201221394 六、發明說明： 【發明所屬之技術領域】 本發明·於-種U由使桿自料體前進祕煞車力輸 出之煞車缸裝置、及具備該煞車缸裝置之碟片煞車裝置。 【先前技術】 • %前’作為具備煞車料置之鐵路車輛用之碟片 煞車裝 置’已知有專利文獻1所揭示者。專利文獻！所揭示之碟片 煞車裝置係構成為藉由氣壓使桿自煞車紅裝置之缸本體前 進而將煞車力輸出。又，於此碟片煞車裝置中，使以可相對 於車輛沿車軸方向進行相對移位之方式所安裝之卡甜本體 之-對煞車槓桿，其-端側分別連結於煞車缸裝置中之桿 側、及構成缸本叙Κ祕構件側。然後，藉祕煞車缸震 置以上述方式運作’而驅動—對煞車槓桿。而且，此碟片煞 車裝置係構成為藉由設置於以上述方式驅動之一對煞車損 桿之另一端側之阻尼器（dam㈣來失住車軸側之碟片而產 、 生煞車力。 ‘ &，作為絲料置’已知有專利讀2所揭示者。專利 文獻2 _示之料缸裝㈣、於料推㈣設£之桿上固 接有活塞。而且，該煞車缸裝置構成為藉由對缸本體内之屬 力室供給壓縮空氣而對活塞施力，使活塞及捍前進。再者， 藉由使桿前進，而自設置為可與桿—起移動之煞車輪出部輸 出煞車力。 100138610 3 201221394 [先前技術文獻] [專利文獻] 專利文獻1 :日本專利特開昭61-175330號公報 專利文獻2 :曰本專利特開2007-131203號公報 【發明内容】 (發明所欲解決之問題） 於專利文獻1所揭示之碟片煞車裝置中，為了產生所需之 煞車力，而設定煞車槓桿之長度。然而，於需要較大煞車力 之情形時’則存錢車槓桿之長度變長而導致卡鉗本體變 大，使碟片煞車裝置之整體大型化之問題。 另一方面，於專利文獻2所揭示之煞車缸裝置中，為了獲 得所需大小之輸出之煞車力，而決定缸本體之直經。如此， ，進行藉由調本體直徑之設定，而產生所需煞車力之設 疋方式。然而’於需要較大煞車力之情形時’則存在紅本體 之直徑變大而導致煞車缸裝置之整體大型化之問題。又，若 煞車缸裝置大型化’則亦會產生導致碟片煞車裝置之 之問顳。 本七月有ϋ於上述實際情況，其目的在於提供—種可一 置之大里化’—面使自與桿—祕動之煞車輸出部 ⑥^煞車力增加的小型之煞車㈣置。又，本發明之目 在於提供一種具備該教車 (解決問題之手段） 之碟片煞車裝置。 100138610 4 201221394 用以達成上述目的之第1發明之煞車缸裝置，其特徵在於 具備：缸本體’其㈣形成中空；桿，其係配置於上述缸本 體之内側’且設置為於沿缸軸方向之直線方向且自上述缸本 體前進之前進方向、與朝向其相反方向後退之後退方向上移 動自如=施力彈菁，其可朝上述後退方向對上述桿施力； 致動…、係配置在相對於上述桿在上述邱方向上重叠之 =，且為進行旋轉動作之旋轉型或進行擺動動作之擺動型 叙m + ^上述致動器進行旋轉動作或擺動 力韓換絲/致動㈣產生之旋轉方向或擺動方向之驅動 轉、為，、上迷桿之移動方向平行之直線方向之驅動力，同 =抗上述桿施力彈簧之作用力，使上述桿沿上述前進方向 ΙΓ車自上述致動11之驅動力增強並仙於上述桿； 輸出部，其係設置為可與上述桿__動，且可藉由 上述杯朝上述前進方向移動而輸出煞車力。 :據本發明’桿係構成為沿缸轴方向之直 且’咖缝—二= =向上與桿重疊。因此’可使致動器 ==向及軸向有效率地縮小。而 ==間之效率化所確保之區域配置增力機構，該 牦力機構係將來自致動器之旋轉方 轉換為直線方向而增強並作用於桿上。' L之驅動力 動力所作狀桿—起移動之煞車輪出部輸出煞車力。如 100138610 201221394 此’可藉由致動器及桿之配置 之大型化而貫現小型化，同拍 ’己置空間之效率化抑制煞車缸裝置 同時可藉由增力機構增加煞鱼^201221394 VI. Description of the Invention: The present invention relates to a brake cylinder device for outputting a lever from a material body and a brake force, and a disk brake device including the brake cylinder device. [Prior Art] • % front is known as a disc brake device for a railway vehicle having a brake material. Patent literature! The disclosed disc brake device is configured to output the braking force by the air pressure to the front of the cylinder body of the vehicle red device. Further, in the disc brake device, the pair of brake levers of the card body which are mounted so as to be relatively displaceable with respect to the vehicle in the axle direction are connected to the rods of the brake cylinder device The side, and the side of the component that constitutes the cylinder. Then, by the secret cylinder, the vibration is operated in the above manner and driven to the brake lever. Further, the disc brake device is configured to generate and generate a braking force by damper (dam (4) provided on the other end side of one of the opposite ends of the vehicle damage lever. As a wire material, it is known as the one disclosed in Patent Reading 2. Patent Document 2 _ shows the cylinder (4), and the piston is fixed on the rod of the material push (4). Moreover, the brake cylinder device is configured as The piston is biased by supplying compressed air to the force chamber in the cylinder body to advance the piston and the crucible. Further, by advancing the rod, the wheel output is set to be movable with the rod. [Technical Document] [Patent Document 1] Japanese Patent Laid-Open Publication