TW200905102A - Damper - Google Patents

Damper Download PDF

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Publication number
TW200905102A
TW200905102A TW097106415A TW97106415A TW200905102A TW 200905102 A TW200905102 A TW 200905102A TW 097106415 A TW097106415 A TW 097106415A TW 97106415 A TW97106415 A TW 97106415A TW 200905102 A TW200905102 A TW 200905102A
Authority
TW
Taiwan
Prior art keywords
rotor
damper
flow path
rotation
liquid chamber
Prior art date
Application number
TW097106415A
Other languages
Chinese (zh)
Inventor
Aiko Inaba
Motoharu Takai
Original Assignee
Nifco Inc
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 Nifco Inc filed Critical Nifco Inc
Publication of TW200905102A publication Critical patent/TW200905102A/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/005—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper
    • F16F13/007—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper the damper being a fluid damper
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

A damper of which the torque exerting upon rotor is variable in response to the rotation speed of the rotor is obtained. Since the space S formed by a trochoid gear portion 16 and a trochoid gear portion 18 of inner member 20 is communicated through a circular groove 58 of plate 30 to make silicon oil flowable, the compression resistance is therefore reduced, and the torque exerting upon the rotor 22 and the damping force from the damper 10 are reduced accordingly. On the other hand, at the time when the plate 30 is rotated, one end of the circular groove 58 is blocked, and the communication state between neighboring spaces S is shut off, then the compression resistance of silicon oil within the space S, the torque exerting upon the rotor 22 and the damping force from the damper 10 become greater. That is, the torque exerting upon the rotor 22 is variable in response to the rotation speed of the rotor 22.

