided. Further, in this configuration example, the inner diameters of the damper chambers 34 and 35 are made different from each other, so that the maximum torque generated in both chambers is different.
[0060]
FIG. 21 shows an example in which the damper chambers 34 and 35 have different widths (depths), FIG. 20 (1) shows a longitudinal section thereof, and FIG. 20 (2) shows an AA line in FIG. 20 (1). The cross section along is shown. In this embodiment, since the widths of the damper chambers 34 and 35 are different from each other, the maximum torque generated in both chambers is different.
[0061]
【The invention's effect】
As described above, according to the first configuration example, the rotary damper of the present invention can freely change the maximum torque generated when the rotating member 4 rotates counterclockwise and clockwise, independently of each other. According to the example, there is an effect that the changed torque generation region can be freely set independently of each other. Furthermore, according to the third configuration example, the rotary damper of the present invention facilitates oil injection when assembling the rotary damper of the present invention including the first chamber and the second chamber, and facilitates air bleeding after assembly. It has the effect. Further, the rotary damper according to the present invention has the effect that the damper device can be reduced in size, and according to the fourth configuration example, the size can be further reduced.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view showing a rotary damper according to a first configuration example of the present invention.
2 is a cross-sectional view taken along line AA in FIG. 1, and FIG. 2B is a cross-sectional view taken along line BB.
FIG. 3 is a longitudinal sectional view showing a modified example of the torque generating means of the first configuration example.
4 is a cross-sectional view of FIG. 3, in which (a) is a cross-sectional view taken along line AA, and (b) is a cross-sectional view taken along line BB.
FIG. 5 is a longitudinal sectional view showing another modified example of the torque generating means of the first configuration example.
6 is a cross-sectional view taken along line AA in FIG. 5, and FIG. 6B is a cross-sectional view taken along line BB.
FIG. 7 is a longitudinal sectional view showing another modified example of the torque generating means of the first configuration example.
8 is a cross-sectional view taken along line AA in FIG. 7, and FIG. 8B is a cross-sectional view taken along line BB.
FIG. 9 is a longitudinal sectional view showing another modification of the torque generating means of the first configuration example.
10 is a cross-sectional view taken along the line AA in the cross-sectional view of FIG. 9; (b) is sectional drawing which follows the BB line.
FIG. 11 is a longitudinal sectional view showing another modified example of the torque generating means of the first configuration example.
12 is a cross-sectional view taken along line AA in FIG. 11, and FIG. 12B is a cross-sectional view taken along line BB.
FIG. 13 is a cross-sectional view showing a rotary damper according to a second configuration example of the present invention.
FIG. 14 is a cross-sectional view showing an operation when the torque control means of the second configuration example is rotated counterclockwise.
FIG. 15 is a cross-sectional view showing an operation when the torque control means of the second configuration example is rotated clockwise.
FIG. 16 is a torque diagram generated by the torque generating means of the first configuration example, (1) is a torque diagram generated by the torque generating means of the first configuration example, and (2) to (5) are second configurations. A torque diagram generated by an example torque generating means.
FIGS. 17A and 17B are a front view and a cross-sectional view showing a partition wall provided in a rotary damper according to a third configuration example of the present invention. FIGS.
FIG. 18 is a longitudinal sectional view showing a rotary damper according to a third configuration example of the present invention.
FIG. 19 is a torque diagram according to a third configuration example.
FIGS. 20A and 20B are cross-sectional views showing a rotary damper according to a fourth configuration example of the present invention, in which FIG. 20A is a vertical cross-sectional view, and FIG. 20B is a cross-sectional view taken along line AA in FIG.
FIG. 21 is a cross-sectional view showing a modified example of the fourth configuration example, (2) is a cross-sectional view taken along line AA in (1).
FIG. 22 is a cross-sectional view of a conventional rotary damper.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Rotary damper, 2 ... Casing, 3 ... Fluid chamber, 4 ... Rotating member, 5 ... Base part, 6 ... Shaft part, 7 ... End part of casing, 8 ... Bearing convex part, 9 ... Opening end part of casing, 10 DESCRIPTION OF SYMBOLS ... Pressure partition, 11 ... O-ring, 12 ... End cap, 13 ... Bush, 14, 15 ... Bearing opening, 16 ... Partition wall, 16 '... Partition wall flange, 17 ... First chamber, 18 ... Second chamber, DESCRIPTION OF SYMBOLS 19 ... 1st base part, 20 ... 2nd base part, 21 ... Stopper wall, 22 ... 1st blade | wing, 22 '... Flat part of 1st blade | wing, 23 ... 1st valve body, 23' ... Flat part of 1st valve body 24 ... first pressure receiving surface, 25 ... second blade, 25 '... flat portion of the second blade, 26 ... second valve body, 27 ... second pressure receiving surface, 28, 29 ... groove, 30, 30', 31 , 31 '... fluid passage, 32 ... communication hole, 33 ... partition wall, 34 ... first chamber, 35 ... second chamber, 36, 37 ... groove, 38 ... first pressure receiving pressure , 39 ... the second pressure receiving surface.