No. SHO-61-175330 (Patent Document No. JP-A-2007-131203) [Problem to be Solved] In the disc brake device disclosed in Patent Document 1, the length of the brake lever is set in order to generate the required braking force. However, when a large braking force is required, the saving truck lever is used. The length becomes longer and leads The caliper body becomes large, and the overall size of the disc brake device is increased. On the other hand, in the stern cylinder device disclosed in Patent Document 2, the cylinder body is determined in order to obtain the output of the required size. In this way, by setting the diameter of the body, the setting method of the required braking force is generated. However, when the situation requires a large braking force, the diameter of the red body becomes large, resulting in a brake cylinder. The problem of the overall size of the device. Moreover, if the size of the vehicle is large, it will also cause problems in the disc brake device. This July is contrary to the above actual situation, the purpose is to provide a kind of The large-scale "---------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------------- 100 610 装置 100 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 138 The inner side of the body is disposed in a linear direction along the cylinder axis direction and advances from the cylinder body forward direction, and moves backwards and backwards in a direction opposite to the direction of the cylinder body, and is movable toward the backward direction. The lever is biased; the actuator is disposed in a rotation type that is superimposed on the rod in the chien direction, and is a rotation type that performs a rotation operation or a swing type that performs a swing motion. Action or swing force Han wire change / actuation (4) The drive direction of the rotation direction or the swing direction generated, the driving force of the linear direction in which the moving direction of the upper lever is parallel, the same as the force of the above-mentioned rod biasing spring a driving force for lifting the rod from the actuating force 11 in the forward direction and enhancing the driving force; and the output portion is arranged to be movable with the rod and can be moved toward the forward direction by the cup Move and output the braking force. According to the present invention, the rod system is configured to be straight along the cylinder axis direction, and the coffee seam is overlapped with the rod. Therefore, the actuator == can be efficiently reduced in the axial direction and in the axial direction. The region-enhanced mechanism is ensured by the efficiency of the ==, which is a mechanism that converts the rotation from the actuator into a linear direction and acts on the rod. 'L's driving force Power rods - the movement of the wheel out of the wheel output 煞 car power. For example, 100138610 201221394 can be miniaturized by the enlargement of the arrangement of actuators and rods, and the efficiency of the same space can be reduced to suppress the cylinder device. At the same time, the squid can be increased by the force increasing mechanism ^