Description

200905102 九、發明說明： 【發明所屬之技術領域】 本發明係有關一種使轉矩作用於轉子之阻尼器。 【先前技術】 當於拉門或抽屜等移動體使用用以制動該移動體之阻 尼器時，係設成移動體不會以超過需要的速度來急速移 例如在專例文獻1中，係藉由與旋轉軸一起旋轉的閥 (valve)構件的旋轉方向來改變黏性流體的通路，藉此調整 作用於旋轉軸之轉矩。 正 ^此外，在專利文獻2中，將辅助室與轉矩產生室分開 叹置，藉由旋轉軸的旋轉方向將配置於轉矩產生室與辅助 =間的板彈簧予以開閉而進行流量調整，以使作用、 轉軸的轉矩改變。 的卩’專利文獻1與專利文獻2係#由旋轉軸（轉子） 作轉矩’並非對應轉子的旋轉速度來改變 專利文獻1 : 專利文獻2 : 【發明内容】 日本特開平10-1 15338號公報 日本特開2000-1 99536號公報 慮到上述情事，而提供—種對應轉 於轉子之轉矩改變的阻尼器。 (發明所欲解決之課題） 本發明的課題係考 子的旋轉速度來使作用 (解決課題的手段） 係在阻尼器中具備有： 申請專利範圍帛1項之發明 319958 5 200905102 • ::::液體室，設置於前述外殼内，並填充有黏性 可旋轉之方式收容於前述外殼内，並承 :::::液體室的黏性流體的阻力；以及流通路徑可變 ^，虽别述旋轉體的旋轉速度達預定值以上時，將前述 成為非連通狀態，而當前述旋轉體= 、又^未相定值時，將液體室彼此_成為連通狀態。 右逢^請專利範圍第1項之發明中，在外殼内設置填充 =性ί體的複數個液體室。此外，在外殼内以可旋轉之 體:::碇轉體，該旋轉體係承受來自液體室内的黏性流 j著，當旋轉體的旋轉速度變成預定值以上時，藉由 ^徑可變手段使液體室彼此間成為非連通狀態。藉 阻力體室t ’除了旋轉體攪拌黏性流體所產生的黏性 間所甚Γ及ί旋轉體旋轉時未受擾拌的黏性流體與旋轉體 體所、4的男切阻力之外，並產生在液體室内壓縮黏性流 成的I縮阻力，而增大作用於旋轉體之轉矩，故阻 匕裔所提供的減震力會變大。 接著，當旋轉體的旋轉速度變成未達預定值時，藉由 :二徑可變手段使液體室彼此間形成為連通狀態。藉 液體室中’會降低在該液體室内愿縮黏性流體時 縮阻力(亦包含幾乎無星縮阻力的情形)，並降低 、旋轉體之轉矩’故阻尼器所提供的減震力會變小。 體的依據申請專利範圍第1項之發明，能根據旋轉 還的％轉速度來改變作用於旋轉體之轉矩。 319958 6 200905102 第ι:=:Γ第2項之發明，係在前述申請專利範圍 器中，前述旋轉體具備有:轉子，傳 轉力，以及偏心構件，相對於前述轉子 i偏心旋轉，且在與前述外殼之間構成前述液體室.且、 _通路徑可變手段，且， 斷構件，者俞、+、喆7 ^弟机通路徑遮 “…專子的旋轉速度達預定值以上時，藉由在 二轉子^產生的剪力或黏性流體的流動力 :述液體室彼此間形成為非連通狀態;以及 = 第-产通^ 通路徑遮斷構件，並將該 :彈;=遞斷構件朝與前述轉子的旋轉方向相反的方 =推’虽轉子的旋轉速度變成未達預定值時，使第一流 通路徑遮斷構件返θ $膝义、+…六μ ^ ’丨l 態的位置。室彼此間形成為連通狀 子，專利範圍第2項之發明中，於旋轉體具備有轉 ::::用以傳達來自外部的旋轉力。在該轉子設置 件，在盘外 芯偏心旋轉之偏心構件，藉由該偏心構 件在與外殼之間構成液體室。 dr且尼器設置有第一流通路徑遮斷構件，其係 ==轉速度達預定值以上時，會藉由與該轉子間所 =的二力或黏性流體的流動力而旋轉，並藉由該第一流 路禮遮㈣件將液體室彼此間形成為非連通狀能。 ，第-流通路徑遮斷構件連結有第一彈推手段，用以 流通路徑遮斷構件朝與轉子的旋轉方向相反的方 推。而且，當轉子的旋轉速度變成未達預定值時，藉 319958 7 200905102 形成=通=第路構件將液體室彼此間 產味萚士# 猎由偏〜構件的旋轉，在液體室中會 在偏：：：構件咖性流體所產生的黏性阻力、以及 生轉時未受㈣的黏性流體與偏心構件間所產 當轉子的旋轉速度達預定值以上時，在盘轉子 ^斤產力或黏性流體的流動力會變得比第一彈推手 轉。藉此遮斷構件會旋 體至彼此間會成為非連通狀態。 因此，在液體室内’除了雜流體所造成的黏性阻力 :了維力之外’還附加有由偏心構件的旋轉而在液趙室 =rr產生的壓縮阻力。如此，作 θ ^大’故阻尼器所提供的減震力會變大。 石I轉子的旋轉逮度變成未達預定值時，在與轉 曰 的剪力或黏性流體的流動力會變得比第一彈推 的彈推力還小，第—彈推手段會恢復原狀。藉此， 二斷構件會返回原本的位置，液體室彼此間 m在液體室内’黏性流體所造成的 二1二減少，作用於轉子之轉矩降低，故由阻尼器所 提供的減展力會變小。 申請專利li 15第3項之發明，係在專利範 ㈣以㈣’前述偏心構件具有第—餘擺線（tr〇ch〇id) 319958 8 200905102 Γ二=外殼的内周面形成與前述第-餘擺線齒形 部斑义.十…—矛'擺線齒形部’並藉由前述第-餘擺線齒形 σ /、述弟二餘擺線齒形部構成前述液體室。 餘：==:::=广'構件具有第- 形部嚙人㈣周面形成與前述第-餘擺線齒 而1: 擺線齒形部’藉由因偏心構件的旋轉， 餘餘擺線齒形部移動時所產生的黏性阻力、在第一 形部的齒部移動時未受細黏性流體與丄 ❺剪切阻力、以及在第一餘擺線齒形部 二齒形部的齒部的過程中第二餘擺線齒= 於轉子之轉矩Γ體被壓縮所產生的壓縮阻力’可產生作用 項所範㈣4項之發明，係在申請專利範圍第1 ' ，且尼裔中，前述旋轉體係具備有：轉子，傳、聿 來自外部的旋轉力；移動構件，配 達 4 i. 並在與前述外殼之門禮m ;别述轉子的外侧， 一構成則述液體室；以及凸輪手段，你 二：之方：凝轉力變換成沿著前述移動構件的該轉子的軸 方方向移動；其中，前述流通路徑可變 二 述構成而構成者：第二流通路； :峨度變成預定值以上時，會藉二 轉：將_體室彼此間形== 構件，並將推2路係連結至前述第二流通路徑遮斷 方…= 遮斷構件朝與前述轉子的_ 相反的方向彈推’當轉子的旋轉速度變成未達= 319958 9 200905102 -%·，第二流通路徑遮 形成為連通狀態的位置。a回至使前述液體室彼此間 在申請專利範園第4 以傳達來自外部的旋轉力、：發明中’於旋轉體具備有用 動構件，且藉由該移並於該轉子外側設置移 接著，藉由凸輪手 ，在與外殼之間構成液體室。 構件的該轉子：軸二將轉子的旋轉力變換成朝沿著移動 寻：的軸方向之方向直線移動。 如此’猎由將轉子的旋轉移動變換 移動’即能對應轉子的^ ㈣什的直線 亦即，的移動I來增加移動構件的移動量。 P此增大作用於轉子之轉矩。 二谅、甫L於t尼益設置有第二流通路徑遮斷構件，該第 時:牛係當轉子的旋轉速度達預定值以上 藉由在與該轉子間所產生的剪力而旋轉，且藉由該 路徑遮斷構件將液體室彼此間形成為非連通狀 ς、:-流通路徑遮斷構件連結有第二彈推手段，係將 通路徑遮斷構件朝與轉子的旋轉方向相反的方向 推而★，t轉子的旋轉速度未達預定值時，#由第二彈 奴，第二流通路徑遮斷構件會返回至將液體室）皮此間 艰成為連通狀態的位置。 形如此，當藉由第二流通路徑遮斷構件將液體室彼此間 :成為連通狀態時’藉由移動構件的移動，在液體室内會 生移動構件攪拌黏性流體所產生的黏性阻力、以及在移 動構件移動時未受料的黏性流體與移動構件間產 切阻力。 力 319958 10 200905102 接著’當轉子的旋轉速度達預定值以上時，在與該轉 子間所產生的剪力會變得比第二彈推手段所產生的彈推力 還大，故第二流通路徑遮斷構件會旋轉。藉此，液體室彼 此間會變成非連通狀態。因此，在液體室内，除了黏性流 體所造成的黏性阻力與剪切阻力之外，還附加因移動構： 的移動而在液體室㈣縮黏性流體所產生的I缩阻力。因 此，作用於轉子之轉矩會增大，故阻尼器所提供的減震力 會變大。 接著，當轉子的旋轉速度變成未達預定值時，在與轉 子間所產生的剪力會變得比第二彈推手段所產生的推 运小’故第二彈推手段會恢復原狀。藉此，第二流通路徑 ，斷構件會返回原本的位置，液體室彼此間會變成連通^ 悲。因此，在液體室内，黏性流體所造成的壓縮阻力合減 知作用於轉子之轉矩會降低，故阻尼器所造成的^力 申請專利範圍第5項之發明，係在申請專·圍第4 項所記載的阻尼H中，前卿動構件係設置錢前述外殼 ^壁Ϊ出’且可於用以界定前述液體室之柱材之間上下 =別述凸輪手段係包含有下述構件而構成者：波狀的 =溝’㈣於前述轉子的外周面，錄該轉子的轴方向 ，、有波峰和波谷m合突起，設置於前述移動構件， 用以與前述凸輪溝嵌合。 動構件 在申請專利範圍第5項之發明中，俜將 成從外殼的内壁突出，i可μ 移動構件設置 土大出亚可於用以界定液體室的柱材間上 319958 11 200905102 ::動。並且，於轉子的外周面形成波狀的凸輪溝，該波 、凸輪溝係於該轉子的軸方向具有波峰與波谷，且於， ==置有用以與該凸輪溝嵌合之嵌合突起 當‘ 十0者轉子的軸方向移動。 項或利範圍第6項之發明，係在申請專利範圍第4 二之Π阻尼器中，前述移動構件係以彼此錯開相位 動之方式，冑前述嵌合突起嵌合至前$凸輪溝。 在申請專利範圍第6項之發明中 彼此錯開相位來移動，且各移：二广動構件係作成 ㈣且各移動構件在液體室内的位置不 :二此，能改變於每個液體室所產生的轉矩，而可平順 地乓減作用於轉子之轉矩。 、 申3奢專利範圍第7 jg > I ,, 項的阻尼器中，前述旋轉二:在::== 搖動構件，在中心軸傾斜的狀態t = 動.乃由〜偏、亚予以連結，且藉由該轉子的旋轉而搖 °又置於刚述搖動構件，並在與前述外 二：構：：述液體室，且藉由前述搖動構件的搖動而來 = 路徑可變手段係包含下述構件而 k路彳工遮斷構件，係當前述轉子的旋轉速 度達預定值以上時，合鹑士 —如# 付、 + θ糟由在與该轉子間所產生的剪力而 二m此間形成為非連通狀態；以及第三 三产通路於則述第三流通路徑遮斷構件，並將第 Μ 斷構件朝與前述轉子的旋轉方向相反的方向 319958 12 200905102 ，推田轉子的旋轉逮度未達預定值時，使第三汽通 ί斷構件相至將前述液體室彼此間形成為連通狀態的Γ _在=::=:轉之:明中’於旋轉體具備有用 ,v . , y ^疋轉力之轉子，且設置有搖動構件，用 二由頃斜的狀態下相對於該轉子的轴芯偏心並予以 該搖：的搖==::_動，但_ 動。在該活塞構件舆;殼置::::^ 移動如:對f===動變換成活塞構件的來回 即，能使作用於轉子加活塞構件的移動量 兮 尼器中’设置有第三流通路徑遮斷構件， 構件係當轉子的旋轉速度變成預定值 由#第—士 一該轉子間所產生的剪力而旋轉，且藉 、甬：ΪΤ:?徑遮斷構件，將液體室彼此間形成為非連 it將二第」t — *通路徑遮斷構件連結有第三彈推手段， 通路徑遮斷構件朝與轉子的旋轉方向相反的 第當轉子的旋轉速度未達預定值時，藉由 讀形=::::徑遮斷構件…將液體室 ^ 11#^通路徑遮斷構件使液體室彼此間 =生:舌夷2態時’藉由活塞構件的移動，在液體室内會 產生活基構件授拌黏性流體所產生的黏性阻力、以及在活 319958 13 200905102 ，塞構件移動時未受攪拌的黏性流體與活塞構件間產生的剪 切阻力。 、^ 接著’當轉子的旋轉速度達預定值以上時，在與該轉 ^間所產生的剪力會變得比第三彈推手段所產生的彈推力 還大，故第三流通路徑遮斷構件會旋轉。藉此，液體室彼 此間會變成非連通狀態。因此，在液體室内，除了黏性流 體所造成的黏性阻力與剪切阻力之外，還附加因活塞構: 的移動而在液體室内壓縮黏性流體所造成的壓縮阻二。因 ^作用於轉子之轉矩會增大，故阻尼器所提供的減震力 會變大。 接著，當轉子的旋轉速度變成未達預定值時，在 子間所產生的剪力會變得比第三彈推手推 還小，故第三彈推手段會恢復原狀。藉 = r:r:回原本的位置，液體室彼此間會; i. :變:用於轉子之轉矩會降低，故阻尼器所提供的減= 申請第8項之發明，係在阻尼 外喊；禝數個液體室，嗖晋於义 、備有. Μ = 於則述外殼内’且填充有黏性 :體，.:子’傳達來自外部的旋轉力，並以轉 收容於前述外殼内，且承受 疋I之方式 阻力，·旋轉構件’具有與前述轉子：同'-室：黏性流體的 轉子的旋轉力；導引突起，㈣:义由心且傳達該 芯錯開位置，·搖動體，係 U述旋轉構件的軸 屯成有與两述導亨/突起族合之直 319958 200905102 Ά rl' V 51 Μ且藉由導引突起的移動而在前述液體室内搖 動，減壓流通路徑，係沿著前述搖動體的移動方向而設置 於搖動體’ J_將該搖動體置於其帛，使大致分離的液體室 f為連通狀態；以及閉塞構件，係設置於前述搖動體，當 月!述轉子的旋轉速度達預定值以上時，藉由前述黏性流體 所造成的黏性阻力而移動來閉塞前述減壓流通路徑。 在申請專利範圍第8項之發明中，於外殼内設置填充 有·的複數個液體室。於外殼内收容有可旋轉的轉 子’該轉子係承受來自液體室内的黏性流體的阻力。並且， 在外殼内設置有旋轉構件，係具有與轉子不同的軸芯，且 傳達該轉子的旋轉力，並設置有從該旋轉構件的軸芯錯開 位置的導引突起。 另一方面，在液體室内設置有可搖動的搖動體，於該 =動體形成與導引突起嵌合的直線狀導引溝，藉由旋轉構 搖：旋轉使導引突起旋轉移動，藉此透過導引溝使搖動體 動 能 如此，藉由將轉子的旋轉移動變換成搖動體的搖動移 而能對應轉子的移動4來增加搖動體的移動量 增大作用於轉子之轉矩。 7 此外，沿著搖動體的移動方向，在搖動體設置 ::路：，將該搖動體置於其間’藉由該減屢流通路; 大致勿離的液體室成為連通狀態。此外，於 工 閉塞構件：該閉塞構件係當轉子的旋轉速度變成：:：有 上時’會藉由黏性流體所造成的黏性阻力而移動 ^ 精由 319958 15 200905102 該閉塞構件的移動來閉塞減麼流通路徑。 、s壯='#由減㈣通路徑使㈣室彼此卿成為連 =:、時：藉由搖動體的移動，於液體室内會產生 =性流體時所產生的黏性阻力、以及在搖動體移動時 未叉授拌的黏性流體與搖動體間所產生的剪切阻力。 接著’當轉子的旋轉速度變成預定值以上時，黏性流 體的黏性阻力會增大，閉塞構件會移動。藉此，㈣減壓 流通路徑，將搖動體置於i M i L 、 p…… 使大致分離的液體室彼此 =成非連通狀態。因此，在液體室内，除了黏性流體所 ^的黏性阻力與剪切阻力之外，還附加因搖動體的移動 而在液體室内I縮黏性流體所造成的I縮阻力。因此，作 用於轉:之轉矩會增大，故阻尼器所提供的減震力會變大。 接著’當轉子的旋轉速度變成未達預定值時，由於 性流體所造成的黏性阻力會減少，故閉塞構件會返回原本 的位置’而開放減屢流通路徑’將搖動體置於其間，使大 致分離的液體室彼此間變成連通狀態。因此，在液體室内 黏性流體所造成的I缩阻力會減少，作用於轉子之轉矩會 降低，故阻尼器所提供的減震力會變小。 申請專利範圍第9項之發明，係在t請專利範圍第8 項所記制阻尼H巾，前述㈣體係讀此錯㈣位來移 動之方式，使前述導引突起嵌合前述導引溝。 夕 在申請專利範園第9項之發明中，各搖動體係作 此錯開相位來移動，且各搖動體在液體室内的位置不同。 因此，能改變於每個液體室所產生的轉矩，而可順暢地增 319958 16 200905102 減作用於轉子之轉矩。 (發明效果） 來改發明作成上述構成，故能對應轉子的旋轉速度 术改熒作用於轉子之轉矩。 【實施方式】 接著，說明树明的第—實施形態的阻尼器。 如第1圖至第3岡&- 圓筒狀之有底外於阻尼器1〇具備有作成大致 的開口側作為‘ Λ η為了方便㈣，係將外殼12 : °° 的上側、將底部側作為阻尼器1 0 、 ，來進行各元件的說明。 -，t該外敢12内填充有作為黏性流體时油（以點狀表 1:’。二ti，)。此外，從外殼12底部側的外周面以 於可推广大叹固定片14，且雖未圖示，但係作成可固定 固i部=部内的拉出構件等可相對移動的移動構件被 夕卜’在弟二至第四實施形態中’係未圖示該固 疋方14。 在外殼12的内周面形成具有複數個齒部i6a(在此 八個）的餘擺線（trc)chc)i㈣形部16，餘擺線齒形部二 餘擺線齒形部）16上端面的高度係比外殼12的上端部= 而且，於餘擺線齒形部16的内側配置有中空狀的 構J牛(偏心構件)20,該内部構件2〇係形成有餘擺線齒形; (第2餘擺㈣形）18，其具有與該餘擺線齒形部a的齒 16A嚙合的齒部18A(在此為五個），且餘擺線齒形部丨^勺 319958 17 200905102 齒部1“上端面的高度係稍微低於餘與括4 16A的上端面。 &線齒形部〗6的齒部 在内部構件20的内侧係設成可内插轉子 22係與傳達旋轉力之傳達構件（ ^專子 係大致區分成略圓筒狀的轴部 回不、結。該轉子22 __之間，於軸二 部2 4還大的薄壁狀台座部2 δ。 &置有直禮比軸 f 上面= 子22插入内部構件2〇的狀態下，偏… 致與餘擺線齒形部16的上端面形成大致 板二(第间成可與餘擺線齒形部16 -起抵接後述的 扳肢（第一流通路徑遮斷構件）3〇 Ο 致圓之下端面，與軸部Μ的同軸地凹設有大 =二套合凹部％，其係套合於突設在外U底面 ^的圓柱狀套合凸部3δ。藉此，形成轉子Μ可在 豉12的中心部旋轉。 ，偏心部26的外周面，比軸部24的外徑還突出的大 :放射線狀的複數個肋部4〇係沿著偏心部⑼的軸方向設 置。而該複數個肋部4G的前端面係位於同—圓周上，且偏 :部26的外周面及該肋部4〇的前端面係形成可抵接至内 4構件20的内周面。 …Τ即，内部構件20係以相對於軸部24呈偏心的狀態 :安衣而虽旋轉轉子22時，如第4圖（Α)及（Β)所示，係 错由肋部4G的前端面來推壓内部構件2G，且内部構件2〇 糸在偏〜的狀_下旋轉。此時，餘擺線齒形部Μ係在與外 319958 18 200905102 殼12的餘摇綠| 下沿著該餘擺線齒形 部16的形狀移動^ 16、合的狀‘癌 狀蓋::方係 ::二3圖所广剖面作成大致L字狀的環 蓋部42中央部的孔部44内。。_成可插通於設置在 在0 = t二=的台座部2 8側形成有0形環安裝溝3 2， 琿34:面接:衣於0形環安裝溝32内的狀態下，該0形 部44的内周面。藉此，將在轉子22 不會漏出至外；。生的間隙予以密封’使外殼12内㈣油 此外如第3圖與第5圖所示，於蓋部42的背面且 孔部4 4的外侧凹設有環狀的溝部4 8。並且，隔著孔部4 4， 於溝部4 8的外側凹設有—對圓弧狀㈣合部5 〇。 〃又於盍部42的背面係形成可安裝環狀的板體3〇。如 第所示，從該板體3〇的内緣部凸設有環狀肋部52, 在該環狀肋部52的外側且為板體3〇的同心圓上，隔著環 狀肋部52設置有一對圓弧肋部54。 _ 該圓弧肋部54係在與嵌合部5〇之間於周方向設置有 間隙的狀態下，與該嵌合部5〇嵌合。如第3圖所示，環狀 肋部52係在與溝部48之間設置有間隙的狀態下抵接至該 溝部48的内壁面。 接著，設置在溝部48與環狀肋部52間的間隙係可安 裝扭轉彈箐（torsi〇n spring)(第一彈推手段）56，且扭轉 319958 19 200905102 彈簧56的一端部係安裝在板體3〇，而扭轉彈簧56的另一 端部係安裝在蓋部42。 另一方面，如第5圖所示’在板體3〇的背面侧，沿著 板體30的同心圓上，以預定間隔凹設有六個圓弧溝 連通路)58。如第6圖（A)所示，從平面觀之，該圓弧溝58 之長度係比設置在外殼12的餘擺線齒形部16的齒部 的齒厚還且在餘擺線齒形部16的齒㉛⑽與圓弧溝 58上下重豐的狀態下’圓弧溝58的兩端部會從齒部 的齒面露出。 此外，如第4圖（A)及（B)所示，在將内部構件別配 12内的狀態下’在外殼12的餘擺線齒形部Μ與内 在此二間S内填充矽油（以點狀顯示）。 此’猎由安裝在溝部48與環狀肋部52間的扭轉彈 -56來定位板體3◦的周方向。在此狀態 2 弧肋部54係配罟^ #十板30的圓 Θ圖(TA)新_、 卩2的嵌合部5〇的中央部，且如第 田 不，從平面觀之，圓弧溝58的位置俜對準於 ::線:r部，的齒部-上下"的位置== 面露出/狀態下’圓弧溝58的兩端部會從齒部⑽的齒 ，、即，如第4圖（A)及（β)所示，由 與内部構件？田餘擺線齒形部16 I稱件20的餘擺線齒 圖及第6圖所示，——j W麟工間如第3 之彼此相鄰的空間ς線齒形部18的各會部⑽所隔開 曰1之間係藉由板體3〇的圓弧溝58而成 319958 20 200905102 =連通狀怨。因此，經由該圓弧溝58，⑦ 鄰的空間S!。 爪動於相 另一方面，當藉由抵抗扭轉彈簧％的彈推力之 應力（使板體30正旋轅弋、运#絲AA & +、 向的 4 轉或疋轉的應力）而使板體30的圓 :部54抵接於蓋部42的嵌合部5。的端面時，如= :开^所不，從平面觀之，圓弧溝58的-端側會被餘擺線 齒形口 Ρ 1 6堵塞’而由私把仏土 、'、 開的相鄰的空間&如^ 部18的各齒部18Α所隔 態。 圖（Α)&(Β)所示會變成非連通狀 說明本發明的第—實施形態的阻尼器的作用。 # 1弟4圖（Α)及⑻所示，#轉+ 偏心部26，内邱搂丛〇λ人 付了稽由 轉。藉此，1 :沿著餘擺線齒形部16的形狀旋200905102 IX. Description of the Invention: [Technical Field] The present invention relates to a damper that applies torque to a rotor. [Prior Art] When a damper for braking the moving body is used for a moving body such as a sliding door or a drawer, it is assumed that the moving body does not rapidly move at a speed exceeding a required speed, for example, in the special document 1, The passage of the viscous fluid is changed by the direction of rotation of the valve member that rotates together with the rotating shaft, thereby adjusting the torque acting on the rotating shaft. In addition, in the patent document 2, the auxiliary chamber is separated from the torque generating chamber, and the flow rate is adjusted by opening and closing the leaf spring disposed between the torque generating chamber and the assist= in the rotation direction of the rotating shaft. In order to change the torque of the action and the shaft.专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利 专利In view of the above, Japanese Laid-Open Patent Publication No. 2000-1 99536 provides a damper corresponding to a change in torque to the rotor. (Problems to be Solved by the Invention) The subject of the present invention is to provide a function of the rotation speed of the test piece (a means for solving the problem). The damper is provided with: Patent Application No. 1 Invention 319958 5 200905102 • ::: a liquid chamber disposed in the outer casing and filled in a viscous and rotatable manner in the outer casing, and bearing: :::: resistance of a viscous fluid in the liquid chamber; and a flow path variable ^, though When the rotational speed of the rotating body is equal to or greater than a predetermined value, the above-described non-communication state is obtained, and when the rotating body is equal to or lower than the predetermined value, the liquid chambers are brought into communication with each other. In the invention of the first aspect of the patent scope, a plurality of liquid chambers filled with a body are provided in the outer casing. In addition, in the outer casing, a rotatable body::: a rotating body, the rotating system is subjected to a viscous flow from the liquid chamber, and when the rotating speed of the rotating body becomes a predetermined value or more, the variable diameter means The liquid chambers are brought into a non-connected state with each other. By the resistance body chamber t', in addition to the viscosity of the viscous fluid caused by the rotating body, and the viscous fluid that is not disturbed when the rotating body rotates, and the male resistance of the rotating body, 4 And the I contraction resistance generated by the compressive viscous flow in the liquid chamber is generated, and the torque acting on the rotating body is increased, so that the damping force provided by the descendants of the scorpion is increased. Next, when the rotational speed of the rotating body becomes less than the predetermined value, the liquid chambers are brought into communication with each other by the two-path variable means. By borrowing in the liquid chamber, it will reduce the shrinkage resistance (also including the almost no star-shrinking resistance) when the fluid is forced to shrink in the liquid chamber, and reduce the torque of the rotating body, so the damping force provided by the damper will Become smaller. According to the invention of claim 1, the torque acting on the rotating body can be changed according to the % rotation speed of the rotation. The invention of claim 2, wherein the rotating body is provided with: a rotor, a transmitting force, and an eccentric member, eccentrically rotating with respect to the rotor i, and Between the outer casing and the outer casing, the liquid passage is formed, and the path of the passage is variable, and when the breaking member is blocked by the Yu, +, and ^7^, the rotation speed of the ... By the shear force generated by the two rotors or the flow force of the viscous fluid: the liquid chambers are formed in a non-connected state with each other; and = the first pass-through path intercepting member, and the: bomb; When the breaking member is opposite to the rotation direction of the rotor, the rotation speed of the rotor becomes less than a predetermined value, and the first flow path blocking member is returned to the θ$ knee, +...6 μ ^ '丨l state. In the invention of the second aspect of the patent, the rotating body is provided with a rotation:::: for transmitting a rotational force from the outside. In the rotor setting member, the outer core of the disk is eccentric. Rotating eccentric member by means of the eccentric member The liquid chamber is configured to have a first flow path blocking member, and when the rotation speed is greater than or equal to a predetermined value, the flow force of the two force or viscous fluid between the rotor and the rotor is Rotating, and the liquid chambers are formed into non-connected energy by the first flow path shielding member. The first flow path blocking member is coupled with the first spring pushing means for the flow path blocking member toward The direction of rotation of the rotor is opposite. In addition, when the rotational speed of the rotor becomes less than the predetermined value, the formation of the 319958 7 200905102 = pass = the path member will produce the taste of the liquid chambers between each other. Rotation, in the liquid chamber, the viscous resistance generated by the partial::: component fluid, and the rotational speed of the rotor when the rotational speed of the rotor is not higher than the predetermined value when the viscous fluid and the eccentric member are not subjected to (4) during the rotation. In the rotor of the disk rotor, the flow force of the force or the viscous fluid will become smaller than that of the first bullet. The blocking member will rotate the body to each other and become non-connected. Therefore, in the liquid chamber Viscous drag caused by fluid : In addition to the maintenance force, the compression resistance generated by the rotation of the eccentric member in the liquid chamber = rr is added. Thus, the θ ^ is large, so the damping force provided by the damper becomes large. When the rotation catch becomes less than the predetermined value, the flow force of the shearing force or the viscous fluid with the turning will become smaller than the elastic force of the first bombing, and the first bombing means will return to the original state. The two-breaking member will return to the original position, and the liquid chambers will decrease in the liquid chamber by the viscous fluid, and the torque acting on the rotor will decrease, so the reduction force provided by the damper will become smaller. The invention of the patent li 15 item 3 is based on the patent (4) to (4) 'the aforementioned eccentric member has a trochoidal line (tr〇ch〇id) 319958 8 200905102 Γ2 = inner peripheral surface of the outer casing is formed and the foregoing - The trochoidal tooth profile portion. The tenth - spear 'cycloidal tooth portion' and the liquid chamber is constituted by the aforementioned first trochoidal tooth shape σ /, the second trochoidal tooth profile. I: ==:::=广''s member has a first-shaped part of the indented (four) circumferential surface formed with the aforementioned apex-cycloidal teeth and 1: the cycloidal toothed portion' by the rotation of the eccentric member, the remaining pendulum The viscous resistance generated when the wire tooth portion moves, the shear resistance of the fine fluid and the crucible when the tooth portion of the first portion moves, and the second tooth portion of the tooth portion of the first trochoidal line In the process of the tooth portion, the second trochoidal tooth = the compression resistance generated by the torque of the rotor is compressed, which can produce the four items of the action item (4), which is in the patent application range 1 ', and Among the above-mentioned rotating systems, there are: a rotor, a rotating force transmitted from the outside, and a moving member, which is assigned to 4 i. and in the outer door of the outer casing; And a cam means, the second side: the coagulation force is changed to move in the axial direction of the rotor along the moving member; wherein the flow path is variably configured to constitute a second flow path; When the degree becomes a predetermined value or more, it will take two turns: the _body chambers are shaped like each other == components, and The two-way system is connected to the second flow path intercepting side... = the blocking member is pushed in the opposite direction to the _ of the rotor described above] when the rotational speed of the rotor becomes unreachable = 319958 9 200905102 -%·, the second flow path The position where the cover is formed in a connected state. a returning to the liquid chambers in the fourth application of the patent application to convey the rotational force from the outside, in the invention, the rotating body is provided with the movable member, and the movement is placed on the outer side of the rotor, A liquid chamber is formed between the outer casing and the outer casing by the cam. The rotor of the member: the shaft 2 converts the rotational force of the rotor into a linear movement in the direction of the axis along which the movement is sought. Thus, the hunting is performed by shifting the rotational movement of the rotor, that is, the movement of the straight line corresponding to the rotor (i.e., the movement I) increases the amount of movement of the moving member. This increases the torque acting on the rotor. The second flow path is provided with a second flow path interrupting member, and the first time: the rotation speed of the rotor when the rotor rotates by a predetermined value or more is rotated by the shear force generated between the rotor and the rotor, and The liquid passage chambers are formed in a non-communicating state by the path blocking member, and the flow path blocking member is coupled to the second spring pushing means in a direction opposite to the rotation direction of the rotor. When the rotation speed of the t rotor is less than the predetermined value, the second flow path blocking member returns to the position where the liquid chamber is in a difficult state. In this manner, when the liquid chambers are separated from each other by the second flow path blocking member: when the moving member moves, the viscous resistance generated by the moving member stirring the viscous fluid in the liquid chamber is generated, and The cutting resistance between the viscous fluid that is not received when the moving member moves and the moving member. Force 319958 10 200905102 Then, when the rotational speed of the rotor reaches a predetermined value or more, the shear force generated between the rotor and the rotor becomes larger than the spring force generated by the second bombing means, so the second flow path covers The broken member will rotate. Thereby, the liquid chambers become non-connected with each other. Therefore, in the liquid chamber, in addition to the viscous resistance and the shear resistance caused by the viscous fluid, the I contraction resistance generated by the viscous fluid in the liquid chamber (4) due to the movement of the moving structure is added. Therefore, the torque acting on the rotor increases, so the damping force provided by the damper becomes large. Then, when the rotational speed of the rotor becomes less than a predetermined value, the shear force generated between the rotor and the rotor becomes smaller than the thrust generated by the second bombing means, so that the second bombing means returns to its original state. Thereby, the second flow path and the broken member return to the original position, and the liquid chambers become connected to each other. Therefore, in the liquid chamber, the compression resistance caused by the viscous fluid is reduced, and the torque acting on the rotor is reduced. Therefore, the invention of the fifth application of the damper caused by the damper is applied for the application. In the damping H described in the fourth item, the front moving member is provided with the outer casing wall and the upper and lower sides of the column for defining the liquid chamber. The constituting member: the undulating groove [4] is disposed on the outer circumferential surface of the rotor, and has an axial direction of the rotor, and has a peak and a valley m-closing projection, and is provided in the moving member for fitting with the cam groove. In the invention of claim 5, the 俜 will protrude from the inner wall of the outer casing, and the movable member can be placed on the column between the columns for defining the liquid chamber. 319958 11 200905102 . Further, a corrugated cam groove is formed on the outer circumferential surface of the rotor, and the wave and the cam groove have peaks and troughs in the axial direction of the rotor, and == a fitting protrusion for fitting with the cam groove is used as 'Ten 0's rotor moves in the axial direction. The invention of claim 6 is the damper according to the fourth aspect of the patent application, wherein the moving member is fitted to the front cam groove so that the engaging projections are shifted from each other. In the invention of claim 6 of the invention, the phases are shifted from each other to move, and each shift: the two wide moving members are made into (4) and the positions of the moving members in the liquid chamber are not: two, which can be changed in each liquid chamber. The torque can be smoothly reduced to the torque of the rotor. In the damper of the 3rd patent range of Shen 3, the above-mentioned rotation two: in the :::== shaking member, the state in which the central axis is tilted t = moving. It is connected by ~ partial, sub- And the rocking member is placed in the rocking member by the rotation of the rotor, and is in the liquid chamber described above, and is shaken by the rocking member. The following components and the k-way completion blocking member are used when the rotational speed of the rotor reaches a predetermined value or more, and the combined gentleman—such as #付, + θ is caused by the shear force generated between the rotor and the rotor. The third flow path is formed in a non-connected state; and the third three-way passage is in the third flow path interrupting member, and the third breaking member is directed in a direction opposite to the rotation direction of the rotor 319958 12 200905102 When the degree is less than the predetermined value, the third steam passage member is brought to the state in which the liquid chambers are in a connected state with each other. _ _ =::=: Turning: Mingzhong' is useful for the rotating body, v. , y ^ 疋 rotor of the rotation, and is provided with a rocking member, with two slanted state Eccentrically to the axis of the rotor core and the roll to be: == :: _ shake movable, but fixed _. In the piston member 舆; the shell is placed::::^ moves as follows: the f=== is converted into a piston member back and forth, that is, the movement amount acting on the rotor plus the piston member is set to have a third a flow path interrupting member, the member is rotated when the rotational speed of the rotor becomes a predetermined value by a shear force generated between the first and second rotors, and the liquid chambers are moved to each other by means of: The second transitional member is coupled to the second thrusting means, and the third path is interrupted. When the rotational speed of the first rotor opposite to the direction of rotation of the rotor is less than a predetermined value By reading the shape =:::: diameter interrupting member...putting the liquid chamber into the path blocking member so that the liquid chambers are in each other = raw: when the tongue is in the 2 state, 'by the movement of the piston member, in the liquid In the room, the viscous resistance generated by the visco-fluid fluid of the living base member and the shear resistance generated between the viscous fluid and the piston member which are not stirred when the plug member moves are generated at 319958 13 200905102. Then, when the rotation speed of the rotor reaches a predetermined value or more, the shear force generated between the rotation and the rotation becomes larger than the spring force generated by the third bombing means, so the third flow path is interrupted. The member will rotate. Thereby, the liquid chambers become non-connected with each other. Therefore, in the liquid chamber, in addition to the viscous resistance and shear resistance caused by the viscous fluid, the compression resistance caused by the viscous fluid being compressed in the liquid chamber due to the movement of the piston structure is added. Since the torque acting on the rotor increases, the damping force provided by the damper becomes large. Then, when the rotational speed of the rotor becomes less than a predetermined value, the shear force generated between the sub-spins becomes smaller than the third push-pull push, so that the third ejecting means is restored. By = r:r: return to the original position, the liquid chambers will meet each other; i. : change: the torque used for the rotor will decrease, so the reduction provided by the damper = the invention of the application of item 8 is outside the damping Shouting; 禝 several liquid chambers, 嗖晋于义,有有. Μ = 于 inside the shell 'and filled with viscous: body, .: child' conveys the rotational force from the outside, and is transferred to the aforementioned shell Inside, and subject to the resistance of the 疋I, the rotating member 'has the same torque as the rotor: the same chamber: the viscous fluid of the rotor; the guiding protrusion, (4): the heart and the position of the core is misaligned, The oscillating body is a shaft 屯 319 519 958 05 958 958 rl rl rl rl rl rl rl 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 The path is provided in the moving body along the moving direction of the oscillating body, and the rocking body is placed in the swaying body, so that the substantially separated liquid chamber f is in a communicating state; and the occluding member is disposed on the oscillating body. In the current month, when the rotational speed of the rotor is above a predetermined value, the aforementioned viscous flow The viscous resistance caused by the body moves to block the decompression flow path. In the invention of claim 8 of the invention, a plurality of liquid chambers filled with · are provided in the outer casing. A rotatable rotor is housed within the housing. The rotor is resistant to viscous fluid from within the liquid chamber. Further, a rotating member is provided in the outer casing, and has a different axial core from the rotor, and transmits a rotational force of the rotor, and is provided with a guiding protrusion that is displaced from the axis of the rotating member. On the other hand, a swinging body is provided in the liquid chamber, and the linear guide groove that is fitted to the guide protrusion is formed in the movable body, and the guide protrusion is rotationally moved by the rotation mechanism rotation. The kinetic energy of the oscillating body is transmitted through the guiding groove. By changing the rotational movement of the rotor into the oscillating movement of the oscillating body, the movement of the oscillating body can be increased to increase the amount of movement of the oscillating body to increase the torque acting on the rotor. 7 Further, along the moving direction of the rocking body, the rocking body is provided with a ::way: the rocking body is placed therebetween. By the reducing flow passage; the substantially empty liquid chamber is in a communicating state. In addition, the working occlusion member: the occluding member is when the rotational speed of the rotor becomes:: when there is above, 'will move by the viscous resistance caused by the viscous fluid, and the movement of the occluding member is 319958 15 200905102 The occlusion reduces the circulation path. , s strong = '# by the subtraction (four) pass path to make the (four) chambers become connected to each other =:, hour: by the movement of the shaking body, the viscous resistance generated when the fluid is generated in the liquid chamber, and the shaking body Shear resistance generated between the viscous fluid that is not forked and the rocking body when moving. Then, when the rotational speed of the rotor becomes a predetermined value or more, the viscous resistance of the viscous fluid increases, and the occluding member moves. Thereby, (4) the pressure-reducing flow path, the shaking body is placed at i M i L , p... so that the substantially separated liquid chambers are in a non-connected state. Therefore, in the liquid chamber, in addition to the viscous resistance and the shear resistance of the viscous fluid, the contraction resistance caused by the viscous fluid in the liquid chamber I due to the movement of the oscillating body is added. Therefore, the torque applied to the rotation will increase, so the damping force provided by the damper will become larger. Then, when the rotational speed of the rotor becomes less than the predetermined value, the viscous resistance caused by the sexual fluid is reduced, so the occluding member returns to the original position 'the open and reduced circulation path' places the oscillating body therebetween. The substantially separated liquid chambers become in communication with each other. Therefore, the contraction resistance caused by the viscous fluid in the liquid chamber is reduced, and the torque acting on the rotor is lowered, so that the damper provided by the damper becomes small. The invention of claim 9 is a damper H towel as recited in item 8 of the patent application, and the fourth (four) system reads the wrong (four) position to move the guide projection into the guide groove. In the invention of claim 9 of the Patent Model, each of the shaking systems is moved in such a staggered phase, and the positions of the respective shaking bodies in the liquid chamber are different. Therefore, the torque generated in each liquid chamber can be changed, and the torque acting on the rotor can be smoothly increased by 319958 16 200905102. (Effect of the Invention) The present invention has been made in the above-described configuration, so that the torque acting on the rotor can be changed in accordance with the rotational speed of the rotor. [Embodiment] Next, a damper according to a first embodiment of the present invention will be described. As shown in Fig. 1 to Fig. 3, the bottom of the cylindrical damper 1 〇 has a substantially open side as ' Λ η for convenience (4), the upper side of the outer casing 12: ° °, the bottom The side is explained as a damper 1 0 , . -, t The outer dare 12 is filled with oil as a viscous fluid (in the form of a dot 1: '. two ti,). Further, the outer peripheral surface of the bottom surface of the outer casing 12 is used to promote the large sigh fixing piece 14, and although not shown, it is a movable member that can be relatively moved, such as a pull-out member that can be fixed in the fixed portion. In the second to fourth embodiments, the solid side 14 is not shown. A trochoidal line (trc) chc)i (four)-shaped portion 16 having a plurality of teeth i6a (here, eight) is formed on the inner peripheral surface of the outer casing 12, and the trochoidal tooth-shaped portion has two trochoidal tooth portions 16 The height of the end surface is higher than the upper end portion of the outer casing 12. Further, a hollow J-shaped (eccentric member) 20 is disposed inside the trochoidal tooth portion 16, and the inner member 2 is formed with a trochoidal tooth shape; (2nd sway (four) shape) 18 having tooth portions 18A (here, five) that mesh with the teeth 16A of the trochoid tooth portion a, and the trochoid tooth portion 319 勺 319958 17 200905102 The height of the upper end surface of the tooth portion 1 is slightly lower than the upper end surface of the remainder 4 16A. The tooth portion of the wire tooth portion 6 is provided on the inner side of the inner member 20 so as to be able to interpolate the rotor 22 and transmit the rotation. The force transmission member (the special-purpose sub-system is roughly divided into a slightly cylindrical shaft portion, and the junction is not formed. The thin-walled pedestal portion 2 δ is larger between the rotors 22 and _. With the direct ratio of the axis f above = when the sub-22 is inserted into the inner member 2〇, the upper end surface of the trochoidal tooth portion 16 is formed into a substantially plate 2 (the first and the trochoidal teeth are formed) unit 16 - abutting the lower limb (first flow path blocking member) 3 后 which is described later, the lower end surface of the circular portion is recessed coaxially with the shaft portion 设有 with a large = two nesting concave portion %, which is fitted to The cylindrical sleeve convex portion 3δ protrudes from the outer bottom surface of the cymbal 12. The rotor cymbal can be rotated at the central portion of the cymbal 12. The outer peripheral surface of the eccentric portion 26 is larger than the outer diameter of the shaft portion 24: The rib-shaped plurality of ribs 4 are disposed along the axial direction of the eccentric portion (9), and the front end faces of the plurality of ribs 4G are located on the same circumference, and the outer peripheral surface of the portion 26 and the rib portion 4 are The front end surface of the crucible is formed to abut against the inner peripheral surface of the inner 4 member 20. That is, the inner member 20 is in an eccentric state with respect to the shaft portion 24: when the rotor 22 is rotated, as in the fourth As shown in Fig. (Α) and (Β), the inner member 2G is pressed by the front end surface of the rib 4G, and the inner member 2 is rotated under the biased shape. At this time, the trochoidal tooth shape The Μ Μ 在 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 319 The wide cross section is formed in the hole portion 44 at the center portion of the substantially L-shaped ring cover portion 42. The _ can be inserted into the O-ring mounting groove 3 formed on the side of the pedestal portion 28 at 0 = t2 = 2, 珲 34: face-to-face: the inner peripheral surface of the o-shaped portion 44 in a state in which the clothing is placed in the o-ring mounting groove 32. Thereby, the rotor 22 will not leak out; the raw gap is sealed' Further, in the outer casing 12, as shown in Figs. 3 and 5, an annular groove portion 48 is recessed on the outer surface of the lid portion 42 and outside the hole portion 44. Further, an arc-shaped (four) joint portion 5 凹 is recessed in the outer side of the groove portion 48 via the hole portion 44. Further, on the back surface of the crotch portion 42, a ring-shaped plate body 3 is formed. As shown in the figure, an annular rib 52 is protruded from an inner edge portion of the plate body 3〇, and an annular rib is interposed between the outer side of the annular rib 52 and the concentric circle of the plate body 3〇. 52 is provided with a pair of circular ribs 54. The arc rib 54 is fitted to the fitting portion 5 in a state in which a gap is formed in the circumferential direction between the fitting portion 5A and the fitting portion 5A. As shown in Fig. 3, the annular rib 52 abuts against the inner wall surface of the groove portion 48 in a state where a gap is provided between the groove portion 48 and the groove portion 48. Next, a gap between the groove portion 48 and the annular rib 52 is attached to a torsion spring (first spring pushing means) 56, and the twist is 319958 19 200905102. One end of the spring 56 is attached to the plate. The body 3 is, and the other end of the torsion spring 56 is attached to the cover portion 42. On the other hand, as shown in Fig. 5, on the back side of the plate body 3, six arc-shaped groove communication paths 58 are recessed at predetermined intervals along the concentric circles of the plate body 30. As shown in Fig. 6(A), the length of the circular arc groove 58 is larger than the tooth thickness of the tooth portion of the trochoidal tooth portion 16 of the outer casing 12, and is in the trochoidal tooth shape. When the teeth 31 (10) of the portion 16 and the circular arc groove 58 are vertically enlarged, the both end portions of the circular arc groove 58 are exposed from the tooth surface of the tooth portion. Further, as shown in Fig. 4 (A) and (B), in the state in which the inner member is misaligned 12, 'the trochoidal tooth portion 外壳 of the outer casing 12 and the inner two inner S are filled with eucalyptus oil ( Dotted display). This hunting is performed by the torsion spring - 56 attached between the groove portion 48 and the annular rib 52 to position the circumferential direction of the plate body 3''. In this state, the arc ribs 54 are arranged in the center of the fitting portion 5〇 of the circle Θ (TA) new _ and 卩 2 of the 十 ^ 30 plate, and as the field is not, from the plane view, the circle The position of the arc groove 58 is aligned with: : line: r portion, the position of the tooth portion - up and down " = = the surface is exposed / the state where the both ends of the arc groove 58 are from the teeth of the tooth portion (10), That is, as shown in Fig. 4 (A) and (β), what is the internal component? The trochoidal tooth diagram of the trochoidal toothed portion 16 I of the symmetry of the symmetry and the figure 6 of the symmetry of the trochoidal portion of the symmetry The section (10) is separated by 圆弧1 by the circular arc groove 58 of the plate body 3319 319958 20 200905102 = connected resentment. Therefore, the space S! adjacent to the arcuate groove 58,7. The pawl moves on the other hand, when by resisting the stress of the spring force of the torsion spring % (the body 30 is rotated, the wire AA & +, the direction of the 4 turns or the twisting stress) The circle portion 54 of the plate body 30 abuts against the fitting portion 5 of the lid portion 42. When the end face, such as =: open ^ no, from the plane view, the end side of the circular groove 58 will be blocked by the trochoidal toothed port Ρ 16 and the private 仏, ,, open adjacent The space & the teeth 18 of the ^ portion 18 are in a state of isolation. The figure (Α) & (Β) will become non-connected. The action of the damper of the first embodiment of the present invention will be described. # 1弟4图(Α) and (8), #转+偏偏部26, 内邱搂丛〇λ人 paid the audition. Thereby, 1: swirling along the shape of the trochoidal tooth portion 16.