Claims

A casing having a fluid chamber filled with fluid; a base portion accommodated in the fluid chamber; and a shaft portion projecting outside the fluid chamber; a rotating member that is rotatable relative to the casing; and provided in the casing. In a rotary damper having a stopper wall that limits a rotation angle of the rotating member in the fluid chamber, and a torque generating means that generates torque in cooperation with the stopper wall at the time of relative rotation of the rotating member,
The casing includes a partition wall that divides the fluid chamber into a first chamber and a second chamber,
The rotating member has a first base located in the first chamber and a second base located in the second chamber so as to rotate integrally, and the first base is formed on the outer peripheral surface of the first chamber. First torque generating means for generating torque in the first chamber when the rotating member rotates in the first direction, comprising at least one first blade projecting radially to the inner peripheral surface of the casing ; The two base portions are composed of at least one second blade protruding radially on the outer peripheral surface to the inner peripheral surface of the casing of the second chamber, and the rotation member rotates in the second direction opposite to the first direction. A second torque generating means for generating torque in the second chamber sometimes,
The rotary damper includes a first torque control unit configured to reduce a generated torque in the first chamber as compared with a torque generated when the rotating member rotates in the second direction, when rotating in the first direction; A second torque control means for reducing the generated torque in the second chamber as compared with the torque generated when rotating in the second direction when the rotating member rotates in the first direction;
The rotary damper further controls a generation region of high torque or low torque generated during a rotation stroke of the first blade in the first chamber when the rotary member rotates in the first direction. Control means, and fourth torque control means for controlling a generation region of high torque or low torque generated during a rotation stroke of the second blade in the second chamber when the rotating member rotates in the second direction. the provided, and the third torque control means and fourth torque control means, the rotary damper, wherein that you have generated region of high torque or low torque is in a phase different between the first and second chambers .

The first chamber and the second chamber are formed to have substantially the same volume, and the maximum torque generated by the first torque generating means in the first chamber when the rotating member rotates in the first direction; The rotary damper according to claim 1, wherein the maximum torque generated by the second torque generating means in the second chamber when the rotating member rotates in the second direction is substantially equal.

The first blade has a first pressure receiving surface that receives the resistance of the fluid in the first chamber when the rotating member rotates in the first direction, and the second blade moves in the second direction of the rotating member. The second pressure receiving surface that receives the resistance of the fluid in the second chamber during rotation, and the area of the first pressure receiving surface is substantially equal to the area of the second pressure receiving surface. Rotating damper.

The first chamber and the second chamber are formed to have different volumes, and the maximum torque generated by the first torque generating means in the first chamber when the rotating member rotates in the first direction; 2. The rotary damper according to claim 1, wherein a maximum torque generated by the second torque generating means in the second chamber when the rotary member rotates in the second direction is made different from one another.

The first blade has a first pressure receiving surface that receives the resistance of the fluid in the first chamber when the rotating member rotates in the first direction, and the second blade moves in the second direction of the rotating member. The first pressure receiving surface is configured to have a second pressure receiving surface that receives the resistance of the fluid in the second chamber during rotation, and the area of the first pressure receiving surface is different from the area of the second pressure receiving surface. The described rotary damper.

6. The rotary damper according to claim 5, wherein the number of the first blades of the first torque generating means and the number of the second blades of the second torque generating means are different.

The first torque control means includes a first valve body provided between a tip end of the first blade and an inner peripheral surface of the first chamber, and the first valve body is the second valve body of the rotating member. A fluid passage is opened during rotation in the direction, and the second torque control means comprises a second valve body provided between the tip of the second blade and the inner peripheral surface of the second chamber, 2 valve body rotary damper according to claim 1 to 6, characterized in that opening the fluid passage during rotation to said first direction of said rotary member.

The first torque control means includes a third valve body provided between the tip of a first stopper wall formed on the inner peripheral surface of the first chamber and the outer peripheral surface of the first base portion of the rotating member. The third valve body opens a fluid passage when the rotating member rotates in the second direction, and the second torque control means includes a second stopper wall formed on an inner peripheral surface of the second chamber. It comprises a fourth valve body provided between the tip and the outer peripheral surface of the second base portion of the rotating member, and the fourth valve body opens a fluid passage when the rotating member rotates in the first direction. The rotary damper according to claim 1 .

The third torque control means also controls the level of torque generated during the rotation stroke of the first blade in the first chamber when the rotating member rotates in the first direction, and the fourth torque control means, during rotation of the second direction of said rotary member, according to claim 1, characterized in that also controls the level of torque generated during rotation stroke of said second blades in the second chamber Rotating damper.

The third torque control means comprises a groove formed along a circumferential direction on at least a part of a wall surface defining the first chamber or an outer peripheral surface of the first base, and the fourth torque control means comprises: 2. The rotary damper according to claim 1 , comprising a groove formed along a circumferential direction on at least a part of a wall surface defining the second chamber or an outer peripheral surface of the second base portion of the rotary member. .

The rotation according to any one of claims 1 to 10 , wherein the first chamber and the second chamber are connected to each other via the partition wall extending in a direction crossing a central axis of the casing. damper.

The rotary damper according to claim 11 , wherein a fluid communication path is formed in the partition wall.

The first chamber and the rotary damper according to any one of claims 1 to 10 and the second chamber, characterized in that it is arranged through the partition wall extending in the axial direction of the rotary member.