加的小型之煞車知裝置。 曰 再者，雖然並非為公知之煞車虹裝置，但可構成如下之煞 車缸裝置，其設置有：線型而非旋轉型或擺動型之致動器: 及增力機構，其係於將來自線型之致動器之直線方向之驅動 力轉換為旋轉方向而增強後，使直線方向之驅動力作用於椁 上。此煞車缸裝置之情形與本發明之煞車缸裝置相比，將導 致增力機構複雜化，且導致零件個數增加。因此，根據本發 明，與設置有線型之致動器、及於將此致動器之直線方向之 驅動力轉換為旋轉方向而增強後使直線方向之驅動力作用 於桿之增力機構的煞車缸褒置相比，亦可藉由零件個數削減 而實現輕量化及小型化。 第2發明之煞車缸裝置係如第i發明之煞車缸裝置，其 中，上述增力機構具有：旋轉凸輪，其連結於將上述致動芎 之旋轉方向或擺動方向之驅動力以旋轉力進行輸出之輸出 軸’同時具有配置成沿著以上述桿之軸中心為中心之圓周方 向延伸之第1凸輪面，且與上述輸出轴一起旋轉；平移凸於 (translation cam)，其與上述桿連結，同時具有配置成沿著 以上述桿之軸中心為中心之圓周方向延伸之第2凸輪面， 100138610 6 201221394 且抵抗上述桿施力彈簧之作用力，使上述桿朝向上述前進 方向沿直線方向移動；及滾動凸輪，其配置於上述第1凸 輪面與上述第2凸輪面之間，並可相對於該第1凸輪面及 該第2凸輪面進行滾動；且，上述第1凸輪面及上述第2 凸輪面中之至少任一者係以相對於上述桿之軸向傾斜之方 式設置。 根據本發明，於增力機構中，在相互對向之第1凸輪面與 第2凸輪面之間配置滾動凸輪，且第1凸輪面及第2凸輪面 之至少任一凸輪面以與桿之軸向傾斜之方式設置。因此，可 利用簡單之結構實現使桿伴隨致動器之輸出轴之旋轉並經 由滾動凸輪之滾動而朝前進方向移動之構成。然後，關於致 動器之驅動力，可於旋轉凸輪與平移凸輪之間有效率地由旋 轉方向轉換為前進方向。而且，可藉由設定缸本體之徑向（或 桿之徑向）之致動器、第1凸輪面、第2凸輪面及滚動凸輪 之配置，而容易地調整增力之比率。 第3發明之煞車缸裝置係如第2發明之煞車缸裝置，其 中，上述第1凸輪面及上述第2凸輪面之兩者均以相對於上 述桿之軸向傾斜之方式設置，上述滾動凸輪係設置為旋轉自 如地被支撐之複數個滾子凸輪，上述滾子凸輪之側面係設置 為以構成圓錐曲面之一部分之方式沿圓周方向延伸，同時相 對於上述第1凸輪面及上述第2凸輪面進行滾動之滾動面。 根據本發明，第1凸輪面及第2凸輪面之雙方係傾斜於桿 100138610 7 201221394 之軸向而設置’且於其等之間配置有作為具有構成圓錐曲面 之-部分之滚動面之滾子凸輪的滾動凸輪。因此，與設 動凸輪作為球狀之球面凸輪之情形相比，可降低作用於^ 個滾動凸輪之接觸面壓。而且，關於使桿伴隨旋轉凸輪之 轉並經由滾動凸輪朝前進方向移動時之前進衝程(：進二 離）’於以#"之㈣凸輪之旋轉量達成較大之前進衝程之 清开/時右使用球面凸輪作為滾動凸輪則需要大直徑之球面 凸輪，但右為滾子凸輪，則不需大型化，而可將傾斜於桿之 車向之第&輪面及第2凸輪面之傾斜之斜率^定為更陡山肖 之斜率。因此，可— 有效率地抑制煞車缸裝置之大型化， 一面任意且容易地確保前進衝程。 第4 ^明之煞車缸骏置係如第3發明之煞車缸裝置，1 中’於上述旋轉凸輅只L ^ 八上述平移凸輪之至少任一者之外周部 刀，δ又置有導引上述 根據本發明，可利用；《滚動方向之導引壁。 之 外周部分設置導引辟疋轉凸輪及平移凸輪之至少任—者 方向。而且，由㈣簡單構成，而導引滾子凸輪之滾動 於旋轉自如地切、:導弓丨壁導引滚子凸輪之滾動，因此對 此，可實現裝置之牙::子凸輪之結構體亦可簡化其構成。藉 ^ C ^ ng 步小型化及輕量化。 第5發明之煞車缸 穸f，苴 、罝係如第3發明或第4發明之煞車缸 霉’且上述停車煞車機構具有：停車煞 100138610 201221394 車用彈簧，其係於上述缸本體之内側沿著該紅本體之内周配 置；及停車絲歸塞，錢配置於上述缸本體之内側，區 隔解除停車絲用之煞車解除壓力室，啊㈣圓周方向勺 圍上述桿及上述平移凸輪之軸周圍之方式配置，且 匕 沿著與上述桿之移動方向平行之方向移動，藉由自 解除壓力室排出壓力流體而利用上述停車煞車 用力相對於上述缸本體朝上述前進耳之作 力機構之上述平移凸輪施力.且㈣動’㈣對上述增 辽卞移凸輪％力，且，上述增力機 保持器’魏轉自如地支撐上述滾子凸輪 有 晉，其朝向上述旋轉⑽對上述保持器施力。保持器施力彈 根據本發明，可於煞車缸裝置 車煞車機構係具備停車煞車料簧，其、產f車機構，該停 力；停車煞車用活塞，其藉由受停車=煞車之煞車 對桿施力;及解除停車煞車用之煞經由 然後’由於與桿之移動額平行地 力室。 以包圍桿及平移凸輪之軸關之 4煞車用活塞係 車煞車絲塞之配置空間效率化，^ ^此，亦可使停 煞車機構之配置”效率化並實縣向使停車 又’根據本發明，於增力機射，設置有㈣置之小型化。 持器施力之保持器施力彈簧。因此，即便於^轉凸輪對保 ==方向僅對平移凸輪施力之情形時運 -力_向旋轉凸輪側並經由保持器對滚 100138610 輪施力而 201221394 將該滾子凸輪保持於特定之位置 器施力彈菁之簡單構成，而於停車煞車機:::::::: 滾子凸輪之位置。 乍時亦保持 第6發明之煞車虹褒置係如第2發明至“ 蚊煞車μ置’其中，構成為㈣叙上述_器且— / 相體’其係固定於上壯本體，並且進行壓力流體之供^ 排出，上述輸出軸，其係旋轉自如地配置於上述箱體内；及 2片葉片’其等係自上述輸出軸朝向徑向之外侧延伸，同時 於上述相體内區隔複數個致動器壓力室。 根據本發明’由於致動器係具備固定於缸本體之箱體、於 箱體内旋轉之輸出轴、及自輸出軸延伸且區隔致㈣壓力室 之2片葉片所構成，因此，可緊凑地構成於缸軸方向與桿重 疊地配置之旋轉型之致動器。 第7發明之煞車缸裝置係如第6發明之煞車缸裝置，其 中，進一步具備裝備有該煞車缸裝置之車柄停車時所使用之 停車煞車機構，且上述停車煞車機構具有：停車煞車用彈 簧，其係於上述缸本體之内側沿著該缸本體之内周配置；及 停車煞車用活塞，其係配置於上述缸本體之内側，區隔解除 停車煞車用之煞車解除壓力室，同時以沿圓周方向包圍上述 桿及上述平移凸輪之轴周圍之方式配置，且設置為可沿著與 上述桿之移動方向平行之方向移動，藉由自上述煞車解除壓 力室排出壓力流體而利用上述停車煞車用彈簣之作用力相 100138610 10 201221394 對於上述缸本體朝上述前進方向移動… 之上述平移凸輪施力；且，ϊ對上述增力機構 煞車用活塞及上述彈簧、上述停車 疊地配置。 之軸向平行之方向重 根據本發明，與第 缸裝置帅亭車煞車機構，同時丄置问樣地，可於煞車 空間效率化而實現煞車㈣置之小型:=機構:配置 明，停車用煞車用之彈簧及活塞與致動器之葉發 軸向平行之方向重疊地配置。因此 ^車^干之 凸輪之增力機構之配置有旋轉凸輪及淚動 小。又，藉此，可利用與徑向有效率地縮 署“ 置之停車煞車機構之配 工s ’、’⑭地活用缸本體之#向㈣，可 :設”轉凸輪之直徑、滚動凸輪之數量及致動 ： 直徑與滾動凸輪之=。：’可以-面使旋轉凸輪之 輪之負m二 降健詩各滚動凸 輪之負載面充4確保前進方向之衝程之方歧 面之斜度，實現致動器之旋轉角度之最佳化。 輪 第8發明之煞車紅裳置係如第3發明或第4發明之煞車 裝置’其中’構成騎轉型之上述雜器具有顧，其 定於上述缸本體，並錢行壓力流體之供給及排出；上 出軸，其係旋轉自如地配置於上述箱體内；及2片，: 一 /1 ’ 其 100138610 11 201221394 等係自上述輸出_向徑向之外 内區隔複數個致動器壓力室；日中Π時於上述箱體 轉凸輪之一方設置有突起部，且於上述旋 :輪:另一_有可嵌入上述突起部」凹部，上= 力彈簧係經由上述平移凸輪及上 述杯施 出軸對上述旋轉凸輪施力，：衰動凸輪’朝向上述輸 施力。 