所攪 曰 _矽油會被内部構件20的齒部18A 所授拌：而在空間S内產生石夕油的黏性阻力。 内移1内部構件20的齒部18A於餘擺線齒形部 動時，會在未授掉㈣油與該齒部18A之間產生剪切 的餘齒形部16之齒部16A與内部構件2〇 齒部18Α^二#齒部18〇斤形成的空間Sl會隨著該 王7油所造成的壓縮阻力。 座 亦即’藉由旋轉内部構体？ η +ώ 阻力、11㈣油所造成的黏性 子22，且物^及壓縮阻力所產生的轉矩會作用於轉 且該轉矩會與轉子22的旋轉速度成正比變大（第7 319958 21 200905102 圖所示的轉矩1 )。 如第6圖（A)所示，由於外殼12内的各空間& 卜30的圓弧溝58使彼此相鄰的空間S!連通，故經由該 =弧溝58,會變成矽油可流動於彼此相鄰的空間心 您0 :此’與彼此相鄰的空間&變成非連通狀態的情形相 用於：：：阻力會減少，而壓縮阻力減少的部分會使作 降低轉子22之轉矩降低，故阻所提供的減震力會 觸如第3圖所示，與轉子22的偏心部26上面接 =體。雖會因轉子22的旋轉而在與偏心㈣上面： B 或黏性流體的流動力，但3() 的扭轉咖的彈推力而限制板體3◦的旋;裝於板體30 卜而然而’當轉子22高速旋轉時，在板體30與偏心部26 之間所產生的剪力或黏性流體的 、過扭轉彈簧56所產生 θ又大而超 彈善^^ 的彈推力。如此，當剪力變得比扭轉 ” 6/斤產生的彈推力還大時，板體30會旋轉。 笔邻1著:山在^體3〇的圓弧肋部54(參照第2圖）抵接於 =42的肷&部50(參照第5圖）端面的狀態下，如第6 二)所不’從平面觀之，板體3〇的圓弧溝58的一端側合 ;=線::部16堵塞’彼此相鄰的空間S·會變成非； :。藉此’空間S1内的矽油的壓縮阻力會變大 轉矩會增大’故阻尼器1。所提供的減震力： ’憂大（弟7圖所不的轉矩2)。 319958 22 200905102 在此狀態下，由於扭轉彈簧56會朝抵抗彈推力的方向 彈推，故扭轉彈簧56會變成蓄積彈性能量（恢復力）的狀 心因此，^轉子2 2的旋轉速度變慢，且在板體3 〇與偏 心部26上面之間所產生的剪力或黏性流體的流動力變得 比該彈性能量還小時，扭轉彈簧56會恢復原狀，且板體 30會返回原本的位置，如第6圖⑴所示，會使彼此相鄰 的空間S!連通。藉此，作用於轉子22之轉矩會返回原本 的狀態（轉矩1的狀態）。 亦即，依據本實施形態，如第7圖所示，能對應轉子 22的旋轉速度來使作用於轉子22之轉矩改變（轉矩1與轉 矩2)。此外，如第8圖所示，藉由調整扭轉彈簧56的彈 推$，能容易地改變轉子22的旋轉速度與低轉矩（轉矩〇 及咼轉矩（轉矩2)的切換位置p。 在此，如第5圖所示，雖於板體3〇的背面側凹設.有六 ，圓弧清58，且從平面觀之為以大致扇狀的肋部6〇來界 定相鄰的圓弧溝58間’但由於只要在設於外殼12的餘擺 線齒形部16的齒部16A與圓弧溝58予以重疊的狀態下， 該圓弧溝58的兩端部會變成從齒部！ 6A露出的長度即可， 故該肋部60的形狀並未限定於此。例如，如第9圖所示， 亦可將用以界^圓弧溝58之肋部6G作成從平面觀之為三 角形的三角肋部62。 接著，說明本發明的第二實施形態的阻尼器。 如第10圖至第12圖所示，於阻尼器1〇〇 大致圓筒狀之有底外殼1Q2。在此，為了方便說明有= 319958 23 200905102 、外殼102的開口側作為阻尼器、1〇〇的上侧、將 阻尼器⑽的下側，來進行各構件的說明。 、J作為 在外殼102内填充有矽油，且可在外殼1〇2内 狀：轉子1〇4。該轉子104-端側的直徑係比另—端側的 直從遇小且露出外部，並與用以傳達旋轉力 圖示）連結。 咬偁仵（未 於轉子104的另-端側，沿著轉子m的轴方向 具有波峰和波谷的波形凸輪溝（凸輪手段）m，且波數^ =。接著’將大致圓筒狀的環套(第二流通 ： 件胸套設在該轉子⑽的另—端側。 逆斷構 在環套108的上端側設置有小 部_而於環請的内周面側設置段差⑽； 該段差刪的角落部形成〇形環安裝溝u . ;裏广。藉由該。形環112，使發油不會在環套10二 104之間漏出外部。 ”得子 12()。^外’在環套1〇8且為對應凸輪溝⑽的位置，以 〇間隔形成有三個矩形孔114，且於環套 反狀的滑動片(移動構卿，該滑動片丨二 =各矩形孔m，且配合環套_ 段的内側中央部突出有嵌合突起(凸輪手 。只肷δ犬起118係可經由環套1〇8的矩形 ::轉I:4的凸輪溝⑽喪合。藉此，藉由轉子1(14的 轉，透過凸輪溝106與嵌合突起11δ，滑動片ιΐ6會沿 319958 24 200905102 著輅子104的軸方向來回移動(參照第13圖） 動片116係彼此錯開相位來移動。 圖）°此時，各滑 在相鄰的滑會j 7， m的側面沿著滑:皮此間設置有間隙’並在滑動片 在此，爲了片116的移動方向形成孔口 12〇。 在此±舄了迴避與安裝在環套108的滑 於外殼102的内周面係凹設有 狀的滑動片收容部(液體室)122。接著，:1、、二大= 122内填充石夕油 Μ “動片收谷部 著轉子ΗΜ 6 θ在滑動片收容部122内沿 者轉千104的軸方向來回移動。 配置在凸輪溝所:，在滑動片116的嵌合突起118 在用以蓋住滑動片=波谷的中央部的狀態下，設置 凸緣部126下而你、谷部I22的上部之後述的内蓋124的 以及設置在、：滑動片116上端面之間的間隙(空間&) 間的間隙(空：部122底面與滑動片116下端面之 116來回移V時所：：成相同的大小。亦即’對於滑動片 ⑴的移動方向=㈣的壓縮力，沒有因為滑動片 套1〇8 如第14圖及第16圖（A)所示，在設置於環 ⑽的轴太矩形孔114與矩形孔114間，在沿著環套 向兩側形成有矩形狀的連通凹部128，並在與滑 動月116之間設置間隙。 面1〇:衣=08的上端部設置有形成為倒三角形狀的凸輪 凸輪132 # 108的上部設置有套設於轉子104的環狀 w ’於該凸輪132的下端部設置可與凸輪面1〇8八面 319958 25 200905102 接觸的凸輪面132A，並彼此嵌合。 i 2 4。t = 2 3 2的外侧套設有作成大致圓筒狀的内蓋 〜内盍124的内周面形成有定位溝134，而沿著凸 :13=的轴方向突設於凸輪132的外周面的定位肋部挪 於較位溝134°在較位肋部136嵌合於該定 / #狀悲下’凸輪⑶係相對於内蓋124被停止旋 轉0 f t K. 另方面，在凸輪132的上部，在與設置在内蓋124 上端部内侧的環狀部舰之間設置有間隙 設螺旋彈簧（第二彈推 " 怦推于杈）137,该螺旋彈簧137的一端 抵接於環狀部124A，另一端部抵接於凸輪132，而將該凸 請向環套108側彈推。藉此，環套1〇“ 寺與凸㈣的凸輪面咖合狀態(凸輪面_ 的W與凸輪面132Α的峰部的位置為—致之狀態）。 此外’藉由形成在環套1〇8上端側的小徑部109,而 於¥套108的外周面設置有段部138。另—方面，在外般 ⑽的上端部内側設置環狀的台座部“Ο,且在環套⑽ 收谷於外殼1 〇 2内的狀能，a — 大致相同高度。 心下。座部⑽變成與段部138 、接著，在套設於環套⑽外側的内蓋124的下端部形 成凸緣部126’该凸、緣部126的下面係大致抵接 及台座部14°。接著，將該凸緣物的下面固定在台座 部14〇。“，藉由：蓋124,凸輪132變成不會旋轉。 MU m24的凸緣部126上面與外殼1〇2 319958 26 200905102 的上端部會變成齊平的狀態，而以覆蓋内蓋 m的方式形成，且内側形成有螺紋部U2A的外蓋14= 螺入形成在外殼1Q2外周面的螺紋部職，透過該外蓋Hi 將内蓋124固定至外殼1〇2。 在此，在凸緣部126下面的外緣部與内緣 ㈣絲部Η4、146，分別可安裝0形環148、15〇。〇有形 ¥ Η8的作用切油不會在内i 124與外殼之間漏出外The enthalpy _ 矽 oil is imparted by the tooth portion 18A of the inner member 20: and the viscous resistance of the zephyr oil is generated in the space S. When the tooth portion 18A of the inner member 1 is moved by the trochoidal tooth portion, the tooth portion 16A and the inner member of the remaining tooth portion 16 which is sheared between the (four) oil and the tooth portion 18A are not imparted. 2 The molar portion 18 Α ^ 2 # tooth portion 18 〇 kg formed space Sl will be caused by the compression resistance caused by the king 7 oil. The seat is also 'by rotating the internal structure? η + 阻力 resistance, 11 (four) oil caused by the viscous 22, and the torque generated by the material and compression resistance acts on the rotation and the torque will become proportional to the rotational speed of the rotor 22 (7 319 958 21 2009 05102 The torque shown in the figure is 1). As shown in Fig. 6(A), since the arc grooves 58 of the spaces & 30 in the outer casing 12 connect the spaces S! adjacent to each other, the arc groove 58 becomes 矽 oil flowing therethrough. Spaces adjacent to each other you 0: This 'spaces adjacent to each other's non-connected state are used for::: the resistance will decrease, and the part with reduced compression resistance will reduce the torque of the rotor 22. When it is lowered, the damping force provided by the resistor is as shown in Fig. 3, and is connected to the eccentric portion 26 of the rotor 22 to be the body. Although it is caused by the rotation of the rotor 22 and the eccentricity (4): B or the flow force of the viscous fluid, but the elastic thrust of the twisted coffee of 3 () restricts the rotation of the plate body 3; it is attached to the plate body 30. When the rotor 22 rotates at a high speed, the shear force generated by the shear force or the viscous fluid between the plate body 30 and the eccentric portion 26 is large and super elastic. In this way, when the shear force becomes larger than the spring force generated by the twisting of 6/kg, the plate body 30 will rotate. The pen is adjacent to the arc rib 54 of the mountain body 3 (see Fig. 2) In the state in which the end face of the 肷 & portion 50 (see Fig. 5) of =42 is abutted, as shown in Fig. 6), one end of the circular arc groove 58 of the plate body 3〇 is closed from the plane view; Line:: Part 16 is blocked. 'The space adjacent to each other S will become non-;;. By this, the compression resistance of the oil in the space S1 will increase and the torque will increase. Therefore, the damper 1 is provided. Force: 'Worry (Torque 2 of the 7th figure) 319958 22 200905102 In this state, since the torsion spring 56 will push in the direction of resisting the thrust, the torsion spring 56 will become accumulated elastic energy (recovery) Therefore, the rotational speed of the rotor 2 2 becomes slow, and the shear force or the viscous fluid generated between the plate body 3 〇 and the eccentric portion 26 becomes smaller than the elastic energy. The torsion spring 56 will return to its original shape, and the plate body 30 will return to its original position. As shown in Fig. 6 (1), the space S! adjacent to each other will be connected. The torque of the rotor 22 returns to its original state (state of torque 1). That is, according to the present embodiment, as shown in Fig. 7, the torque acting on the rotor 22 can be made corresponding to the rotational speed of the rotor 22. Change (torque 1 and torque 2). Further, as shown in Fig. 8, by adjusting the spring pushing amount of the torsion spring 56, the rotational speed and the low torque of the rotor 22 can be easily changed (torque 〇 and 咼) Here, as shown in Fig. 5, the switching position p of the torque (torque 2) is recessed on the back side of the plate body 3〇. There are six, the arc clears 58, and the view from the plane is approximately The fan-shaped ribs 6 界定 define the space between the adjacent circular arc grooves 58. However, as long as the tooth portions 16A provided in the trochoidal tooth portion 16 of the outer casing 12 overlap with the circular arc grooves 58, The both ends of the circular arc groove 58 may have a length that is exposed from the tooth portion 6A. Therefore, the shape of the rib portion 60 is not limited thereto. For example, as shown in Fig. 9, it may be used for the boundary. The rib 6G of the circular arc groove 58 is formed as a triangular rib 62 which is triangular in plan view. Next, a damper according to a second embodiment of the present invention will be described. As shown in Fig. 12, the damper 1 has a substantially cylindrical bottomed outer casing 1Q2. Here, for convenience of explanation, there is = 319958 23 200905102, the open side of the outer casing 102 serves as a damper, and the upper side of the cymbal, The lower side of the damper (10) is used to describe each member. J is filled with eucalyptus oil in the outer casing 102, and can be in the outer casing 1 〇 2 shape: the rotor 1 〇 4. The diameter of the rotor 104-end side is On the other hand, the straight side of the end side is small and exposed to the outside, and is connected to the figure for transmitting the rotational force. The bite is not (on the other end side of the rotor 104, there are peaks and troughs along the axis of the rotor m). Wave cam groove (cam means) m, and the number of waves ^ =. Next, 'a substantially cylindrical ring sleeve is provided (the second flow: the chest sleeve is provided on the other end side of the rotor (10). The reverse fracture is provided with a small portion on the upper end side of the collar 108. The circumferential side is provided with a step difference (10); the corner portion of the step is formed to form a 〇-shaped ring installation groove u.; 广广. By the ring 112, the oil does not leak outside between the ring sleeves 10 and 104. The sub-12().丨 = = each rectangular hole m, and the inner central portion of the matching ring sleeve _ segment protrudes with a fitting protrusion (cam hand. Only 肷 δ dog from 118 series can be rectangular via the ring sleeve 1 〇 8:: turn I: 4 The cam groove (10) is slid. Thus, by the rotation of the rotor 1 (14, through the cam groove 106 and the fitting projection 11δ, the sliding piece ι 6 moves back and forth along the axis direction of the die 104 along 319958 24 200905102 (refer to the 13th Figure) The moving piece 116 is shifted from each other in phase to move. Figure) ° At this time, each sliding on the side of the adjacent sliding j 7, m along the sliding: the skin is provided with a gap Here, in the sliding piece, the opening 12 is formed for the moving direction of the piece 116. Here, the sliding piece accommodating and slidably attached to the inner circumferential surface of the outer casing 102 of the cuff 108 is accommodated. Part (liquid chamber) 122. Next, 1, 1, and 2 = 122 filled with Shixia oil Μ "The rotor is wound around the rotor ΗΜ 6 θ in the direction of the axis of the slider 104 in the direction of the axis 104 In the cam groove: in the state in which the fitting projection 118 of the slide piece 116 covers the center portion of the slide piece = trough, the flange portion 126 is provided and the upper portion of the valley portion I22 is described later. The gap between the inner cover 124 and the gap (space &) disposed between the upper end faces of the sliding sheets 116 (empty: the bottom surface of the portion 122 and the lower end surface 116 of the sliding sheet 116 are moved back and forth by V: The size of the sliding force of the sliding piece (1) = (four), not because the sliding piece 1〇8 is as shown in Fig. 14 and Fig. 16(A), the axis disposed on the ring (10) is too rectangular Between the hole 114 and the rectangular hole 114, a rectangular connecting concave portion 128 is formed on both sides of the ring sleeve, and is slid A gap is provided between the upper surfaces of the cam 132. The upper end portion of the garment = 08 is provided with a cam cam 132 formed in an inverted triangular shape. The upper portion of the sleeve 108 is provided with a ring w' sleeved on the rotor 104 at the lower end portion of the cam 132. The cam surface 132A which can be in contact with the cam surface 1 〇 8 occupants 319958 25 200905102 is fitted to each other. The outer side of the i 2 4 t= 2 3 2 is sleeved with a substantially cylindrical inner cover ～ inner 盍 124 The inner circumferential surface is formed with a positioning groove 134, and the positioning rib protruding from the outer circumferential surface of the cam 132 along the axial direction of the convexity 13= is moved to the positioning groove 134°, and the positioning rib 136 is fitted to the positioning rib/ The cam (3) is stopped rotating relative to the inner cover 124 by 0 ft K. On the other hand, in the upper portion of the cam 132, a gap is provided between the annular ship and the inner side of the upper end of the inner cover 124. a coil spring (the second spring push) is 137, and one end of the coil spring 137 abuts against the annular portion 124A, and the other end abuts against the cam 132, and the convex portion is urged toward the collar 108 side. Push. Thereby, the cam sleeve 1 〇 "the temple and the convex (four) cam face-to-face state (the position of the cam surface _ W and the cam portion 132 Α peak portion is the same state). In addition, 'by forming in the ring sleeve 1〇 8 is a small-diameter portion 109 on the upper end side, and a segment portion 138 is provided on the outer circumferential surface of the sleeve 108. On the other hand, a ring-shaped pedestal portion "Ο" is provided inside the upper end portion of the outer casing (10), and the ring sleeve (10) is valleyd. The shape energy in the outer casing 1 〇 2, a - is substantially the same height. Heart. The seat portion (10) is formed with the segment portion 138, and then the flange portion 126' is formed at the lower end portion of the inner lid 124 that is sleeved outside the collar (10). The convex portion and the lower surface of the edge portion 126 are substantially abutted against the pedestal portion 14°. Next, the lower surface of the flange is fixed to the pedestal portion 14A. "With the cover 124, the cam 132 becomes non-rotating. The upper end portion of the flange portion 126 of the MU m24 and the outer casing 1 〇 2 319958 26 200905102 become flush, and are formed to cover the inner cover m. The outer cover 14 having the threaded portion U2A formed on the inner side is screwed into the threaded portion formed on the outer peripheral surface of the outer casing 1Q2, and the inner cover 124 is fixed to the outer casing 1〇2 through the outer cover Hi. Here, at the flange portion 126 The lower outer edge portion and the inner edge (four) wire portion 、4, 146 can be respectively mounted with O-rings 148, 15〇. The action of the tangible shape Η8 does not leak between the inner i 124 and the outer casing.

部，〇形環150的作用為石夕油不會在内蓋124與環套1〇8 之間漏出外部。 如第14圖所示’在藉由配設在凸輪132上部盥内罢 m的環狀部124A之間的螺旋彈簧137的彈推力，使凸： 132的凸輪面132A與環套1〇8的凸輪面刪嵌合的狀I; 下’且在外殼102 0收容有環套1〇8❺狀態下，設置在環 套108的連通㈣128會面向用以界定設置在外殼ι〇2内 的彼此相鄰的滑動片收容部122之界定肋部(柱材)13〇,並 (從界定肋部130的兩側面露出。 如第16圖（A)所·示，雖然幾乎不會在環套108的外周 面與界定肋部130之間產生間隙，但由於在連通凹部128 ^界疋肋部130之間設置間隙，且連通凹部128從界定肋 邛130的兩侧面露出’故經由連通凹部128，彼此相鄰的 滑動片收容部122會變成連通狀態(彼此相鄰的空間&與 空間S2會變成連通狀態）。 、 另方面，如第15圖所示，當藉由朝抵抗螺旋彈簧 137的彈推力方向的應力（使環套1〇8正旋轉或逆旋轉的應 319958 27 200905102 •力）而解除凸輪132的凸輪面ι32Α盥f套 -端側H時_:如第16圖⑻所示，連通凹部⑵的 造成相鄰的堵塞。亦即，因連通凹部128而 U相4的α動片收容部m 的空間S丨盥办η c： 欠战非連通狀悲（彼此相鄰 /、二間S2邊成非連通狀態）。 ^兄月树明的第二實施形態的阻尼器的作用。 轉子二圖所不’當轉子104低速旋轉時，透過形成在 =的凸輪溝⑽及形成在滑動#ii6 : 容物内沿著轉子;n:tr的狀而於滑動片收 — 轉子104的轴方向來回移動。 藉此’在第14圖及第 m内，會產生滑動片⑴碑4()所不的滑動片收容部 ,, U6攪拌滑動片收容部122内的矽 油所產生的黏性阻力以及在 夕 收容邻122&囟μ 在月動片移動時在與滑動片 收谷邛122的内壁之間產生的剪切阻力。 在此，例如當滑動片116朝上方 滑動片116上端面盥内#丨％ 6V几綠λ 由於叹置在 隙(空間亀窄，、故;二!Γ τ面之間的間 支乍故會產生矽油所造成的壓縮阻力。 然而，由於各滑動片116係錯開相位 滑動片U6不會皆朝相间太士“ 木㈣故二個 相8方向移動。因此，如第14圖所干， 在藉由滑動片m的移動所構成的空間s 由相鄰滑動片116所構成的空間义會變寬。乍的“下， —另一方面，言史置在環套1〇8的連通凹部128會在盘只 疋肋部130之間設置有間隙的狀態下大致 二 定肋部⑽的兩㈣露出，經由該連通凹部128，使= 319958 28 200905102 片收容所122連通(使彼此相鄰的空間Sl、空 *門二’當因滑動片116的移動使空間變窄時，由於該 =滑由環套108的連通凹部128而移動至相 收合部122，故矽油所造成的壓縮阻力小。 及剪=藉由滑動片116的來回移動，石夕油的黏性阻力 所造成的轉矩主要會作用於轉子1〇4。 由於縮阻力降低，其降低的部分會 的轉矩變小，故阻尼器⑽戶斤提供的減震力小。轉子 雖合如第12圖所示，與轉子104接觸的環套⑽ ^ 口轉子1〇4的旋轉而在與轉子1〇4之間產 藉由螺旋彈簧137的彈推力 仁 與環套108的凸輪面_人輪132的凸輪面132A W㈣面im嵌合’以限制環套1〇8的旋轉。 …、、而，當轉子1G4高速旋轉時，在轉？ 1() 之間所產生的剪力會變大，而办、風说 ^ 彈推力。如此，如第二螺旋彈簧137所產生的 。"7“丄 弟以圖所不，當該剪力變得比螺旋彈夢 了^產生的彈推力還大時，環套_會_，在環套‘ 的凸輪面108A與凸輪132的凸 偏移。 7凸褊面132A之間會產生位置 韓圖及第16圖⑻所示，由於罐m的旋 奋 28的位置會偏移，連通凹部128的一端例 Γ;界定肋部13“者塞。亦即，因連通凹㈣而造成相 s :二片成為非連通狀態(彼此相鄰的空間In the part, the function of the ring-shaped ring 150 is that the stone oil does not leak outside between the inner cover 124 and the ring sleeve 1〇8. As shown in Fig. 14, the cam surface 132A of the convex portion 132 and the collar 1 〇 8 are made by the spring force of the coil spring 137 disposed between the annular portions 124A disposed in the upper portion of the cam 132. The cam surface is in the form of a fitting I; the lower portion, and in a state in which the outer casing 102 0 accommodates the loop cover 1〇8, the communication (four) 128 provided in the loop sleeve 108 faces adjacent to each other for defining the inner side of the outer casing ι2 The sliding piece accommodating portion 122 defines a rib (column) 13 〇 and is exposed (from both side surfaces defining the rib 130. As shown in Fig. 16(A), although it is hardly on the outer circumference of the collar 108 A gap is formed between the face and the defining rib 130, but a gap is provided between the communicating ribs 130 and the communicating recesses 128 are exposed from both sides of the defining rib 130. The adjacent slider accommodating portion 122 is brought into a communication state (the space adjacent to each other & the space S2 becomes a communication state). On the other hand, as shown in Fig. 15, when the spring force is applied against the coil spring 137 Directional stress (so that the ring sleeve 1〇8 is rotating or counter-rotating should be 319958 27 200905102 • force) When the cam surface of the cam 132 is released from the sleeve to the end side H, the adjacent recess is blocked by the communication recess (2) as shown in Fig. 16 (8). That is, the alpha diaphragm of the U phase 4 is connected to the recess 128. The space of the accommodating part m η c: owing to the non-connected sorrow (adjacent to each other, and the two S2 sides are in a non-connected state). ^ The function of the damper of the second embodiment of the brother. In the second diagram of the rotor, when the rotor 104 rotates at a low speed, it passes through the cam groove (10) formed in the = and is formed in the sliding #ii6: the space along the rotor; n: tr in the shape of the sliding piece - the axis of the rotor 104 The direction moves back and forth. Thus, in the 14th and the mth, the sliding piece accommodating portion of the sliding piece (1) the monument 4 () is generated, and the viscous resistance generated by the squeegee in the U6 agitating sliding piece accommodating portion 122 is generated. And the shearing resistance generated between the outer side of the slider 122 and the inner wall of the sliding piece 122 when the moon piece moves. Here, for example, when the sliding piece 116 faces upward, the upper end of the piece 116 is swept upward. #丨% 6V, a few green λ, because the sigh is in the gap (the space is narrow, so; the second! Γ τ surface between the branches will cause 矽The compression resistance caused by the oil. However, since the sliding pieces 116 are staggered, the phase sliding piece U6 does not move toward the phase of the phase "wood (four), so the two phases 8 move. Therefore, as shown in Fig. 14, The space s formed by the movement of the sliding sheet m is widened by the space formed by the adjacent sliding sheets 116. "Bottom, on the other hand, the communication recess 128 placed in the collar 1〇8 will be Two (four) of the substantially two fixed ribs (10) are exposed in a state where a gap is provided between the ribs 130, and the slabs 122 are connected to each other via the communicating recesses 128 (the spaces S1 adjacent to each other, When the space is narrowed by the movement of the slide piece 116, since the slip is moved to the phase folding portion 122 by the communication concave portion 128 of the ring cover 108, the compression resistance by the oil is small. And the shear = by the back and forth movement of the sliding piece 116, the torque caused by the viscous resistance of the stone oil mainly acts on the rotor 1〇4. Since the reduced resistance is reduced, the reduced portion of the torque becomes smaller, so that the damping force provided by the damper (10) is small. Although the rotor is as shown in Fig. 12, the ring sleeve (10) which is in contact with the rotor 104 is rotated by the rotor 1〇4, and the spring force of the coil spring 137 and the ring sleeve 108 are produced between the rotor and the rotor 1〇4. The cam surface _ the cam surface 132A W (four) surface of the human wheel 132 is im fitted 'to limit the rotation of the collar 1 〇 8 . ..., and, when the rotor 1G4 rotates at a high speed, is it turning? The shear force generated between 1() will become larger, while the wind and the wind say ^ elastic thrust. Thus, as produced by the second coil spring 137. "7 "The younger brother is not in the picture, when the shear force becomes larger than the impact force generated by the spiral bomb dream ^, the ring sleeve _ will _, the cam surface 108A of the ring sleeve and the convexity of the cam 132 Offset. 7 position between the convex surface 132A and the image shown in Fig. 16 (8), since the position of the rotation 28 of the can m is shifted, one end of the communication concave portion 128 is exemplified; the rib 13 is defined Plug. That is, the phase s is caused by the communication concave (four): the two pieces become non-connected (spaces adjacent to each other)