肖此朝上述後退方向對上述桿 根據本發明，可緊凑地構成於虹轴方向與桿重叠地 ^轉型之致純。_，根據本翻，可藉㈣突起部^ 至凹部而容易地組I旋轉凸輪與設置有葉片之輸出轴，6 =:由利用桿施力彈簧之作用力對旋轉凸輪向輸出如 =咖輪與輸出輪緊固。因此，對於增力機構之旋· (、致動$之輸出轴，彻簡單之進行 容易地進行組裝。 u並且, 第&月之煞車缸裝置係如第8發明之煞車紅裝置，其 中進#具備裝備有該煞車缸袈置之車輛停車時所使用之 H’’、車機構’上述停車煞車機構具有停車煞相彈菁，其 述缸本體之内側沿著該缸本體之關配置；及停車煞 車用活塞纟係配置於上述缸本體之内侧，區隔解除停車煞 車用之煞車解除壓力室，同時以沿_方向包圍上述桿及上 述平移凸輪^轴周圍之方式配置，且設置為可沿著與上述桿 移動方向平仃之方向移動，藉由自上述煞車解除麗力室排 100138610 12 201221394 出麗力流體而利用上述停車煞車用彈簧之 述缸本體朝上述前進方a## +力相對於上 進方向移動，而僅對上述增力機 平移凸輪施力；且，上述增力機構進—步具有保持器= 轉自如地支撐上述滾子凸輪；及保胸施力二疋 述旋轉凸輪對上述保持器施力。 -朝向上 w赞明之煞車缸裝置同樣地 缸裝置中組裝停車煞車機構 、…、車 空:效率化，實現煞車缸裝置之小型置 I猎由利則痛力彈簧之仙力朝輪_ 力’而將旋轉凸輪與輸出軸緊固，㈣ 轉凸輪知 簧而朝向旋轉凸輪對保持器施力。3由保持11施力彈 構運作，並!赠it方向剌平移 卩便心車煞車機 除了桿施力彈簧更藉由如設置保之情科，亦可 成，而保持滾子凸輪之位置。、㈣力#簧之簡單之構 弟Π)發明之絲缸裝置係如第6 中’於上述輸出軸及上述2片 .、、、車缸裝置，其 連通孔係將由-方之上述葉片、°卩&置有連通孔’該 器壓力室與由另一方之上述葉片;高f則之上述致動 動器壓力室連通。 、品隔之尚壓側之上述致 第11發明之煞車缸裝置#士 中，於上述輪出軸及上述2:=發明之煞車-裝置，其 連通孔_一…述一：==: 100138610 201221394 器壓力室與由另一方之上述葉片所區隔之高壓側之上述致 動器壓力室連通。 根據此4發明，该煞車虹裴置係構成為經由設置於輸出軸 及葉片内部之連通孔，將一方之高壓侧之致動器壓力室與另 一方之高壓側之致動器壓力室連通。因此，可僅藉由對任一 方之高壓側之致動n壓力室供給壓力流體，而使雙方之高壓 側之致動器壓力室以相同之時序運作。而且，與將連通一方 及另-方之高壓側之致動器壓力室之連通孔設置於箱體之 情形相比’可使箱體之壁厚變薄。因此，可f現致動器之小 型化’藉此’可實現裝置之更小型化。 第12發明之煞車缸裝置係如第2發明至第4發明之任一 發明之煞車缸裝置，其中，上述增力機構進一步具有筒狀導 引構件’其係具有固定於上述缸本體且同時以沿著圓周方向 包圍上述桿之軸周圍之方式配置的筒狀部分，且設置有形成 為沿著與上述桿之軸向平行之方向延伸之槽或孔的導引 部；及輥體，其係相對於配置在上述筒狀導引構件内側之上 述平移凸輪旋轉自如地被支撐，且配置為可沿著上述導引部 進行滾動。 根據本發明，可藉由在固定於缸本體且包圍桿之軸周圍之 筒狀導引構件所設置作為槽或孔之導引部，同時於平移凸輪 方疋轉自如地設置如輥體之簡單結構，而容易地構築使年·移凸 輪停止旋轉之結構， 100138610 201221394 第13發明之煞車缸裝置係如第6發明之煞車㈣置，其 中，上述增力機構進一步具有筒狀導引構件，其係具有固^ 於上述缸本體且同時以沿著圓周方向包圍上述桿之轴周= 之方式配置的筒狀部分，且設置有形成為沿著與上述桿二輪 向平行之方向延伸之槽或孔的導引部；及輥體，其係相對於 配置在上述筒狀導引構件内側之上述平移凸輪旋轉自如地 被支撐，且配置為可沿著上述導引部進行滚動；且上述致動 器進-步具有2個區隔塊體’其等係固定於上述箱體之動 侧’並且在該箱體之圓周方向上分別配置於上述2片葉内 間；及銷構件，其係使兩端分別嵌人上述箱體與上述筒$ 引構件而加以固定；且於一方之上述區隔塊體與另一方之 述區隔塊體之間，藉由-方之上述葉片區隔高壓側之上^上 動器壓力室與低壓侧之上述致動器壓力 ’〔致 王々；力一方之上 區隔塊體與一方之上述區隔塊體之間，藉由另—方之上、^ 片區隔高壓側之上述致動器壓力室與低壓侧之上述致 壓力室’且於上述區隔塊體中後入有上述葉片所抵接之彈性 體，上述區隔塊體與上述彈性體係於由上述銷構件所貫通之 狀態下，固定於上述箱體及上述筒狀導引構件。 第14發明之煞車缸裝置係如第8發明之煞車虹裝置，其 中，上述增力機構進-步具有筒狀導引構件，其係具有固^ 於上述缸本體且同時以沿著圓周方向包圍上述桿^軸周2 之方式所配置的筒狀部分，且設置有形成為沿著與上述栌之 100138610 15 201221394 == 槽或孔的導w對 =上述筒狀導引構件内側之上述平 =支撐牛且配置為可沿著上述導引部進行滾動；且上述致 側，並且在該箱體之圓周方向上::係固定於上述箱體之内 端相^以紐與上述筒狀導 μ構件而加以固定；且，於— L _ 、 之·上述區隔塊體與另一方之 上述區隔塊體之間，藉由—方 致動器壓力室與健側之上述致動_高壓側之上述 述區隔塊體與—方之上述 以力至’於另—方之上 葉片區隔高壓側之上述致:::二間’藉由另-方之上述 0 找動—力室與低壓側之上述致動 2力至，且於上述區隔塊體中嵌人有上述 體與上述彈性體係於由上述銷構件所二 之“下’固疋於上述箱體及上述筒狀導引構件。 發明’與第u發明同樣地，可藉由設置筒狀導 弓構件之導引部及平移凸輪之輥體，而簡單之結構容易 地構築使平移凸輪停止旋轉之結構。而且，根據本發明，藉 由將兩端嵌人至筒狀導引構件與箱體之銷構件，而將與葉片 之間區隔南壓側及低壓側之致動器壓力室之區隔塊體與嵌 —至此區隔塊組且葉片所抵接之彈性體係於貫通狀態下進 疋口此於问狀導弓1構件與箱體之間，無需使用藉由 如螺检及螺帽之複數個構件來緊固之緊固機構，便可將區隔 100138610 16 201221394 由此，可實現零件個數之削減 而實現 塊體及彈性體固定 裝置之更輕量化。 第15發明之煞車缸裝置係如第7發明之煞車缸裝置，其 中’上述致動器進-步具有2個區隔塊體，該2個區隔塊體 係固定於上述箱體之内側，同時於該箱體之圓周方向上分別 ;上< 2片葉片之間’且於—方之上述區隔塊體與另-方之上述區隔塊體之間，藉由一方之上述葉片區隔高壓側之 上述致動益壓力室與低壓側之上述致動器壓力室，於另—方 之上述區隔塊體與—方之上述區隔塊體之間，藉由另一方之 上述f片區隔高壓侧之上述致動器壓力室與低壓側之上述 致動益壓力至，可對各低壓側之上述致動器壓力室供給及排 出外部之空氣之供排氣口，係連通於上述缸本體内配置有上 述停車煞車用彈簧之彈簧室。 *根據本發明，該煞車紅裝置係設置為藉由區隔塊體，在與 葉片之間區隔南壓側及低壓側之致動^壓力室，錢可對各 低麗侧之致動_力室供給及排出外部之空氣之供排氣 口 ’連通於配置有停車煞車用彈簧之彈簧室。目此，可利用 簡單之結構容易地構築藉由於缸本體中僅設置〗個使彈簧 至連通至外部之通氣口，而使各低歷側之致動器壓力室與外 部連通之構成。 又，作為其他觀點之發明，亦可構成具備上述任一煞車缸 裝置之碟月煞車裝置之發明。