Si 工間S2 s成為非連通狀熊）。 319958 29 200905102 被此且的移動而變窄的空間内㈣油會 形成在滑動片u6側面的==成的石夕油流通路徑僅有 亦即，除了矽油所造成的黏性阻 矽油的I縮阻力也會附 ：阻力之外’ 的轉矩樺女，从锝千104而使作用於轉子1〇4 乂 7 #尼益100所造成的減震力會變大。 4 ，藉由環套108的旋轉，會透過環套1〇8的 面108Α與凸輪132的 狀衣套108的凸輪 沿著凸輪132_方^1咖，對職彈簧137賦予 復力）的狀態。 車由力’而成為蓄積有彈性能量（恢 環套：之=°4的旋轉速度變慢，且在轉子_ 旋彈箬137备r 剪力變得比該彈性能量還小時，螺 二H 原狀’且透過凸輪132使環套⑽返回 原本的位置，而如第..14圖 的滑動片收容1 122、… （）所示，使彼此相鄰 σ 連通（使彼此相鄰的空間Sl、空間S2 連通此，作祕轉子1G4之轉衫返 而:即，依據本實施形態，能對應轉子m的旋㈣ 104之轉矩改變。此外，藉由調整職 及根it 6、彈推力容易地改變轉子104的旋轉速度以 及低美'矩與高轉矩的切換位置。 ^卜’在轉子1〇4的外周面沿著轉子1〇4的轴方向設 峰與波谷波形的凸輪溝1〇6，且藉由轉子1〇4的 該凸輪溝嵌合的滑動片116沿著轉子104的軸方 口 “回移動’藉此能對應轉子1〇4的移動量而增加滑動片 319958 30 200905102 116 的移動晉。介 亦即，靶增大矽油的黏性阻力以及剪切阻 力。 藉由使各滑動片Π 6彼此錯開相位來移動，在 :動片11 6中’因在滑動片收容部】22内的位置不同，Si S2 s becomes a non-connected bear). 319958 29 200905102 The space that is narrowed by the movement of this (4) oil will form on the side of the sliding piece u6 == The flow path of the Shixia oil is only the same, except for the viscous oil which is caused by the oil The resistance will also be attached to: the torque outside the resistance', the damping force caused by the action of the rotor 1〇4 乂7 #尼益100 will increase. 4, by the rotation of the cuff 108, the cam 108 of the cuff 1 〇 8 and the cam of the sleeve 108 of the cam 132 are along the cam 132 _ _ _ _ _ _ _ _ _ . The car is accumulating by the force' and becomes the elastic energy (recovery ring: the rotation speed of °=°4 becomes slower, and the shear force of the rotor _ 箬 箬 箬 变得 变得 becomes smaller than the elastic energy, the snail 'And the ring sleeve (10) is returned to the original position by the cam 132, and as shown by the slide piece housing 1 122, ... () of Fig. 14 , the adjacent σ is connected to each other (the spaces S1 and spaces adjacent to each other) S2 is connected to this, and the rotor of the secret rotor 1G4 is returned: that is, according to the present embodiment, the torque of the rotary (four) 104 of the rotor m can be changed. Further, by adjusting the position and the root, the spring force is easily changed. The rotational speed of the rotor 104 and the switching position of the low-thickness and high torque. ^'The cam groove 1〇6 of the peak and the valley waveform is arranged along the axial direction of the rotor 1〇4 on the outer circumferential surface of the rotor 1〇4, Further, the sliding piece 116 fitted by the cam groove of the rotor 1〇4 is “returned” along the axial port of the rotor 104, whereby the movement of the sliding piece 319958 30 200905102 116 can be increased corresponding to the amount of movement of the rotor 1〇4. Jin. The target is that the target increases the viscous drag and shear resistance of the eucalyptus oil. The movable piece Π 6 is moved in a phase shifted from each other, and the position of the moving piece 161 in the sliding piece accommodating portion 22 is different.