即，第16發明之碟片煞車裝 100138610 201221394 ㈣15 一任-發… 對於車輛沿車㈣虹]係裝備有該煞車&裝置且以可相 煞車缸U進It進移位之方式料；且藉由上述 片爽持車_之碟片而產生煞車力&卡鉗本體之—對煞車 根據本發明，可提 增加煞車力之小型如tr鳴置之大型化一面 (發明效果） 根據本發明，可提供一種能夠一面抑制裂 面增加自與桿-起㈣域車⑽料❹之匕 型之煞車缸裝置。又，可提供-種具備該煞車缸裝置::、 煞車裝Ϊ。 碼片 【實施方式】 以下’ -面參照圖式—面對用以實施本發明之形態進行說 明。再者’關於本發日狀煞車㈣置及具備顧車紅裝置之 碟片煞車裝置’係、以作為鐵路車輛用之情形為例進行說明。 又，圖式係以相當於設計圖之精度製作。 圖1係自車軸方向觀察本發明一實施形態之碟片煞車裝 置1之側視圖。又，圖2係自上方觀察圖1所示碟片煞車裝 置1之俯視圖。圖1及圖2所示碟片煞車裝置丨係構成為具 備：煞車虹裝置2 ;卡钳本體11，其係裝備有此煞車缸裝置 2，且以矸相對於車輛本體100沿車轴方向進行相對移位之 100138610 18 201221394 方式安裝 plate)(12、 (13 、 13) 〇 ，及作為阻尼器保持部之 12) ’其等係分別保持作為阻尼 一對背板（back 器之一對煞車片 對…、車片（13、13)係經由背板u而安裝於卡鉗本體U。 而H片煞車I置1係構成為藉由煞車缸裝置2之運作， 、對…、車片⑴、π)夾持與鐵路車輛之車輪(未圖示)之旋 轉連=也％轉之車軸側之碟片即圓板狀之煞車碟片1〇1而 …、車力再者，煞車碟片1〇1係形成為具有以與旋轉軸 正乂之方式所形成之雙面之制動面（l〇la、l〇la)的圓板狀。 而且’藉由煞車虹裝置2進行運作，使煞車片（13、13)以自 一…、車碟片101之旋轉軸方向大致平行之方向從兩側夾持 煞車碟片101之方式抵壓於制動面（101a、l〇la)。 卡钳本體Η係具備結合構件14與一對煞車槓桿（15、 15)。結合構件14係以可沿與車輛之前進方向平行之軸周圍 擺動之方式經由擺動銷14a而安裝於固定在車輛本體1〇〇 之底面之托架l〇〇a。而且，相對於此結合構件14大致對稱 地設置有可經由一對支點銷15a進行擺動的一對煞車槓桿 (15、15)。此支點銷15a係於自碟片煞車ι〇1之旋轉軸方向 觀察時，以沿相對於擺動銷14a之軸向垂直之方向延伸之方 式所設置。 一對煞車槓桿（15、15)係構成為於其一端侧經由缸支撐銷 Mb而安裝有煞車缸裝置2，且藉由此煞車缸裝置2驅動一 1〇〇138610 19 201221394 立而側而且，一對煞車槓桿（15、15)係在相對於安裝有煞車 缸裝置2之一端側介隔支點銷15a之另一端側，分別安裝有 保持煞車片13之1背板(12、12)。背板12躲由與支點 銷15a平仃地延伸之支撐銷]2a而擺動自如地安裝於煞車積 桿15。 於上述碟片煞車裂置i中，在一方之煞車横桿15安裝有 下Uk裝置2之致動器24之箱體32,而在另-方之煞 車核杯15 *裝有煞車輸出部21，且藉由煞車缸裝置2之運 作使煞車輸出部21相對於缸本體20進行前進之動作（自缸 本脰+冑開之動作）或後退之動作（向缸本體2G靠近之動 乍）藉^則吏對煞車槓桿(15、15)之缸支樓銷15bP付近 相互分離或接近之方式進行驅動。 =以上述方式進行驅動，故碟片煞車裝置丨係使一對煞 ^貝才干(15、15)以支關…為支轴進行動作，且以利用煞 料13失持煞車碟片而之方式進行動作。然後’此時， 槓桿(15、15)中’設置於一方之煞車槓桿15之 觸而之且、I片13就會先與煞車碟片101之制動面驗接 觸。而且，另一方之煞車積桿15係利用自接觸 之-方之煞車片13所受之反作用力將另—方制動面腕 抵壓至煞車碟片101之制動面1〇u。藉此，車片13 片（!3、13)央持煞車碟片1()1，而藉由於煞&〜對煞車 制動面（1GU、H)la)之間所產生之摩擦力 =、⑶與 車磲片101 100138610 20 201221394 之旋轉制動，而將設置為與煞車碟月101同軸之鐵路車輛之 車輪之旋轉制動。 接著，針對本發明一實施形態之煞車缸裝置2進行詳細說 明。圖3係煞車缸裝置2之立體圖，且係以切口剖面表示内 部結構之圖式。又，圖4及圖5係煞車缸裝置2之剖面圖。 於圖4及圖5中，圖示有包含煞車缸裝置2之中心軸線P(於 圖4及圖5中以一點鏈線P所表示之中心轴線），且位置不 同之剖面。再者，圖5係圖4中之A-A線箭線位置之剖面 圖，而針對下述致動器24係相對於其他部分，圖示以中心 轴線P為中心之圓周方向上之不同角度之剖面。又，圖3、 圖4及圖5所示之煞車缸裝置2雖然與圖1及圖2所示之煞 車缸裝置2以相同之方式構成，但變更外形之一部分而進行 圖示。 煞車缸裝置2係使其煞車運作方向之兩端部分別連結於 缸支撐銷15b。而且，如圖3至圖5所示，煞車缸裝置2係 具備缸本體20、煞車輸出部21、桿22、桿施力彈簀23、致 動器24、增力機構25、及停車煞車機構26等所構成。於此 等構成要素中，關於設置為結構構件之構件，例如係由鐵系 材料等金屬材料所形成。再者，於圖4及圖5中，針對桿 22係圖示其外形而非圖示其剖面。 圖3至圖5所示之缸本體20之構成係包含第1筒狀部20a 與第2筒狀部20b，且内部形成為中空。於缸本體20之内 100138610 21 201221394 側配置有桿22、桿施力彈簧23、增力機構 及停車煞車機構26等。第！筒狀部 主要部分、 均設為筒狀之構件，且於軸向(與中:二第2筒狀部2〇b 上以串聯結合。 u，線p平行之方向） 又，於第1筒狀部20a中設置有筒㈣分27 部分27b，其係形成為於此筒狀部分以 ⑽凸多大 P平行之方向）上之-端部朝向_突與中心轴線 延伸之凸緣狀。於凸緣狀部分咖之之_沿圓周方向 成有貫通孔，該貫通孔係於由桿22、連^央部分，形 28、及下述停車煞車機制之停車煞車用°活^52^螺桿轴 之狀態下配置。 土 58寺所貫通 第2筒狀部20b係於其轴向（與中心 _ 上之-端部，藉由螺栓29 —體地結合 、’仃之方向） 而且，第2筒狀部20b係於其軸向上之另H同狀部施。 述增力機構25之筒狀導引構件5〇 端卩結合於下 增力機構U之筒狀導引構件50、及下Z2筒狀部勘、 ,9 及下述致動器24之箱體 32,係藉由螺检3〇結合為-體。再者，致動器以之箱體 32係藉由紅切銷15b連結於—方之煞車槓桿15。 圖3至圖5所示之桿22係設置為配置於缸本體20内側之 筒狀之構件。而且，桿22係移動自如地設置於沿著紅轴方 向（與中心轴線P平行之方向）之直線方向且自缸本體20前 進之剛進方向與朝向其相反方向後退之後退方向上。再者， 100138610 22 201221394 如圖4及圖5所示，將上述前進方向稱為「前進方向XI」(於 圖中由箭頭XI所表示之方向），且將上述後退方向稱為「後 退方向X2」（於圖中由箭頭X2所表示之方向），進行以下說 明。 於桿22設置有於前進方向XI側，以局部地擴徑為凸緣 狀之方式所形成之階部22a。而且，於桿22之階部22a之 周圍之軸周圍，係以可自桿22之與軸向平行之方向之兩 側分別抵接於此階部22a之方式，配置有離合器單元31。 離合器單元31係固定於下述增力機構25之平移凸輪46。 而且，離合器單元31係於平移凸輪46沿前進方向朝向XI 移動時，自缸本體20側抵接於桿22之階部22a並朝前進 方向XI對桿22施力。另一方面，離合器單元31係於平 移凸輪46沿後退方向朝向X2移動時，自下述煞車輸出部 21側抵接於桿22之階部22a並朝後退方向X2對桿22施 力。 圖3至圖5所示之桿施力彈簧23係設置為配置於下述筒 狀導引構件50之内側且為平移凸輪46之周圍之螺旋狀之彈 簧，並以相對於筒狀導引構件50朝向後退方向X2對平移 凸輪46施力之方式設置。藉此，桿施力彈簧23係構成為可 經由平移凸輪46及離合器單元31朝後退方向XI對桿22 施力。再者，於本實施形態中，雖然例示將桿施力彈簧23 設置為2個螺旋彈簧(23、23)之形態，但亦可並非如此，亦 100138610 23 201221394 可設置為1個螺旋彈簧或3個以上之螺旋彈簧等。 圖3至圖5所示之煞車輸出部21係經由螺桿軸28而連結 於桿22，且設置為可與桿22 —起移動。藉此，煞車輸出部 21係設置為可朝自缸本體20前進之前進方向χι、與以接 近缸本體20之方式後退之後退方向Χ2移動，且構成為可 藉由使桿22朝前進方向X1移動而輸出煞車力。又，煞車 輸出部21係藉由缸支撐銷15b而連結於另一方之煞車槓桿 15 ° 再者，於桿22之内侧及外周設置有間隙調整機構，該間 隙調整機構係具備螺桿轴28、離合器單元31、及内置於桿 22之未圖不之彈簧構件等所構成。於因碟片料裝置1之 煞車片13之磨損等而導致在煞車解除狀態下至煞車動作位 置為止之間隙變大之情形時，可藉由此間隙調整機構，自動 地对上述間隙。再者’雖'然省略詳細結構之說明，但於此 間隙》周&機構中，係構成為於未產生因煞車片之磨損等 所導致之間隙之狀態下，相對於與桿22連結之螺桿轴28 之桿22之相對位置不會發生變化，若產生上述間隙，則於 進打煞車動作時’螺桿轴28將自桿Μ突出， 28對於桿22之相斟&罢立& 干釉 相對位置產生變化，而自動地調整此間隙。 圖6係圖4戶斥-妨* 1 '、 斤不煞車缸裝置2之B-B線箭線位置之剖面 圖^圖7係表示致動器24及增力機構25之分解立體圖。 致動24係構成為旋轉型之致動器，其配置在相對於桿u 100138610 24 201221394 在缸軸方向上重豐之位置’且藉由供給及排出作為壓力流體 之壓縮空氣而進行旋轉動作。而且，此致動器24係具備箱 體32輸出轴33、2片葉片（34、35)、2個區隔塊體(36、37)、 複數個彈性體38、及複數個鎖構件39等所構成。再者，圖 6係對於輸出轴33、2片葉片（34、35卜2個區隔塊體⑽、 37)及複數個銷構件39圖示其外形，而非圖示其剖面。 圖8係表示致動器24之一部分之立體圖。圖3至圖8所 示之柏體32係形成為具有底部並且底部之相反側開口之大 致圓筒狀之殼體，且經由下述增力機構25之筒狀導引構件 50而固定於缸本體20。而且，此箱體32係構成為經由貫通 形成於箱體32之壁部之供排氣口 32a，進行作為壓力流體 之壓縮空氣朝向内部之供給及朝向外部之排出。再者，供排 氣口 32a係連接於未圖示之壓縮空氣供排氣管，進一步藉由 切換閥（未圖示）切換連接路徑而連接於壓縮空氣供給源（未 圖示）及壓縮空氣排氣口（未圖示）β 圖9係表示輸出軸33及葉片（34、35)之立體圖。圖3至 圖7、圖9所示之輸出軸33係設置為圓筒狀之構件，且旋 轉自如地配置於箱體32内。此輸出軸33係設置為將致動器 24之旋轉方向之驅動力作為旋轉力輸出之構件。再者，於 箱體32之内側之底部之中央部分固定有設置為圓筒狀構件 之套筒40。而且，輸出軸33係相對於套筒4〇配置為同心 狀’並且以與桿22之軸中心一致之中心轴線ρ為中心旋轉 100138610 25 201221394 自如地配置。即，於將套筒40嵌入至輸出軸32之狀態下， 以使輸_32之内周相對於套筒40之外周滑動自如之方式 配置輸出軸33 °又’在輸出軸33之端部與箱體32之底部 之間。又置有相對於箱體32旋轉自如地支樓輸出軸33之軸 承41(參照圖4及圖5)。 圖3至圖7、圖9所示之葉片（34、35)係設置有2片，分 另J开y成為平板狀，且構成為自輸出軸％朝向徑向之外側延 伸’同時於箱體32内區隔下述複數個致動器壓力室（42a、 42b、43a、43b)。而且’ 2片葉片（34、35)係配置於輸出軸 33之圓周方向上錯開18〇度之位置，分別固定於輸出軸33。 又’葉片34係具備金屬製之2個矩形之板狀體(34a、 34b)、及被夾於該等板狀體(34a、34b)之間且與板狀體(34a、 34b)結合之樹脂製之矩形之密封構件34c所構成。密封構件 34c係構成為滑動自如地配置於箱體32之内壁，且以氣密 狀態區隔下述致動器壓力室（42a、42b)。同樣地’葉片35 係具備金屬製之2個矩形之板狀體(35a、35b)、及被夾於該 等板狀體(35a、35b)之間且與板狀體(35a、35b)結合之樹脂 製之矩形之密封構件35c所構成。密封構件35c係構成為滑 動自如地配置於箱體32之内壁，且以氣密狀態區隔下述致 動器壓力室（43a、43b)。 圖3至圖8所示之區隔塊體(36、37)係設置有2個’且固 定於箱體32之内側’同時於箱體32之圓周方向上分別配置 100138610 26 201221394 於2片葉片（34、35)之間。*且，各區隔塊體(36、3乃係密 接地配置於箱體32之内壁與輸出軸33之外周。 又，區隔塊體36係具備金屬製且形成為大致三角柱狀之 第1塊體36a及第2塊體36b、及被夾於第！塊體36a及第 2塊體36b之間且與第丨塊體36a及第2 _鳩結合之樹 脂製之矩形之密封構件36c所構成。密封構件3&係構成為 密接地配置於箱體32之内周及底面、輸出軸33之外周及增 力機構25之筒狀導引構件5〇之端面，且以氣密狀態區隔箱 體32内❶同樣地，區隔塊體37係具備金屬製且形成為大致 三角柱狀之第i塊體37a及第2塊體37b、及被夾於第^鬼 體37a及第2塊體37b之間且與第1塊體37a及第2塊體 37b結合之樹脂製之矩形之密封構件3乃所構成。密封構件 37C係構成為密接地配置於箱體32之内周及底面、輪出軸 33之外周及增力機構25之筒狀導引構件5〇之端面，且以 氣掛狀態區隔箱體32内。 又，如圖ό所示，於致動器24中，係於一方之區隔塊體 36 ^、另方之區隔塊體37之間，藉由一方之葉片34區ρ 有高壓側之致動器壓力室42a與低壓側之致動器壓力= 42b。由此，高壓側之致動器壓力室係由第）塊體％&、 葉片 相體32之内周及底面、輸出軸33之外周、芮狀 V引構件5〇之端面所區隔。低壓側之致動器壓力室々a係 由第2塊體37b、葉片34、箱體32之内周及底面、輪出軸 100138610 27 201221394 33之外周、筒狀導引構件50之端面所區隔。再者，壓縮空 氣之供排氣用之供排氣口 32a係以連通於高壓側之致動器 壓力室42a之方式設置。 而且，在另一方之區隔塊體37與一方之區隔塊體36之 間，藉由另一方之葉片35區隔有高壓側之致動器壓力室43a 與低壓側之致動器壓力室43b。由此，高壓側之致動器壓力 室43a係由第1塊體37a、葉片35、箱體32之内周及底面、 輸出轴33之外周、筒狀導引構件50之端面所區隔。低壓側 之致動器壓力室43b係由第2塊體36b、葉片35、箱體32 之内周及底面、輸出轴33之外周、筒狀導引構件50之端面 所區隔。再者，於圖6中，對於對箱體32内供給壓縮空氣 前之狀態之葉片（34、35)，以實線進行表示，對於對箱體32 内供給壓縮空氣後處於旋轉過程中之狀態之葉片（34、35)以 二點鏈線進行表示。 又，於致動器24中，如圖3至圖6、圖9所示，於輸出 軸33及2片葉片（34、35)之内部，設置有複數個連通孔44。 各連通孔44係設置為連通由一方之葉片34所區隔之高壓侧 之致動器壓力室42a與由另一方之葉片35所區隔之高壓侧 之致動器壓力室43a之孔。 