故能改變每個潛叙y & — A 片收谷邛1 22所產生的轉矩，而可順暢 地曰減作用於轉子104之轉矩。 貝鈿形恶中，雖考慮到矽油的壓縮效率而將滑動 」作成從平面觀之呈圓孤狀，但由於滑W⑴係對 心片收容部122來形成，故未必要作成圓弧狀。 1D4 卜轉凸輪溝⑽的波數作成四㈤，且設成轉子 116 -次時滑動片116能四次來回移動，並將滑動片 ϊ 16作成二個，传）、晋叙^彳彳e τ人卜 便，月動片I16不會皆朝相同方向移動，但 ^可的變^凸輪溝1〇6的形狀（波的周期、波數等）或滑動片 、目，來调整滑動片116的脈動或轉矩等..。 ㈣亦可以將環套108設計成具有密封的功能，俾 轉子104的凸輪溝106内。此外，雖旋轉 :讀使連通凹物的位置錯開來進行轉矩切換 的流動。 内-置未圖不的閥’以控制矽油 接著，說明本發明第三實施形態的阻尼器。 大致5 ΐΠ至广弟19圖所示，於阻尼器200具備有作成 t致0同狀之有底外殼202。在此，為了方便說明 阻尸哭？nrJ 的上側、將底部側作為 P尼TO 200的下側，來進行各構件的說明。 319958 31 200905102 在該外殼202内填充石夕油，並從外殼m的㈣㈣ 著外殼2G2的周方向以間隔12Q。在三個地方突設有導引肋 部204。此外，於外殼202的底部中央凹設有大致圓柱狀 的安裝凹部206。 另一方面’在大致圓板狀的閥（第三流通路徑遮斷構 件）208的下面令央部突設有安裝凸部21〇，且可與安裝凹 部206喪合。在將該安裝凸部21〇嵌合在安裝凹部挪的 狀態下，閥208會變成可相對於外殼2〇2旋轉。 從閥208的外周面形成有朝與時鐘的旋轉方向相反的 方向（與後述的轉子244的祐## 士 a 旋片212，且沿著閥相反的方向)延伸的渴 地方。 8的周方向以間隔12〇。設置在三個 拉伸彈簧（第三彈推手段）？彳 旋"2的前端部，拉伸=二一端安裝在該满 9no . 坪” 214的另一端部安裝至外殼 的方向彈過:旋片212,將閥208朝與時鐘的旋轉方向相反 在閥2 0 8的上面中央部·罢士丄^ π m 91nh又置有大致圓柱狀的流通路徑 =…在該流通路徑體216凹設有 中央部以間隔120。伸展的三條流 連體： 218。流通路徑體216 #卜& , 峪仫C弟—連通路徑） 捏體2心 係形成凹狀的曲面，且流通路 且為面可載置由小球體220與大球體222所構成 為残痛狀（或葫蘆狀）的活塞體（搖動構件）224。成 另 方面’在外殼2 0 2内#可你六/以丁 狀的内部外殼225，'、收奋攸平面觀之呈圓弧 又225亚在内部外&郎的背面中央部沿著 319958 32 200905102 内部外殼225的高度方向凹設有導引溝226。該導引溝226 係可與外殼202的導引肋部204嵌合，並在導引肋部2〇4 嵌合在導引溝2 2 6的狀態下，使内部外殼不會旋轉。 此外，在内部外殼225的内側係可收容活塞體224的 大球體222，且在内部外殼225的内側收容有活塞體224 的大球體222的狀態下，活塞體224的小球體22〇係從内 部外殼225的上面露出。 為了收容活塞體224的大球體222，内部外殼225的 (内側係對應活塞體224的大球體222的形狀，除了内部外 殼225的上端部與下端部，均為具有凹狀的曲面228。在 該曲面228的中央部凹設有大致矩形狀的活塞收容部 230，並形成孔口 232，該孔口 232係從該活塞收容部230 的下緣部中央經由曲面228而朝向内部外殼225的下端部。 搔著，在活塞收容部230内可填充矽油，且活塞收容 部230内的矽油可在該孔口 232内流動。該孔口 232係可 (與形成在閥208的流通路徑體216的流通路徑218連通， 且如第21圖（A)所示，在孔口 232與流通路徑218的位置 一致的狀態下，活塞收容部23〇内的矽油可經由孔口 232 而μ向流通路徑218内。亦即，經由該流通路徑2丨8，彼 此相鄰的活塞收容部23〇會變成連通狀態。 不過，如第17圖至第19圖所示，在活塞體224的大 球體2 2 2的外周面，以間隔12 〇。在三個地方凹設有配合大 球體222的形狀而呈大致矩形狀的彎曲凹部。在該彎 曲凹部234的中央部凹設有大致圓柱狀的嵌入凹部236， 33 319958 200905102 而可嵌入設置在用以與彎曲凹部234嵌合之嵌合片2別内 面侧的嵌入突起240。 在將嵌入突起240嵌入在嵌入凹部236的狀態下，嵌 合片238的外面係變成與活塞體224的大球體222的外面 為齊平。此外，活塞（活塞構件）242係從嵌合片238的外 面中央部突出。此活塞242係被收容於活塞收容部23〇内。 此外，内部外殼225外周面的上部側係形成為小徑， 且在與外殼202的内周面之間設置有間隙。此間隙係可插 通環狀的導引片246,該導引片246係從兩段式構成的大 致圓柱狀的轉子244的大徑側的底部外緣垂下。 在轉子244的小徑側可連結用以傳達旋轉力的傳達構 件（未圖示），且在轉子244大徑側的底部抵接於内部外殼 225上面的狀態下，透過導引片246，轉子244會沿著外殼 202的周方向旋轉。 开 在轉子244的小徑側可插通環狀的蓋部248，且該蓋 部248係固定於外殼2〇2。藉此，阻止轉子⑽脫落^ 此，在蓋部248的内緣側下部凹設有〇形環安裝部25〇， 並安裝有0形環252。藉此，填充在外殼2〇2内的石夕油不 會漏出外部。 並且，在轉子244大輕侧的底部，從轉子244的軸芯 p移的位置形成有可連結活塞體224的小球體22〇之連結 部254,當藉由該連結部254來連結活塞體224的小球^ 22〇時’活塞體224係以傾斜的狀態载置於閥2〇8上。 接著，當轉子244旋轉時，活塞體224係透過小球體 319958 34 200905102 220而以'點P為中心而搖動。此時，如第22圖所示，雖然 活塞體224的活塞242係在活塞收容部230内一邊搖動一 邊上下移動，但各活塞242係彼此錯開相位來移動。 閥208係藉由安裝在渦旋片212的拉伸彈簧的彈 推力來疋位，且如第21圖（A)所示，形成在流通路徑體216 的流通路# 218會變成與活塞收容冑230的孔π 232連通 的位置。因此，活塞收容部23〇内的石夕油會經由孔口饥 、=動^姐# 218’並經由㈣通路徑218,使相鄰的 /基收容部230彼此會變成連通狀態。 彈4=面，如第21圖⑻所示，當藉由朝向抵抗㈣ ,"的無推力方向的應力而使閥208旋轉時，流通辟 從體216的流通路徑218 的孔口州… 移，活塞收容部23丨 因流、兩^ 流通路徑體216的周壁堵塞。亦即， 態 < 從218造成相鄰的活塞收容部23G變成非連通狀 如實施形態的阻尼器的作用。 虽轉子244低速旋轉時，雖然活塞; 動1上下移動/土 242會在活塞收容部230内-如 收容部230 =::= 23°内，會產i活塞242在活J 移動時在舆活=;Γ:產生的黏性阻力以及活塞24: 力。 邛230的内壁之間所產生的剪切陌 319958 35 200905102 机此、’ 士:帛19圖所示，當活塞242朝上方移動時，由 2置在活基242上端面與活塞收容部23()之間的間隙會 變窄:故會產切油所造成的壓縮阻力，但由於三個活^ 242係刀別錯開相位移動，故在活塞收容部内的位置 皆不同。 亦即’在設置在活塞242上端面與活塞收容部23〇之 間=間隙變窄的狀態下’在相鄰的活塞⑽上端面與活塞 收容部230間所構成的間隙會變寬。 因此’當活塞242朝下方移動時，由於活塞收容部23〇 内的石夕油會經由設置在該活塞收容部23〇的孔口挪，瘦 由閥m的流通路徑218而移動至相鄰的活塞收容部 230，故矽油所造成的壓縮阻力小。 _亦即，藉由活塞242的來回移動，矽油的黏性阻力及 剪切阻力所造成的轉矩主要會作用於轉子⑽。接著，前 述壓縮阻力會減少，其減少的部分會使作用於轉子244之 轉矩變小，故致振器200所提供的減震力小。 此外’雖然會因活塞體224的搖動而在間與活塞 體224之間產生剪力，但與活塞體m接觸的閥會藉由拉 伸彈簧214的彈推力而定位。 而田轉子244咼速旋轉時，在活塞體224與閥2〇8 之間所產生的剪力會變大，而超過拉伸彈簧214所產生的 :推力。如此，如第20圖⑻所示，當剪力變得比拉伸彈 簧214所產生的彈推力還大時，閥2〇8會旋轉。 如第21圖（B)所不，因閥208的旋轉’閥2〇8的流通 319958 36 200905102 ，徑m的位置會從活塞收容部咖的孔口 232的位置偏 移_ ^ ’活塞收容部23G❸孔口 232的端部會被流通路 ，體216的周壁堵塞’㈣流通路徑218造成相鄰活塞收 谷部230變成非連通狀態。 —因此’因活塞242的移動而變窄的空間内的矽油被壓 縮’石夕油所造成的I縮阻力會變得比轉+ 244料旋轉時 运大，因該麗、缩阻力，作用於轉子244之轉矩會增大。亦 即，阻尼态2 0 0所提供的減震力會變大。 在此’由於閥208會朝抵抗拉伸彈簧214的彈推力方 向移動’而變成在拉伸彈簧214#積有彈性能量（恢復力） 的狀態’故當轉子244的旋轉速度變十曼，在活塞體⑽與 閥208之間所產生的首力變得比該彈性能量還小時，如第 21圖⑷與第22圖⑷所示，拉伸彈簧214會恢復原狀並 使闕m回到原有位置，且如第21圖⑴所示，使相鄰的 活塞收容部23G連通。藉此，作用於轉子⑽之轉矩 回原本的狀態。 曰 亦即，依據本實施形態，能對應轉子244得旋轉速戶 ^吏作詩轉子244之轉矩改變。此外，藉由調整拉伸^ 簧214的彈推力’能容易地改變轉子244的旋轉速度以及 低轉矩與南轉矩的切換位置。 此外，將轉子244的旋轉力變換成活塞體224的搖動 力，使設置在活塞體224外周面的活塞242上下移動，藉 此月b對應轉子244的移動量而增加活塞242的移動量。 並且，藉由使各活塞242彼此錯開相位來移動，各活 319958 37 200905102 塞242在活塞收容部230内的位置亦不同。因此，能改變 在每個活塞收容冑230所產生的轉㊣，而卩順暢地增減作 用於轉子244之轉矩。 在此，如第18圖所示，雖於活塞體224的大球體222 凹設有彎曲凹部234，並形成與該彎曲凹部234嵌合的嵌 合片238,且於該嵌合片238設置活塞242，但如第以圖 所示，亦可將活塞體224的大球體222與活塞242 一體形 成。 此外，如第20圖（Α)及（Β)所示，在本實施形態中，雖 然使涡旋片212從閥2G8的外周面伸出，並在該渦旋片212 的前端部設置拉伸彈簧214，且藉由該拉伸彈酱214使闕 208朝與時鐘的旋轉方向相反的方向彈推，但此係轉子 的旋轉方向為單向時之構成。 因此，在轉子244進行正旋轉與逆旋轉的情形中，如 第24圖(Α)所示’係在渴旋片212的前端部延設朝内側折 曲的折曲部212Α，而在折曲部⑽與渦旋片212之間形 成鈍角’且在外殼202的内周面凹設有大致三角形的傾斜 部202Α，使渦旋片212沿著該傾斜部2〇2Α的形狀一邊 内側折曲一邊移動。 亦即’當因轉子244的旋轉（箭頭方向）而利用在 ^與活塞體224之間所產生的剪力使闕m旋轉時厂如 4像線所示，絲渦旋片212會沿著該傾斜部2G2A移動， t此時渦旋片212會彈性變形’藉此蓄積彈性能量（恢復 力。因此，該情形中，即不需要拉伸彈簧214。 319958 38 200905102 接著，當轉子244的旋轉速度變慢，且在 與闕2〇8之間所產生的剪力變得比該彈性能量還二： 實線所示，渦旋片212會恢復原狀，且閥208會返回 的位置（貫線所示的位置），作用於轉 、 原本的狀態。 之轉矩會返回 另一方面，在使轉子244逆旋轉的情形中，如 圖⑻所示，渦旋片212係順著傾斜部2m的形 會彈性變形，藉此二 一此外，除了第24圖（A)及（B)所示的構成外，亦可依未 方式’在外殼與閥之間配設扭轉彈菁’藉由該扭轉 贯來進行闕的周方向之定位。並且，藉由轉子的旋轉而 在轉子與活塞體之間產生剪力，使閥正旋轉與逆旋轉。在 此情形中，.由於扭轉彈簧可蓄積彈性能量，.故不需要渦 片 212。 接著，說明本發明的第四實施形態。 如第25圖至第26圖所示，於阻尼器3〇〇具備有大致 圓筒狀之有底外殼302。在此，& 了方便說明，係將外殼 =2的開口側作為阻尼器糊的上側、將底部側作為阻尼 器300的下側，來進行各構件的說明。 ^在外殼302的庳部中央凹設有軸孔308，該軸孔3〇8 2可軸支（用轴支撐）與傳達旋轉力之傳達構件（未圖示）連 的棒狀轉子304。此外，於外殼302的底部以間隔120。 °又有扇狀的收容部（液體室）31 〇，於該收容室31 〇内填充 39 319958 200905102 矽油，且以可搖動之方式收容大致扇狀的搖動體3i2。 在收容部310的底部形成有用以與設置在搖動體312 下面的軸部3H後合之軸孔315，且在該軸部314愈軸孔 315嵌合的狀態下，搖動體312可以轴部314為中心來搖 動。 在該搖動體312的上面，於軸部314的同轴上，立設 =部⑽’且於搖動體312的上面中央部沿著搖動體312 的半徑方向凹設有導引溝320。 士於外殼302内，大致圓板狀的導引板33〇係固設於外 ，302 ^底部，且於導引板33〇的中央部形成有供轉子綱 蚕通的貫通孔332。在轉子3〇4係對應貫通孔332凹設有〇 形，用安裝溝350’且在該〇形環用安裝溝35〇内安裝有〇 开》環3 5 2的狀態下’該〇形環俜 〜衣你囱接觸於貫通孔332的内 =面，.以使石夕油不會通過貫通孔332漏出至導引板33〇的 表面。 ，導引板咖以12〇。的間隔形成有：貫通孔334、以 盘形成在搖動體312的轴部316嵌合之轴孔335，並 與收容部310形成對庫。而B ^ ^一於相鄰的貫通孔334之間 成大致扇形之所謂的減厚邱q q 、士 f- 度較薄。 ，減厚部336的部分厚 338。該齒輪構 於該齒輪340 於貫通孔334内分別可安裝齒輪構件 件338的上部具備有齒輪（旋轉構件 的下邻δ又置大致圓柱狀的密封部⑽。 在該密封部3 4 2 的外周面形成0形環用安裝溝344 319958 40 200905102 裝溝344内安裝有〇形環346的狀態下，〇 由於貫通孔334的内周面，使石夕油不會經 〜貝通孔334而漏出至導引板33G的表面。 π的位ΐ Γ a封部342的背面，在從齒輪34G的軸芯偏 狀的導引凸柱(導弓丨突起跡因此，當 “ 疋轉時，導引凸柱348係以齒輪340的軸芯為中 心進行旋轉。 该導引凸柱348係可嵌合在凹設於搖動體312上面的 =〇°因此’如第28圖（A)至⑼所示，雖然藉由齒 :340的旋轉所進行的導引凸柱州的移動，搖動體312 1過與導引凸柱348嵌合的導引溝32〇來移動，但相對 引凸柱348所進行的圓孤移動，由於導引溝32〇為直 線形狀，故藉由該導引溝32〇,搖動體312會在收容部31〇 内以軸部314、316為中心進行搖動。 ^此時，導引凸柱348相對於齒輪34〇的位置，在每個 導引凸柱348皆不同’且導引凸柱348在各搖動體312的 導引溝320内的位置皆不同。在此，大齒輪脱係彼合在 輅子304，而可與轉子3〇4 —體旋轉。當該大齒輪354與 各齒輪340嚙合，且使轉子304旋轉時，藉由大齒輪354， 各齒輪340會旋轉。 士此外，將可插通轉子304之大致環狀的蓋體356係安 裝在外殼302。在該蓋體356下面凹設有定位凹部36〇，該 定位凹部360係供設置在齒輪34〇上面的定位凸部358嵌 合。在相當於蓋體356的導引板330的減厚部336之位置 319958 41 200905102 形成圓弧狀的開口 362。並且，從蓋體356内緣部的下面 突設有抵接肋部364，並抵接於大齒輪354上面。藉此， 阻止轉子304的脫落。 此外，如第29圖所示，在搖動體312的下面凹設有可 收容所謂銀杏葉型的閥（閉塞構件）321之收容凹部似。該 收容凹部324係形成為比閥321的形狀稍大，並使該閥32ι 於收容凹部324内可沿著搖動體312的搖動方向進行搖動 (參照第30圖（B)及（D))。 如第30圖⑴及⑻所示(註:第3〇圖⑷為第3〇圖⑻ =A-A箭頭方向剖面圖，第3〇圖（c)為第3〇圖⑶）的 前碩方向剖面圖），收容凹部324係在與構成闕321之直緣 =的閥部32“㈣部之間設置有間隙，且在收容該閥部 26的區域’形成有供石夕油沿著搖動體312的搖動方向通 、的流通路徑（減塵流通路徑）328。藉此，冑由搖動體 312’將一大致經分隔的收容部31〇變成連通狀態。 方面錯由搖動體312的搖動，收容凹部324内 2 321會藉由通過流通路經挪内的石夕油的黏性阻力而 而如第30圖（〇及⑻所示’當流通路徑328的一方 封閉時’藉由搖動體312，大致被分隔的收容 邛310會變成非連通狀態。 接著。兒明本發明的第四實施形態的阻尼器的作用。 34〇=二，示’當令轉子304低速旋轉時，各齒輪 夢由^lit輪354而旋轉。如第28圖⑴至⑻所示， 猎由邊齒輪340的旌媸，座 〕疋轉狄置在各齒輪340的導引凸柱348 319958 42 200905102 會以齒輪340的車由心為中心進行旋轉。藉此，透過盘導引 凸柱348後合的導引溝32〇,搖動 ； 内以軸部314、316為中心進行搖動。日在U训 在此，如第30圖⑴及（B)所示，由於收容凹部似Therefore, it is possible to change the torque generated by each of the submerged y & - A pieces, and smoothly reduce the torque acting on the rotor 104. In the case of the shellfish, the sliding is made to have a circular shape from the plan view in consideration of the compression efficiency of the eucalyptus oil. However, since the sliding W (1) is formed by the core accommodating portion 122, it is not necessary to form an arc shape. 1D4 The number of waves of the cam groove (10) is set to four (five), and is set to the rotor 116 - the sliding piece 116 can move back and forth four times, and the sliding piece ϊ 16 is made into two, pass), and the 彳彳 彳彳 e τ People, the moon moving piece I16 will not all move in the same direction, but the shape of the cam groove 1〇6 (wave period, wave number, etc.) or the sliding piece, the eye, to adjust the sliding piece 116 Pulsation or torque, etc. (d) The collar 108 can also be designed to have a sealing function within the cam groove 106 of the rotor 104. Further, although the rotation: reading shifts the position of the communicating concave to perform the torque switching flow. The inside of the valve is not shown to control the oil. Next, the damper according to the third embodiment of the present invention will be described. As shown in the figure of Fig. 19, the damper 200 is provided with a bottomed casing 202 which is formed in the same shape as 0. Here, for the sake of convenience, the corpse is crying? The upper side of the nrJ and the bottom side are referred to as the lower side of the P-Ni 200, and the description of each member is performed. 319958 31 200905102 The outer casing 202 is filled with Shishi oil, and is spaced from the (4) (four) outer casing m by the circumferential direction of the outer casing 2G2 at intervals 12Q. Guide ribs 204 are protruded at three places. Further, a substantially cylindrical mounting recess 206 is recessed in the center of the bottom of the outer casing 202. On the other hand, in the lower surface of the substantially disk-shaped valve (third flow path blocking member) 208, the mounting convex portion 21 is protruded from the central portion, and the mounting concave portion 206 can be comminuted. In a state where the mounting projection 21 is fitted in the mounting recess, the valve 208 becomes rotatable relative to the housing 2〇2. From the outer peripheral surface of the valve 208, a thirsty portion extending in a direction opposite to the direction of rotation of the clock (toward the rotor 212 of the rotor 244, which will be described later, and in the opposite direction of the valve) is formed. The circumferential direction of 8 is at intervals of 12 〇. Set in three tension springs (third push means)? The front end of the mediation "2, the extension = the second end is mounted on the full 9no. The other end of the ping" 214 is mounted in the direction of the outer casing: the rotary vane 212, the valve 208 is opposite to the direction of rotation of the clock In the upper center portion of the valve 208, the striker 丄^ π m 91nh is further provided with a substantially cylindrical flow path=...the flow path body 216 is recessed with a central portion at an interval of 120. The three continuations are extended: 218. Flow path body 216 #卜&, 峪仫C brother-connecting path) The pinch body 2 has a concave curved surface, and the flow path and the surface can be placed by the small sphere 220 and the large sphere 222. A painful (or gourd-like) piston body (shaking member) 224. In other respects, 'in the outer casing 2 0 2 #可你六/丁丁的内壳225, ', round the plane view The arc 225 is recessed with a guiding groove 226 in the central portion of the inner surface of the inner and outer lang; 319958 32 200905102. The guiding groove 226 is engageable with the guiding rib 204 of the outer casing 202. When the guide ribs 2〇4 are fitted in the guide groove 2 26, the inner casing is not rotated. The large spherical body 222 of the piston body 224 is accommodated inside the inner casing 225, and the small spherical body 22 of the piston body 224 is detached from the inner casing 225 in a state where the large spherical body 222 of the piston body 224 is housed inside the inner casing 225. In order to accommodate the large sphere 222 of the piston body 224, the inner casing 225 (the inner side corresponds to the shape of the large sphere 222 of the piston body 224, except for the upper end portion and the lower end portion of the inner casing 225, each having a concave curved surface 228. A substantially rectangular piston receiving portion 230 is recessed in a central portion of the curved surface 228, and an opening 232 is formed. The opening 232 extends from the center of the lower edge portion of the piston receiving portion 230 toward the inner casing via the curved surface 228. The lower end of the 225. The piston can be filled with the oil in the piston receiving portion 230, and the oil in the piston receiving portion 230 can flow in the opening 232. The opening 232 can be (through the flow path formed in the valve 208) The flow path 218 of the body 216 is in communication, and as shown in FIG. 21(A), in a state where the position of the orifice 232 and the flow path 218 are coincident, the oil in the piston housing portion 23 can be moved toward the hole 232 through the opening 232. Flow path In other words, the piston accommodating portion 23 adjacent to each other is in a communication state via the flow path 2丨8. However, as shown in Figs. 17 to 19, the large sphere 2 2 in the piston body 224. The outer peripheral surface of the second surface is provided with a substantially rectangular curved concave portion in a shape of a large spherical body 222, and a substantially cylindrical embedded concave portion 236 is recessed in a central portion of the curved concave portion 234. 33, 319958 200905102, the insertion protrusion 240 provided on the inner surface side of the fitting piece 2 to be fitted to the curved concave portion 234 can be fitted. In a state where the fitting projection 240 is fitted in the fitting recess 236, the outer surface of the fitting piece 238 becomes flush with the outer surface of the large spherical body 222 of the piston body 224. Further, the piston (piston member) 242 protrudes from the outer central portion of the fitting piece 238. The piston 242 is housed in the piston housing portion 23A. Further, the upper side of the outer peripheral surface of the inner casing 225 is formed to have a small diameter, and a gap is provided between the inner peripheral surface of the outer casing 202. This gap is inserted into the annular guide piece 246 which hangs from the bottom outer edge of the large-diameter side of the two-stage substantially cylindrical rotor 244. A transmission member (not shown) for transmitting a rotational force is coupled to the small-diameter side of the rotor 244, and the guide piece 246 is passed through the guide piece 246 in a state where the bottom portion of the large-diameter side of the rotor 244 abuts against the upper surface of the inner casing 225. The 244 will rotate in the circumferential direction of the outer casing 202. The annular cover portion 248 is inserted into the small diameter side of the rotor 244, and the cover portion 248 is fixed to the outer casing 2〇2. Thereby, the rotor (10) is prevented from coming off, and the ring-shaped ring mounting portion 25 is recessed in the lower portion of the inner edge side of the lid portion 248, and the O-ring 252 is attached. Thereby, the Shixia oil filled in the outer casing 2〇2 does not leak out of the outside. Further, a coupling portion 254 of the small spherical body 22 that can connect the piston body 224 is formed at a position shifted from the axial center p of the rotor 244 at the bottom portion of the rotor 244, and the piston portion 224 is coupled by the coupling portion 254. The small ball ^ 22 〇 'the piston body 224 is placed on the valve 2 〇 8 in an inclined state. Next, as the rotor 244 rotates, the piston body 224 is oscillated about the 'point P' through the small spheres 319958 34 200905102 220. At this time, as shown in Fig. 22, the piston 242 of the piston body 224 moves up and down while being rocked in the piston housing portion 230, but the pistons 242 are shifted from each other in phase. The valve 208 is clamped by the elastic force of the tension spring attached to the scroll piece 212, and as shown in Fig. 21(A), the flow path #218 formed in the flow path body 216 becomes into contact with the piston. The position of the hole π 232 of 230 is connected. Therefore, the Shixia oil in the piston accommodating portion 23 will pass through the venting port, and the adjacent/base accommodating portion 230 will be brought into communication with each other via the (4) through path 218. The spring 4=face, as shown in Fig. 21 (8), when the valve 208 is rotated by the stress in the thrust-free direction against (4), "" the orifice state of the flow path 218 of the body 216 is shifted The piston housing portion 23 is blocked by the flow and the peripheral wall of the flow path body 216. That is, the state < from 218 causes the adjacent piston housing portion 23G to become non-connected, as in the damper of the embodiment. Although the rotor 244 rotates at a low speed, although the piston; the moving 1 up/down movement/the soil 242 will be in the piston accommodating portion 230 - such as the accommodating portion 230 =::= 23°, the i-piston 242 will be active during the moving J movement. =; Γ: the resulting viscous drag and the piston 24: force. The shearing force generated between the inner walls of the crucible 230 is 319958 35 200905102. Here, as shown in Fig. 19, when the piston 242 is moved upward, 2 is placed on the upper end surface of the movable base 242 and the piston receiving portion 23 ( The gap between them will be narrowed: the compression resistance caused by the cutting oil will be produced, but since the three movable 242 knives do not shift in phase, the positions in the piston accommodating portion are different. That is, the gap formed between the upper end surface of the adjacent piston (10) and the piston accommodating portion 230 is widened in a state where the gap between the upper end surface of the piston 242 and the piston accommodating portion 23 is narrowed. Therefore, when the piston 242 moves downward, the Shiyue oil in the piston housing portion 23 is moved through the opening provided in the piston housing portion 23, and is thinned by the flow path 218 of the valve m to the adjacent one. Since the piston housing portion 230 is used, the compression resistance caused by the oil is small. That is, by the back and forth movement of the piston 242, the torque caused by the viscous resistance of the oil and the shear resistance mainly acts on the rotor (10). Then, the compression resistance is reduced, and the reduced portion causes the torque acting on the rotor 244 to be small, so that the shock absorbing force provided by the vibrator 200 is small. Further, although a shear force is generated between the piston body 224 and the piston body 224 due to the rocking of the piston body 224, the valve in contact with the piston body m is positioned by the spring force of the tension spring 214. When the rotor 244 rotates at an idling speed, the shear force generated between the piston body 224 and the valve 2〇8 becomes larger, and exceeds the thrust generated by the tension spring 214. Thus, as shown in Fig. 20 (8), when the shear force becomes larger than the spring force generated by the tension spring 214, the valve 2 〇 8 is rotated. As shown in Fig. 21(B), due to the rotation of the valve 208, the flow of the valve 2〇8 is 319958 36 200905102, the position of the diameter m is offset from the position of the orifice 232 of the piston housing portion _ ^ 'piston housing portion The end of the 23G port 232 is blocked by the flow path, and the peripheral wall of the body 216 is blocked. (4) The flow path 218 causes the adjacent piston receiving portion 230 to become non-connected. - Therefore, the squeegee in the space narrowed by the movement of the piston 242 is compressed, and the I-shrinkage resistance caused by the Shixia oil becomes larger than that of the rotation + 244 material, because the yoke and the contraction resistance act on The torque of the rotor 244 will increase. That is, the damping force provided by the damped state 200 will become larger. Here, 'because the valve 208 moves toward the elastic thrust direction against the tension spring 214', the elastic spring (recovery force) is accumulated in the tension spring 214#, so when the rotational speed of the rotor 244 becomes ten, in The first force generated between the piston body (10) and the valve 208 becomes smaller than the elastic energy. As shown in Figs. 21(4) and 22(4), the tension spring 214 is restored to its original state and the 阙m is returned to the original state. At the position, as shown in Fig. 21 (1), the adjacent piston accommodation portions 23G are communicated. Thereby, the torque acting on the rotor (10) is returned to the original state. That is, according to the present embodiment, the torque of the rotor 244 can be changed in accordance with the rotor 244. Further, the rotational speed of the rotor 244 and the switching position of the low torque and the south torque can be easily changed by adjusting the spring force ' of the tension spring 214. Further, the rotational force of the rotor 244 is converted into the rocking force of the piston body 224, and the piston 242 provided on the outer peripheral surface of the piston body 224 is moved up and down, whereby the amount of movement of the piston 242 is increased in accordance with the amount of movement of the rotor 244. Further, by moving the pistons 242 in phase with each other, the position of each of the plugs 242 in the piston housing portion 230 is different. Therefore, it is possible to change the positive rotation generated at each of the piston housings 230, and smoothly increase or decrease the torque applied to the rotor 244. Here, as shown in Fig. 18, the large spherical body 222 of the piston body 224 is recessed with the curved concave portion 234, and the fitting piece 238 fitted to the curved concave portion 234 is formed, and the fitting piece 238 is provided with a piston. 242, but as shown in the figure, the large sphere 222 of the piston body 224 may be integrally formed with the piston 242. Further, as shown in Fig. 20 (Α) and (Β), in the present embodiment, the scroll piece 212 is extended from the outer peripheral surface of the valve 2G8, and the end portion of the scroll piece 212 is stretched. The spring 214 pushes the crucible 208 in a direction opposite to the rotation direction of the clock by the stretched ejector 214, but the rotation direction of the rotor is one-way. Therefore, in the case where the rotor 244 performs the forward rotation and the reverse rotation, as shown in Fig. 24 (Α), the bent portion 212 折 which is bent inward is extended at the front end portion of the thirteen fins 212, and is bent. An obtuse angle ' is formed between the portion (10) and the scroll piece 212, and a substantially triangular inclined portion 202Α is recessed in the inner circumferential surface of the outer casing 202, and the scroll piece 212 is bent inside along the shape of the inclined portion 2〇2Α. mobile. That is, when the 阙m is rotated by the shear force generated between the rotor and the piston body 224 due to the rotation of the rotor 244 (the direction of the arrow), as shown by the 4-line, the wire scroll 212 will follow the The inclined portion 2G2A moves, t at which the scroll 212 is elastically deformed 'by thereby accumulating elastic energy (recovery force. Therefore, in this case, the tension spring 214 is not required. 319958 38 200905102 Next, when the rotational speed of the rotor 244 Slower, and the shear force generated between the 阙2〇8 becomes two times higher than the elastic energy: as shown by the solid line, the scroll 212 will return to its original shape, and the valve 208 will return to the position (the line The position shown is applied to the state of the rotation and the original state. The torque will return to the other side. In the case where the rotor 244 is reversely rotated, as shown in (8), the scroll piece 212 is formed along the inclined portion 2m. Elastically deformed, in addition to the configuration shown in Fig. 24 (A) and (B), it is also possible to arrange a torsional elastic between the outer casing and the valve by means of the non-method To position the circumferential direction of the crucible, and the rotor and the piston body by the rotation of the rotor The shear force is generated to cause the valve to rotate positively and reversely. In this case, since the torsion spring can accumulate elastic energy, the scroll 212 is not required. Next, a fourth embodiment of the present invention will be described. As shown in Fig. 26, the damper 3A is provided with a substantially cylindrical bottomed casing 302. Here, for convenience, the opening side of the casing = 2 is used as the upper side of the damper paste, and The bottom side serves as the lower side of the damper 300 for the description of each member. ^ A shaft hole 308 is recessed in the center of the crotch portion of the outer casing 302, and the shaft hole 3〇8 2 can be pivoted (supported by the shaft) and conveys rotation. The rod-shaped rotor 304 to which the force transmitting member (not shown) is connected. Further, at the bottom of the outer casing 302, there is a gap of 120. The fan-shaped housing portion (liquid chamber) 31 is filled in the housing chamber 31. 39 319958 200905102 矽 oil, and swayably accommodates a substantially fan-shaped oscillating body 3i2. A shaft hole 315 is formed at the bottom of the accommodating portion 310 to be engaged with the shaft portion 3H disposed under the oscillating body 312, and In a state where the shaft portion 314 is engaged with the shaft hole 315, the rocking body 312 can be The shaft portion 314 is pivoted about the center. On the upper surface of the rocking body 312, the portion (10)' is erected on the coaxial portion of the shaft portion 314, and is recessed along the radial direction of the rocking body 312 at the upper center portion of the rocking body 312. There is a guiding groove 320. In the outer casing 302, a substantially disc-shaped guiding plate 33 is fixedly attached to the outside, 302 ^ bottom, and a central portion of the guiding plate 33 is formed with a rotor for the rotor The through hole 332 is formed in a meandering shape in the rotor 3〇4 corresponding to the through hole 332, and the mounting groove 350' is attached to the ring-shaped mounting groove 35〇 in the state in which the ring 3 5 2 is attached. The 〇-shaped ring 俜 衣 囱 囱 接触 接触 接触 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 332 The guide board is 12 inches. The space is formed by a through hole 334 and a shaft hole 335 in which the disk portion 316 of the rocking body 312 is fitted, and is formed in a space with the housing portion 310. The B ^ ^ is a substantially fan-shaped so-called reduced thickness q q , and the f - degree is thinner between the adjacent through holes 334. The portion of the reduced thickness portion 336 is 338 thick. The gear is disposed in the through hole 334, and the upper portion of the gear member 338 is provided with a gear (the lower portion of the rotating member is adjacent to the δ and the substantially cylindrical sealing portion (10). The outer periphery of the sealing portion 341 The surface of the O-ring mounting groove 344 319958 40 200905102 In the state in which the ring 346 is attached to the groove 344, the inner peripheral surface of the through hole 334 prevents the stone from leaking through the through hole 334. To the surface of the guide plate 33G. The position of π ΐ Γ The back surface of the seal portion 342, the guide post that is deflected from the axis of the gear 34G (the guide bow projection, therefore, when "turning, guiding The stud 348 is rotated about the axis of the gear 340. The guiding stud 348 can be fitted to the recess 凹 recessed on the rocking body 312 so as shown in Fig. 28 (A) to (9) The moving body 312 1 moves through the guiding groove 32 嵌合 fitted with the guiding post 348 by the movement of the guiding stud state by the rotation of the tooth 340, but is performed with respect to the guiding post 348. The circular orphan movement, because the guiding groove 32 is linear, the rocking body 312 will be in the receiving portion 31 by the guiding groove 32 The inside of the crucible is pivoted about the shaft portions 314, 316. ^ At this time, the position of the guiding stud 348 relative to the gear 34 , is different at each of the guiding studs 348 and the guiding studs 348 are shaken at each The position of the guiding groove 320 of the body 312 is different. Here, the large gear is detached from the tweezer 304 and can rotate integrally with the rotor 3 〇 4. When the large gear 354 meshes with each gear 340, and When the rotor 304 is rotated, the gears 340 are rotated by the large gear 354. Further, a substantially annular cover 356 that can be inserted into the rotor 304 is attached to the outer casing 302. The cover 356 is recessed under the cover 356. The positioning recess 36 is fitted to the positioning convex portion 358 provided on the upper surface of the gear 34. The position of the thickened portion 336 of the guide plate 330 corresponding to the cover 356 is 319958 41 200905102. The opening 362. The abutting rib 364 is protruded from the lower surface of the inner edge of the cover 356, and abuts against the large gear 354. Thereby, the falling of the rotor 304 is prevented. Further, as shown in Fig. A valve (occlusion member) 321 capable of accommodating a so-called ginkgo leaf shape is recessed under the oscillating body 312 The receiving recess 324 is formed to be slightly larger than the shape of the valve 321 , and the valve 32 ι can be rocked in the accommodating recess 324 along the rocking direction of the oscillating body 312 (refer to FIG. 30(B) and (D)). As shown in Figure 30 (1) and (8) (Note: Figure 3 (4) is the third diagram (8) = AA arrow direction profile, and the third diagram (c) is the third diagram (3)) In the front cross-sectional view, the housing recess 324 is provided with a gap between the "fourth" portion of the valve portion 32 constituting the straight edge of the crucible 321 and is formed in the region where the valve portion 26 is accommodated. A flow path (dust reduction flow path) 328 in which the rocking direction of the rocking body 312 is turned. Thereby, the substantially separated compartment 31 is turned into a communicating state by the rocking body 312'. The error is caused by the shaking of the rocking body 312, and the 2321 in the receiving recess 324 is passed through the flow path through the viscous resistance of the stone oil as shown in Fig. 30 (〇 and (8)' when the flow path 328 When one is closed, the substantially accommodating pocket 310 will be in a non-connected state by the rocking body 312. Next, the function of the damper according to the fourth embodiment of the present invention will be described. 34〇=2, indicating 'When the rotor 304 At the low speed rotation, each gear dream is rotated by the ^lit wheel 354. As shown in Fig. 28 (1) to (8), the shackle of the side gear 340 is seated on the guide boss 348 of each gear 340. 319958 42 200905102 will rotate around the center of the car of the gear 340. Thereby, the guide groove 32 后 after the disk guide post 348 is swayed and shaken; the inner portion is swung around the shaft portions 314 and 316. In U training, as shown in Figure 30 (1) and (B), because of the containment recess