於本實施形態中，連通孔44設置有2個，且形成為於輸 出軸33及2片葉片（34、35)之内部分別彎曲一次而延伸。 又，2個連通孔44係於缸轴方向上排列設置有2個，且形 100138610 28 201221394 成為沿著與中心軸線P垂直之面平行地延伸。再者，於圖4 及圖5中，以二點鏈線表示2個連通孔44於缸軸方向上之 位置。又，各連通孔44係形成為於在葉片34開口之開口 44a與致動器壓力室42a連通，且於在葉片35開口之開口 44b與致動器壓力室43a連通。藉此，將自供排氣口 32a供 給至箱體32内之壓縮空氣供給至致動器壓力室42a，並且 經由連通孔44亦供給至致動器壓力室43a。 圖6至圖8所示之彈性體38係設置有複數個，且分別設 置為塊狀之橡膠構件。而且，各彈性體38係構成藉由於嵌 入形成於區隔塊體（36、37)之矩形之孔，且以其端部自區隔 塊aa(36 37)犬出之狀態進行配置，而抵接於葉片（34、35) 之〇卩刀再者，肷入至第1塊體36a之彈性體38係以抵接 於葉片之板狀體34已之方式所配置，嵌入至第2塊體36b 之彈!·生體38係以抵接於葉片％之板狀體说之方式所配 置又甘八入至第1塊體37&之彈性體38係以抵接於葉片 34之板狀體35a之方式所配置，嵌入至第2塊體37b之彈 I·生體38係μ抵接於葉片35之板狀體她之方式所配置。 圖4、圖6至圖8所示之銷構件39係設置有複數個，且 圓柱狀延伸為較長之金屬製之構件。然後，各 狀導引構件之底部與筒 系於— ’區隔塊體(36、37)與彈性體 ” 牛39所貫通之狀態下定於箱體32及筒狀 100138610 29 201221394 導引構件50。即，第1塊體36a及嵌入該第1塊體36a之 彈性體38、第2塊體36b及嵌入該第2塊體36b之彈性體 38、第1塊體37a及嵌入該第1塊體37a之彈性體38、及 第2塊體37b及嵌入該第2塊體37b之彈性體38，係分別 由1個銷構件39所貫通。再者，於圖4中，係以二點鏈線 表示銷構件39於缸軸方向上之位置。 圖3至圖5、圖7所示之增力機構25係設置為如下機構： 若致動益24進行旋轉動作，就會將致動器24所產生之旋轉 方向之驅動力轉換為與桿22之移動方向平行之直線方向之 驅動力，並且抵抗桿施力彈簧23之作用力而使桿22朝前進 方向XI移動，使來自致動器24之驅動力增強並作用於桿 22°此增力機構25係具備旋轉凸輪45、平移凸輪46、滾動 凸輪47、保持器48、保持器施力彈簧49、筒狀導引構件50、 及輥體51等所構成。 圖係表示旋轉凸輪45之立體圖，且表示使致動器24 側之端部朝向下方之狀態之立體圖（圖10(a))、及使致動器 24側之端部朝向上方之狀態之立體圖（圖1〇(b))。圖3至圖 5、圖7、圖10所示之旋轉凸輪45係設置為環狀構件，且 設置為連結於致動器24之輸出軸33並與輸出軸33 —起旋 轉之構件。 旋轉凸輪45係於與致動器24側為相反側（即，前進方向 XI側）之端部，設置有複數個（於本實施形態中為6個）第1 100138610 30 201221394 凸輪面45a。而且，複數個第1凸輪面45a係配置成沿著以 桿22之軸中心（即，中心軸線p)為中心之圓周方向依序排 列，且以各第1凸輪面45a亦沿著以桿22之轴中心為中心 之圓周方向延伸之方式配置。又，各第1凸輪面45a係以相 對於桿22之軸向傾斜之方式所設置。 又’於旋轉凸輪45之致動器24側（即’後退方向X2側） 之端部設置有複數個（於本實施形態中為4個）凹部45b(參照 圖10)。複數個凹部45b係沿著圓周方向排列而配置。再者， 於輸出軸33之旋轉凸輪45側（即，前進方向χι側）之端部， 設置有複數個（於本實施形態中為4個）突起部33a，且此等 複數個突起部33a係沿著圓周方向排列而配置（參照圖9)。 而且，各突起部33&係對應於各凹部45b而設置，且各突起 部33a構成為嵌入至各凹部价中。於本 起部33a係形由& _ 入 成為以南度較低之四角柱狀突出部分， =:形成為矩形剖面之凹陷部分。再者，於煞車二 之狀態下，IT構成為，於突起部^嵌人至凹部伙 朝向輪46及滾_47 對桿22施力。 輪45施力’而藉此朝後退方向X2 平移凸輪 46之立體圖。圖 圖11所示之平梦M J至圖5、圖， 夕凸輪46係前進方向χι側形 筒狀部分卩M、a %成為小直輕 100138610 直“狀部52,且後退方向Χ2側係形成為 31 201221394 直徑之環狀部分即大直徑環狀部53。 一 在其前進方向XI側之端部之内側，固：:狀部52， 照圖4及圖5)。藉此，平移凸輪46經=二早元叫參 連結於桿22。 0态早兀31而 平移凸輪46之大直徑環狀部53传 诉配置成於與桿 向平行之方向上對向於旋轉凸輪45。而且 仟“之軸 53係於旋轉凸輪45側（即，後退方向大直徑環狀部 有複數個（於本實施形態中為6個）第2 — 卩，叹置 第2凸輪面53a係沿著以桿22夕^ ^輪面53&。複數個 為中心之圓周方向依序排列而配置，且 中心轴線P) 亦以沿著以對桿22之轴中心也+ 且各第2凸輪面53a 配置。又，各第2凸輪面53 圓周方向延伸方向所 叫糸以相對於 之方式所設置。 、杆22之軸向傾斜 又，於大直徑環狀部53 之如進方向γ 1 y , 抵接之方式配置有配置在小 —★ 則之端面，係以 之桿施力彈簧23。而且，萨由彳、^ 52之周圍之螺旋狀 器24之運作而朝前進方向幻灸大直傻每狀部53隨著致動 抵抗桿施力彈簧23之作H 士 平移凸輪46係構成為 叩用力而使;p π 起朝向前進方向沿著直線 干2與離合器單元31一 圖！2係表示滾動凸輪47及2器 圖5、圖7、圖12所示之沪動 < 立體圖。圖3至 實施形態中為ό個）滾子 係叹置為複數個(於本 __ 咖下，亦稱為「滚子凸輪47j)， 32 201221394 且旋轉自如地受保持器48所支撐。 再者，保持器48係設置為環狀之構件，且於其外周突出 地設置有朝向徑向之外側延伸之複數個（於本實施形態中為 6個）旋轉軸部48a。而且，各滾子凸輪47係旋轉自如地支 撐於該各旋轉軸部48a。又，於保持器48之内側，在與旋 轉凸輪45對向之端部側，設置有形成為朝向徑向内側突出 並且沿圓周方向延伸為凸緣狀之内側凸緣部48b。 複數個滾子凸輪47係在旋轉自如地保持於保持器48之狀 態下，配置於第1凸輪面45a及第2凸輪面53a之間。然後， 各滾子凸輪47係可滾動地配置於對向配置之各第1凸輪面 45a及各第2凸輪面53a。而且，各滚子凸輪47之側面係設 置為滾動面47a，該滾動面47a係以構成圓錐曲面一部分之 方式沿圓周方向（沿各滾子凸輪47之圓周方向）延伸，並且 相對於第1凸輪面45a及第2凸輪面53a進行滾動。 又，複數個滚子凸輪47係設置為位於沿著以桿22之軸中 心為中心之1個圓周上，且配置於保持器48之圓周方向上 均等角度之位置。再者，如圖5、圖10及圖11所示，於旋 轉凸輪45之外周部分，設置有導引滾子凸輪47之滾動方向 之導引壁45c，且亦於平移凸輪46之大直徑環狀部53之外 周部分，設置有導引滾子凸輪47之滾動方向之導引壁53b。 各導引壁45c係設置為於各第1凸輪面45a之徑向外側沿著 相對於各第1凸輪面45a正交之方向較小地突出之壁部，而 100138610 33 201221394 各導引壁53b係設置為 相對於各第2凸輪面仏正*凸輪面53a之徑向外側沿著 又’如圖4及圖5所示人之气向較小地突出之壁部。 直徑環狀部53之間， 保持器48與平移凸輪46之大 .„ ^ 有保持器施力彈蕃仙 力弹貫49係設置為配置於桿 I 49。