係在與閥3 2 1的閥部3 2 fi的ifr W 4丨的削糙部之間設置有間隙，且在 收谷該閥部326的區域沿著搖動體312的搖動方向設置有 石夕油可通過的流通路謂’故當搖動體312 搖動體312推開㈣油會在該流通路徑⑽流動，而被導 引至與搖動體312的前進方向相反側的區域。 亦即，由於該搖動體312的搖動，雖然會在收容部31〇 產生搖動體312授拌石夕油所產生的黏性阻力、以及搖動 ，312搖動時在與收容部31〇的内壁之間所產生的剪切阻 仁由於因搖動體312的搖動而在收容部別内被壓 的壓縮阻力較小，故作用於轉子3〇4之轉矩小，且阻尼器 300所提供的減震力小。 古另—方面，當令轉子304高速旋轉時，藉由搖動體312 的门速說轉，㊉油所造成的黏性阻力會增加。藉此，如第 3〇圖（C)及（D)所示，搖動體312内的目321會搖動，而閉 塞減㈣㈣通路徑328的—方。因此，在收容部31〇内， 石夕油曰被搖動體312麼、縮，而會增大壓縮阻力，作用於轉 子3 0 4之轉矩;^ + 土 £ 3大’使阻尼器300所提供的減震力變大。 在此’當轉子304的旋轉速度變慢，石夕油所造成的黏 性阻力變小時，關q 9 勾1 a搖動而返回原本的位置（收容凹部 324的中央部），丄，办 且错由搖動體312使大致經分隔的收容部 43 319958 200905102 3態1〇。連通。藉此’作用於轉子m之轉矩會返回原本的狀 來使：虞本實施形態，能對應轉子304的旋轉速度 !: 304之轉矩改變。此外，藉由調筆1 々搖動力’月b谷易地改、變錄早λα 與高轉矩之切換位置。的疑轉速度以及低轉矩 鏺播！>匕外’透過會輪340來加速轉子304的旋轉速度，並 韓㈣ΐ動體312的搖動力，藉此能相對於轉子304的旋 轉私動置而增加搖動體312的移動量。 並且’使各搖動體312彼此錯開相位移動 動體312在收容部川内的位置會不同。因此，能改變在 子3〇4之轉矩。 W矩而可順暢地增減作用於轉 在此，大齒輪354與齒輪340的齒面接觸所造成的摩 力或導引凸柱348在導引溝320移動時所造成的滑動 ^且力專雖均變成作用於轉子3〇4之轉矩，但由於僅是說明 错由矽油所作用之轉矩’故省略此等阻力的說明。 如上所述，依據這些實施形態的阻尼器，除了拉出構 =外’亦能設置於拉門、輪椅的車輪、百葉窗、寵物的 牽鍊、鋼琴蓋、行李箱、以及汽車的置物箱等，且當移動 構件的移動速度變成預定值以上時，由於透過轉子合使阻 尼器所提供的減震力變大，故能使移動構件的移動減速。 、此外，由於本發明只要為當轉子的旋轉速度達預定值 Μ上時’液體室彼此間變成非連通狀態；當轉子的旋轉速 319958 44 200905102 度變成未達預定值時，兮 予5亥液體至彼此間變成連通狀能之播 造即可，故本發明邗尤— λ 心之構 月I不限疋於以上的實施形態。 【圖式簡單說明] 第1圖係顯示本發明第 體圖。 月弟貝鉍形悲的阻尼器之剖面立 第2圖係顯示本發明第 體圖。 弟只轭形悲的阻尼器之分解立 弟3圖係顯示太蘇日日赞 ^ x月弟一貫施形態的阻尼器之剖面 圖。 第上圖(A)及⑻係顯示用以構成本發明第一實施形態 的阻尼益之内部構件動作之平面圖。 〜 第5圖係顯示用以構成本發明第一 之板體與蓋部之立體圖。 。们丨且尼益 第6圖係顯示本發明第—實施形態的阻尼器之平面 =A)為彼此相鄰的空間成為連通的狀態，⑻為彼 ;鄰的空間成為不連通的狀態。 第7圖係用以說明本發明筮 ^ _ .t 知月弟—實施形態的阻尼器的作A gap is provided between the roughened portion of the ifr W 4丨 of the valve portion 3 2 fi of the valve 3 2 1 , and a region is provided along the rocking direction of the swinging body 312 in the region of the valve portion 326. The flow path through which the oil can pass is so that when the oscillating body 312 is pushed away by the oscillating body 312, the oil flows in the flow path (10) and is guided to a region on the side opposite to the advancing direction of the oscillating body 312. That is, due to the shaking of the oscillating body 312, the viscous resistance generated by the swaying body 312 is applied to the accommodating portion 31, and the viscous resistance generated by the slick oil is shaken, and between the 312 and the inner wall of the accommodating portion 31, when the 312 is shaken. Since the shear resistance generated by the shearing resistor is less due to the shaking of the rocking body 312 in the housing portion, the torque acting on the rotor 3〇4 is small, and the damping force provided by the damper 300 is small. small. In other respects, when the rotor 304 is rotated at a high speed, the viscous resistance caused by the oil is increased by the door speed of the rocking body 312. Thereby, as shown in Figs. 3(C) and (D), the head 321 in the rocking body 312 is shaken, and the (4) (four) through path 328 is closed. Therefore, in the accommodating portion 31, the Shixia oil shovel is swayed by the swaying body 312, and the compression resistance is increased, and the torque acting on the rotor 306 is applied; ^ + soil is £3, which makes the damper 300 The damping force provided is increased. Here, when the rotational speed of the rotor 304 is slowed, the viscous resistance caused by the Shixia oil becomes small, and the hook 9 a is shaken to return to the original position (the central portion of the housing recess 324), oh, wrong and wrong. The substantially separated accommodating portion 43 319958 200905102 is 1 〇 by the oscillating body 312. Connected. Thereby, the torque acting on the rotor m returns to the original state, so that the torque of the rotor 304 can be changed in accordance with the present embodiment. In addition, by adjusting the pen 1 々 动力 ’ ’ 月 b 谷 谷 易 易 易 易 易 易 易 易 易 易 ’ ’ ’ ’ ’ ’ ’ ’ ’ Suspected speed and low torque broadcast! > 匕 ’ 加速 加速 会 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 340 Further, the positions in which the respective oscillating bodies 312 are shifted from each other in phase are different in the position of the accommodating portion. Therefore, the torque at sub 3〇4 can be changed. The W moment can smoothly increase or decrease the sliding force caused by the contact between the large gear 354 and the tooth surface of the gear 340 or the sliding of the guiding protrusion 348 when the guiding groove 320 moves. Although they all become the torque acting on the rotor 3〇4, since only the torque acting on the squeegee is explained, the description of the resistance is omitted. As described above, the damper according to these embodiments can be provided in the sliding door, the wheel of the wheelchair, the blinds, the pet's chain, the piano cover, the trunk, and the storage compartment of the car, in addition to the pull-out configuration. Further, when the moving speed of the moving member becomes a predetermined value or more, since the damping force provided by the damper is increased by the rotor coupling, the movement of the moving member can be decelerated. Further, since the present invention is such that the liquid chambers become non-connected with each other when the rotational speed of the rotor reaches a predetermined value ;; when the rotational speed of the rotor becomes 319958 44 200905102 degrees becomes less than a predetermined value, It is only necessary to be able to spread the connectivity to each other. Therefore, the configuration of the present invention is not limited to the above embodiments. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a view showing the first embodiment of the present invention. The section of the damper of the moon-shaped bellows is shown in Fig. 2 to show the first figure of the present invention. Decomposition of the yoke-shaped damper of the younger brother. The 3rd picture shows the cross-section of the damper that has been applied to the form of the moon. The above figures (A) and (8) show plan views showing the operation of the internal member constituting the damping benefit of the first embodiment of the present invention. ~ Fig. 5 is a perspective view showing a plate body and a lid portion for constituting the first aspect of the present invention. . In the sixth diagram, the plane of the damper according to the first embodiment of the present invention is a state in which spaces adjacent to each other are in communication, and (8) is a state in which the adjacent spaces are not in communication. Figure 7 is a diagram for explaining the damper of the present invention 筮 ^ _ .t

用之曲線圖。 F 第8圖係用以說明本發明筮 弟一貫施形態的阻尼器之變 形例的作用之曲線圖。 艾 第9圖係顯示用以構成本發明第一實施形態的阻尼哭 之板體的變形例之立體圖。 σ 圖。第10圖係顯示本發明第二實施形態的阻尼器之立體 319958 45 200905102 立體^ U圖係顯示本發明第二實施形態的阻尼器之分解 弟12圖係顯示本發明第二實施形態的阻尼器之剖面 哭之I Γ圖係顯示用以構成本發明第二實施形態的阻尼 之轉子與滑動片的關係。 :Η圖係顯示本發明第二實施形態的阻尼器之剖面 —且相鄰的空間彼此為連通的狀態。 :15圖係顯示本發明第二實施形態的阻尼器之剖面 圖，且相鄰的空間彼此為非連通的狀態。 第16圖係顯示本發明第二實施形態的阻尼器 ===此為連通的狀態， 立體=7.圖係顯示本發明第三實施形態的阻尼器之分解 ”圖係顯示本發明第三實施形態的 部分之分解立體圖。 j土要 圖。第19圖係顯示本發明第三實施形態的阻尼器之剖面 能的^尸如圖⑴及⑻係顯示用以構成本發明第三實施形 ,〇、的阻尼态之閥的位置之平面圖。 ' 第21圖係顯示本發明第三實 面圖，⑷為相鄰的空間彼此為連的阻尼器之橫剖 空間彼此為不連通的狀態。 ' ® ’⑻為相鄰的 3]9958 46 200905102 第22圊係說明用以構成本發明第三實施形態的阻尼 器之活塞的動作之剖面圖。 第23圖係顯示本發明第三實施形態的阻尼器的主要 部分的變形例之分解立體圖。 第24圖（A)及（B)係顯示用以構成本發明第三實施形 悲的阻尼器之閥的變形例之平面圖。 弟25圖係顯示本發明第四實施形態的阻尼哭 立體圖。 〇〇 肝Use the graph. F Fig. 8 is a graph for explaining the action of a modified example of the damper of the present invention. Fig. 9 is a perspective view showing a modification of the damped crying plate body constituting the first embodiment of the present invention. σ map. Figure 10 is a perspective view showing a damper of a second embodiment of the present invention. 319958 45 200905102 A perspective view showing a damper of a second embodiment of the present invention showing a damper according to a second embodiment of the present invention. The cross-sectional view of the cross-section shows the relationship between the damper rotor and the sliding sheet constituting the second embodiment of the present invention. The plan view shows a cross section of the damper according to the second embodiment of the present invention - and the adjacent spaces are in communication with each other. Fig. 15 is a cross-sectional view showing the damper according to the second embodiment of the present invention, and the adjacent spaces are in a non-connected state. Figure 16 is a view showing a damper according to a second embodiment of the present invention === this is a state of communication, and a stereoscopic figure is 7. The figure shows an exploded view of the damper according to the third embodiment of the present invention. An exploded perspective view of a portion of the form. Fig. 19 is a view showing the cross-sectional energy of the damper according to the third embodiment of the present invention, and Figs. (1) and (8) are shown to constitute a third embodiment of the present invention. A plan view of the position of the damper state valve. '21 is a third solid view of the present invention, and (4) is a state in which the cross-sectional spaces of the dampers adjacent to each other are not in communication with each other. '(8) is adjacent 3]9958 46 200905102 Section 22 is a cross-sectional view showing the operation of the piston constituting the damper according to the third embodiment of the present invention. Fig. 23 is a view showing the damper according to the third embodiment of the present invention. Fig. 24(A) and (B) are plan views showing a modification of the valve for constituting the damper of the third embodiment of the present invention. Fig. 25 shows the present invention. Damping of the fourth embodiment Figure thousand and liver

第2 6圖係顯示本發明筮鲁A 圖 χ β弟四貫施形態的阻尼器之剖面 第2 7圖係顯示本發明第每 圖 a罘四貝施形態的阻尼器之平面 / 28®⑴至⑻係顯示用以構成本發明第 態的阻尼器之齒輪的導引凸柱盥 、形 t 29 FI^is - a ”搖動體的關係之平面圖。 弟29圖係顯不用以構成本 哭之搖動驴丁 ；从操〇·、 X月弟四貝施形恶的阻尼 之搖動體下面的構成之分解立體圖。 第30圖（Β)及（D)係顯示用 & , 用以構成本發明笫ra隹^ Α π 悲的阻尼器之搖動體的閥的動 貝轭形 Α-Α箭頭方向剖面圖，（c) 二，（Α)為（Β)的 【主要元件符號說明】’、、、白、β—β箭頭方向剖面圖。 、100、200、300 阻尼器 12 ' 102、202、302 外殼 14 1β 左人Λ 14 固定片 16 餘擺線齒形部（第'終 乐一餘擺線齒形部） 16Α、18Α 齒部 319958 47 200905102 18餘擺線齒形部（第—餘擺線齒形部） 2〇 内部構件（偏心構件）22、104、244、304 轉子 24、314、316、318 轴部 26 心部 28^140 30板體（第一流通路徑遮斷構件 110 〇形環安裝溝 32、 34、 36 40、 44 50 54 56 58 106 108 108A 109A 116 118 120、 122 124 嵌合凹部 6 0肋部 孔部 嵌合部 圓弧肋部 台座部 流通路徑可變手段） 346 、 352 〇形環 38 嵌合凸部 42 、 248 蓋部 48 溝部 52 環狀肋部 扭轉彈簧(第—彈推手段 圓弧溝 抓通路！可變手段） 62 _ 凸輪溝（凸輪手段) 一角肋部 %套(第二流通路徑遮 132A凸輪面 机通路徑可變手段）Figure 26 shows a section of the damper of the present invention. Figure 27 shows the plane of the damper of the first embodiment of the present invention. / 28®(1) To (8) is a plan view showing the relationship between the guide studs and the shape t 29 FI^is - a "shake body" of the gears constituting the damper of the first aspect of the present invention. The brother 29 shows that the figure does not need to constitute the crying Shake the shackles; an exploded perspective view of the structure below the damped body of the damper of the X-ray 四 、 。 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第 第笫ra隹^ Α π sorrow of the damper of the damper of the damper yoke Α-Α arrow direction cross-sectional view, (c) two, (Α) is (Β) [main component symbol description] ', , white, β-β arrow direction profile., 100, 200, 300 damper 12 ' 102, 202, 302 housing 14 1β left man Λ 14 fixed piece 16 trochoid tooth profile (the first 'final after a pendulum Line toothed part) 16Α, 18Α Toothed part 319958 47 200905102 18 trochoidal tooth profile (partial trochoidal tooth profile) 2〇Internal component (eccentric structure) 22), 104, 244, 304 rotor 24, 314, 316, 318 shaft portion 26 core portion 28^140 30 plate body (first flow path blocking member 110 〇 ring mounting groove 32, 34, 36 40, 44 50 54 56 58 106 108 108A 109A 116 118 120, 122 124 fitting recess 60 rib hole fitting fitting arc rib pedestal flow path variable means 346 , 352 〇 ring 38 fitting projection 42 248 Cover portion 48 Groove portion 52 Annular rib torsion spring (first - spring push means circular groove catching passage! Variable means) 62 _ Cam groove (cam means) One corner rib % set (second flow path cover 132A cam Variable machine path

109 段差 、 114 滑動片（移動構件） 嵌合突起（凸輪手段） 232 孔口 滑動片收容部（液體室） 内蓋 124A 小徑部 矩形孔 環狀部 319958 48 200905102 126 凸緣部 130 界定肋部 134 定位溝 137 扭轉彈簧 138 段部 128 132 136 第二彈推手段、 142 142A、1G2A螺紋部 連通凹部 凸輪 定位肋部 机通路徑可變手段） 外蓋 144、146、250 0形環安裝部 導引肋部 ♦通路徑可變手段） 202A 傾斜部 2()4109 step difference, 114 slide (moving member) fitting projection (cam means) 232 orifice slide accommodating portion (liquid chamber) inner cover 124A small diameter portion rectangular hole annular portion 319958 48 200905102 126 flange portion 130 defining rib 134 Positioning groove 137 Torsion spring 138 Segment 128 132 136 Second spring pushing means, 142 142A, 1G2A threaded part communicating recessed cam positioning rib machine path variable means) Cover 144, 146, 250 0-ring mounting part guide Leading ribs ♦ pass path variable means) 202A inclined part 2 () 4

206 安裝凹部 208閥（弟二流通路徑遮斷構件 210 安裝凸部206 mounting recess 208 valve (different flow path blocking member 210 mounting convex portion

212 212A 滿旋片（第三彈推手段、流通路徑 折曲部 可變手段） 彈推手段、流通路徑可變手段） 214 拉伸彈簧（第 216 流通路徑體 220 小球體 224 活塞體（搖動構件） 226 導引溝 230活塞收容部（液體室 234 彎曲凹部 238 喪合片 242 活塞（活塞構件） 254 連結部 312 搖動體 218 流通路徑 222 大球體 225 内部外殼 228 曲面 236 嵌入凹部 240 嵌入突起 246 導引片 310 收容部（液體室 315 、 335 軸孔 49 319958 200905102 320 導引溝 321 閥（閉塞構件） 324 收容凹部 326 閥部 328 流通路徑（減壓流通路徑） 330 導引板 332 、 334 貫通孔 336 減厚部 338 齒輪構件 340 齒輪（旋轉構件） 342 密封部 344、 350 0形環用安裝溝 348 導引凸柱（導引突起） 354 大齒輪 356 蓋體 358 定位凸部 362 開口 354 抵接肋部 S 空間（液體室） Si ' S 2空間 50 319958212 212A full rotation piece (the third spring pushing means, the flow path bending part variable means) the spring pushing means, the flow path variable means) 214 tension spring (the 216th flow path body 220 small sphere 224 piston body (shaking member) 226 guiding groove 230 piston receiving portion (liquid chamber 234 curved concave portion 238 splicing piece 242 piston (piston member) 254 connecting portion 312 shaking body 218 circulation path 222 large sphere 225 inner casing 228 curved surface 236 embedded recess 240 embedded protrusion 246 Tab 310 accommodating portion (liquid chamber 315, 335 shaft hole 49 319958 200905102 320 guide groove 321 valve (occlusion member) 324 accommodating recess 326 valve portion 328 flow path (decompression flow path) 330 guide plate 332, 334 through hole 336 Thickened portion 338 Gear member 340 Gear (rotating member) 342 Sealing portion 344, 350 0-ring mounting groove 348 Guide post (guide projection) 354 Large gear 356 Cover 358 Positioning projection 362 Opening 354 Abut Rib S space (liquid chamber) Si ' S 2 space 50 319958

Claims (1)

200905102 圍 十、申請專利範 一種阻尼器，係具備有： 外殼； ’並填充有黏性 流 複數個液體室，設置於前述外殼内 心旋轉體，以可旋轉之方式收容於前述外殼内，並承 文來^前述液體室的黏性流體的阻力；以及 ^机通路徑可變手段，當前述旋轉體的旋轉速度達預 定^以上時，將前述液體室彼此間形成為非連通狀離: :::::::::度未達預定值時，將前述液體室彼 2·如申=專利範圍第1項之阻尼器，其中， 前述旋轉體係具備有： 轉子傳達來自外部的旋轉力；以及 =，件，相對於前述轉子的軸芯偏心旋轉，且在 ，、处外叙之間構成前述液體室；而 前述流通路徑可變手段係構成為包含有： :-流，徑遮斷構件，當前述轉子 =值以上時，藉由在與該轉子之間產生 連通狀態；以及 將則边液體室彼此間形成為非 第一彈推手段，連結於前述第一流通路 件，並將該第一流通路栌 遮斷構 方向相反的方向彈推，：朝與前述轉子的旋轉 泮推，*轉子的旋轉速度未達預定值 319958 51 200905102 :’使第—流通路徑遮斷構件返回 間形成為連通狀態的位置。 ，别处液體室彼此 .如申明專利範圍第2項之阻尼器，A 係具有第—餘襬線齒形部，於前述外^的=偏心構件 與前述第—餘襬線齒形部鳴合的第；；= 周面形成有 藉由前述第一你# ^ i 罘一餘擺線齒形部，並 構成前述液體室形部與前述第二餘擺線齒形部 4.如申=專利範圍第i項之阻尼器，其令， 前述旋轉體係具備有： 〃 轉子，傳達來自外部的旋轉力； 移動構件，gp署奶^ + 殼之間構成前述液體室H的外側’並在與前述外 移動轉力變換成朝沿著前述 _ 得于的軸方向之方向移動，·而 ;述=:獲可變手段係包含下述構件而構成者： 預定值以上時，藉由旋轉速度達 ^ ^ ^ 、忒轉千間產生的剪力而旋轉， 、=y'(體至彼此間形成為非連通狀態；以及 件，並將节’連結至前述第二流通路徑遮斷構 通路徑遮斷構件朝與前逑轉子的旋轉 時，使Β_、ά 推*轉子的旋轉速度未達預定值 吏弟、•通路徑遮斷構件返回至將前述液體室彼此 間形成為連通狀態的位置。 .如申請專利範圍第4項之阻尼器，其中， 319958 52 200905102 且 則述移動構件係設置成從前述外殼的内壁 可於：以界定前述液體室之柱材之間上下移ς; 耵述凸輪手段係包含有下述構件而構成者··200905102 围十, application for a patent damper is provided with: a casing; 'filled with a viscous flow of a plurality of liquid chambers, disposed in the inner casing of the outer casing, rotatably received in the outer casing, and The resistance of the viscous fluid of the liquid chamber; and the variable path of the machine passage, when the rotation speed of the rotating body reaches a predetermined value or more, the liquid chambers are formed into a non-connected state: :: When the ::::::: degree is not up to the predetermined value, the damper of the liquid chamber of the first aspect of the invention, wherein the rotating system is provided with: the rotor transmits a rotational force from the outside; The member is eccentrically rotated with respect to the axis of the rotor, and the liquid chamber is formed between the outer and outer portions; and the flow path variable means is configured to include: a flow, a diameter interrupting member, When the rotor value is equal to or greater than a value, a communication state is generated between the rotor and the rotor; and the liquid chambers are formed as non-first spring pushing means to be coupled to the first flow passage member, and The first flow passage is urged in a direction opposite to the direction of the blocking mechanism, and is pushed toward the rotation of the rotor. The rotation speed of the rotor is less than a predetermined value. 319958 51 200905102: 'The first flow path is interrupted. A position that is formed in a connected state. Other than the liquid chambers of each other. For example, the damper of the second paragraph of the patent scope, the A system has a first trochoidal tooth-shaped portion, and the outer eccentric member and the first trochoidal tooth portion are combined. The front surface is formed by the first first #^ i 罘 余 摆 齿 齿 , , , , , 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体 液体The damper of the item i, wherein the rotating system is provided with: a rotor that transmits a rotational force from the outside; and a moving member that is configured to form an outer side of the liquid chamber H between the shells and the outer portion The moving rotational force is changed to move in the direction along the axial direction from which the above-mentioned _ is obtained, and the variable means includes the following members: when the predetermined value or more is reached, the rotational speed is up to ^^ ^, rotating the shear force generated by thousands of turns, , = y ' (the body is formed into a non-connected state with each other; and the piece, and joining the section to the aforementioned second flow path intercepting the path through the blocking member When the rotation of the rotor is turned toward the front and the front, the rotation speed of the rotor is pushed by Β_, ά If the predetermined value is not reached, the passage path member is returned to a position where the liquid chambers are formed in communication with each other. The damper of claim 4, wherein 319958 52 200905102 and the moving member The inner wall of the outer casing is configured to move up and down between the columns defining the liquid chamber; the cam mechanism includes the following components: 波狀的凸輪溝，形成於前述轉子的外周面 轉子的軸方向具有波峰和波谷；以及 溝嵌Γ突起’設置於前述移動構件，用以與前述凸輪 ’請專利範圍第4項或第5項之阻尼器，其中 私動構件係以彼此錯開相位來則述 突起嵌合於前述凸輪溝。#動之方式，使别述嵌合 如申請專利範圍第i項之阻尼器，其中， 前述旋轉體係具備有： 轉子，傳達來自外部的旋轉力； '搖動構件，在中心軸傾斜 丁 的軸芯偏連& ㉟下相對於前述轉子 以及 連'、、°且精由該轉子的旋轉而搖動； 之間=二置於前述搖動構件，並在與前述外殼 〜间構成刖述液體室，日茲 1 ^ 回移動；且 1且错由則述搖動構件的搖動而來 别述流通路徑可變丰 第三流通特遮斷4#^^述構件而構成者： 預定值《上時，轉子的旋轉速度達 轉’::r/手， 矛一坪推手段，連社‘ ' °至刚返苐三流通路徑遮斷構 319958 53 200905102 件，並將該第三流通路徑遮斷構件义 方向相反的方向彈推，當轉絲刚子的旋轉 眭，蚀筮-* s * 得子的旋轉速度未達預定值 時使第二〜通路徑遮斷構件返回 值 間形成為連通狀態的位置。 、n a體室彼此 δ. 一種阻尼器，係具備有·· 外殼； 複數個液體室，設置於箭 流體； 置^边外殼内’且填充有黏性 收容達來自外料旋轉力，独可旋轉之方式 的阻力； 又來自則述液體室的黏性流體 旋轉構件，具有與前述 轉子的旋轉力； 轉子㈣的軸芯，且傳達該 置；V引大起’设置成從前述旋轉構件的軸芯錯開位 引溝搖與前述導引突起嵌合之直線狀的導 減芦、:、引穴起的移動而在前述液體室内搖動； 於搖動通路徑’沿著前述搖動體的移動方向而設置 體室妒成A?㈣_體£於⑽，將A致經分隔的液 體至形成為連通狀態；以及 速度設置於前述搖動體’當前述轉子的旋轉 阻力時，藉由前述黏性流體所造成的黏性 夕動，以閉塞前述減壓流通路徑。 9 ·如申請專利誌 # 項之阻尼器，其中，前述搖動體係 319958 54 200905102 以彼此錯開相位來移動之方式，使前述導引突起嵌合至 前述導引溝。 55 319958a corrugated cam groove having a peak and a trough in an axial direction of the rotor of the outer peripheral surface of the rotor; and a groove-embedded protrusion 'provided to the moving member for use with the aforementioned cam's patent range 4 or 5 The damper in which the telekinetic members are in a phase shifted from each other, and the projections are fitted to the cam grooves. The method of moving, such as the damper of claim i, wherein the rotating system is provided with: a rotor that transmits a rotational force from the outside; a rocking member that is tilted at a central axis The partial connection & 35 is oscillated with respect to the aforementioned rotor and the connection of ', °, and fine by the rotation of the rotor; between = two is placed on the rocking member, and a liquid chamber is formed between the outer casing and the outer casing 1 1 back movement; and 1 and wrong by the shaking of the shaking member, the flow path variable flow third flow special occlusion 4 # ^ ^ description of the components: the predetermined value "on the rotor The rotation speed is up to '::r/hand, spear-push push means, Lianshe' '° to just return to the third circulation path to block the structure 319958 53 200905102 pieces, and the third flow path blocking member is in the opposite direction The direction of the rotation is ,, and when the rotation speed of the fused 筮-* s * is less than the predetermined value, the second return path is interrupted to a position where the return value is formed in a connected state. , na body chambers δ. A damper with a · · shell; a plurality of liquid chambers, set in the arrow fluid; placed inside the shell 'and filled with viscous accommodation up to the external material rotation force, can be rotated The resistance of the mode; the viscous fluid rotating member from the liquid chamber, having the rotational force with the rotor; the axis of the rotor (four), and conveying the position; the V-increase is set to be from the axis of the rotating member The core misalignment groove is formed by a linear guide roller that is fitted into the guide protrusion, and the movement of the hole is moved in the liquid chamber; the rocking path is set along the moving direction of the rocker The body chamber is entangled into A? (4) _ body (10), the A-separated liquid is brought into a connected state; and the speed is set in the aforementioned oscillating body' when the rotational resistance of the rotor is caused by the viscous fluid The viscous eclipse is used to occlude the aforementioned decompression flow path. 9. The damper of the patent application, wherein the oscillating system 319958 54 200905102 is configured to be engaged with the guiding groove by moving in a phase shifted from each other. 55 319958
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EP2484932B1 (en) * 2009-09-30 2018-02-14 Sugatsune Kogyo CO., LTD. Rotary damper
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