保持器施 且，保持器施力彈簧49 。圍之螺旋狀之彈簧。而 塾圈之環構件54，而切於:方之端部經岭置為彈簧用 -側之端部’另一方；則之後退方向 方向XI側之端面而支撐於保持器此=8b之前進 菁的構成為朝向旋轉凸輪料保持心::持器施力彈 圖13係表示筒狀導引構件5Q之立體圖^ 7、圖13所示之筒狀導引構心係使前進方向χι圖貝1 為小直徑之筒狀部分即小—部分55，並使^成 X2側形成為大直徑之環狀部分即大直徑環狀部分 徑環狀部分56係與箱體32 _起藉由螺栓⑽而固定於 體2 0之第2筒狀部2 0 b。小直徑筒狀部分5 5係設置為以沿 圓周方向環繞桿22之軸之方式所配置之筒狀部分。又，二 小直徑筒狀部分55係設置有沿著與桿22之軸向平行之方向 延伸作為長孔狀之孔所形成的導引部55a。再者，導？丨部5化 係於本實施形態中設置有2個，且設置於小直徑筒狀部分 55之圓周方向上錯開180度之位置。 圖3、圖4、圖7、圖11所示之親體51係設置為圓筒狀 100138610 34 201221394 ^件，且旋轉自如地支樓於配置在筒狀導引構件50之小 直徑离狀部分55内側之平蔣Λ认 _Ί .. ^ 多凸輪46之大直徑環狀部53。 輥體51係設置有2個。而且， 5〇 ™ , 輥肢51係於筒狀導引構件 50之圓周方向上，對應於各 導引邛55a而配置，並且配置 各¥引部仏滾動。再者，以使各輥體51於i個部 =:導引部55a之壁面進行平滑滾動之方式，設定為 各導引杨之寬度尺寸略大於各輕㈣之外周之直徑尺 寸。又，如本實施形態於將導㈣55a形成為孔之情形時， 當將平移凸輪46之小直徑筒狀部52插人筒狀導㈣件5〇 之J直位筒狀部分55之内側後，可將各輕體Μ自筒狀導引 構件50之外側配置於各導引部％之内側而旋轉自如地安 裝於平移凸輪46。 再者，如圖5所示，於增力機構2 5中，將致動器2 4之自 配置有各葉片（34、35)之中央部分之位置至中心轴線P之距 離設定為大於自配置有複數個滾子凸輪47之位置至中心轴 線P之距離。藉此，構成為可增強致動器24所產生之驅動 力並自桿22輸出。 煞車缸裝置2係藉由經由供排氣口 32a對高壓側之致動器 壓力室(42a、43a)供給壓縮空氣而使葉片（34、35)及輸出軸 疋轉而且，輸出轴33之旋轉驅動力係藉由增力機構25 增強並傳遞至桿22，使桿22朝前進方向XI與螺桿軸28 -起前進’藉此’自煞車輸出部21輸出煞車力。而且，於 100138610 35 201221394 煞車缸裝置2中藉由利用致動器24之運作使增力機構 才干22專運作而產生煞車力之煞車機構係使用於鐵路車輛之 正常行駛時。 相對於上述内容，圖3至圖5所示之停車煞車機構％係 設置為裴備有煞車缸裝置2之鐵路車輛停車時所使用之煞 車機構。而且，停車煞車機構26係具備複數個停車煞車用 彈簧57、停車煞車用活塞58等所構成。 複數個（於本實施形態中為2個）停車煞車用彈簧係分 別设置為螺旋狀之彈簧。而且，各停車煞車用彈簧5 γ係配 置於虹本體20與筒狀導引構件50之間。即，各停車煞車用 彈簧57係於缸本體20之内側且沿著缸本體2〇之内周所配 置，並且於疴狀導引構件50之小直徑筒狀部分％之外側且 沿著小直徑筒狀部分55之外周所配置。又，各停車煞車用 彈ί 57係使一端侧之端部抵接於停車煞車用活塞％而被支 撐，並使另一端側之端部抵接於筒狀導引構件5〇之大直徑 環狀部分56之前進方向X〗侧之端面而被支撐。 再者，於筒狀導引構件5〇之大直徑環狀部分56，設置有 f為2個)供排氣口 59(參照圖*及圖 13) ’且各供排氣口 59係以連通於缸本體2㈣之配置有停 車煞車用彈簧57之彈簧室60之方式形成。又，各供排氣口 59係作為可對致動益24之各低㈣之致動器壓力室㈣、 43b)供給及排出外部空氣之貫通孔㈣置於脉導引構件 100138610 36 201221394 50。又，於與各通氣口 59對向之各第2塊體(36b、37b)， 在與各通氣口 59對向之位置上，分別凹陷地形成有作為用 以容許空氣通過通氣口 59之區域之通氣口對向區域 61(參 照圖6及圖8)。再者，於缸本體2〇之第2筒狀部2〇b，在 未圖示之位置上，設置有連通彈簧室60與外部之通氣口， 且此通氣口係設置為貫通形成於第2筒狀部勘之孔。 知車煞車用活塞58係配置於缸本體之内側，且設置為 氣密性地接於缸本體2Q之第丨筒狀部施之筒狀部分… 内周面並且可相對於筒狀部分27a沿轴向滑動。藉由利 用此停車煞車用活塞58與第丨筒狀部施所區隔之空間， :於缸本體20之_形成解除停車煞車狀煞車解除壓力 室62。又’對於煞車解除壓力室&，係構成為經由未圖示 之連通路徑，供給及排出作為壓力流體之壓縮空氣。 又’於停車煞車用活塞58,設置有圓盤狀部娜、筒狀突 ，部58b及平移凸輪連結部58c。圓餘部娜係設置為於 嵌入外周之密封構件上滑接於第i筒狀部施之筒狀部分 %之内周的圓盤狀之部分。而且，於圓盤狀部娜，在中 央部分形成有貫通孔’且自此貫通孔之邊緣部分朝向前進方 向X!側以圓筒狀突出之筒狀突起部58b係與圓盤狀部他 形成為-體。於此筒狀突起部58b之外周，滑接有叙入第i 筒狀部20a之凸緣狀部分27b内周之密封構件。 又，停車煞車用活塞58之圓盤狀部1及筒狀突起部哪 10〇13861〇 _ 201221394 係沿包圍平移凸輪46之周圍的筒狀導引構件5〇之小直徑筒 狀部分55之周圍所配置。藉此，停車煞車用活塞％係以沿 圓周方向包圍桿22及平移凸輪46之軸周圍之方式所配置， 且设置為可沿著與桿22之移動方向平行之直線方向移動。 平移凸輪連結部58c係於停車煞車用活塞％，作為與圓 盤狀部58a為相反側之部分而設置於筒狀突起部5奶，且構 成為具備自筒狀突起部58b之端部以凸緣狀形成於内側之 部分、t央形成有較大貫通孔之複數個圓盤狀之構件 、及配 置於其等内側之筒狀之構件。再者，複數_盤狀之構件係 藉由螺栓而緊固於筒狀突起部鄕内側之形成為凸緣狀之 部分。又，複數個圓盤狀之椹 為環狀之連結構件《而連结t與⑽之構件’係經由形成 合地設置於複數個in盤狀之構連、。構件63係可分別卡 又攝件之内周側與筒狀之構件 外周侧，且藉由連結構件63 +人 #牛 丄土 卡5於此等構件，使平移ώ鈐 連結部58c經由連結構件63 1地連#。 十移凸輪 再者，於平移凸輪連結部58e_^° 自前進方向XI側之端部之内侧向外側擴設置有 藉此，平移凸輪連結部58C内側之筒η之階梯狀之槽。 車煞車用活塞58朝向前進“ R狀構件係構成為僅於停 乃向XI移動拄 合於嵌入平移凸輪52之小直牺 f，於上述槽内卡 64。 Μ狀部52之外周而固定之環 由於如上述構成停車煞車 機構26 100138610 因此藉由對煞車解除 38 201221394 壓力室62供給壓㈣氣’抵抗停車煞車 力並沿後退方向X2對停車煞車用活塞5 > s 57之作用 產生停車煞車用彈簧57之停車煞車之/轭力，可維持不 除停車煞車之狀態）。另—方面，藉由7車力之狀態（已解 排出塵缩空氣，利用停車煞車用彈簧W、、、車解除壓力室62 車用活塞58相對於缸本體2〇朝前進方^作用力使停車煞 移凸輪連結部58c僅對增力機 向Xl移動，而由平 城楫25之平移Add a small car to know the device. Furthermore, although not known as the car-and-red device, it may constitute a following-cylinder device provided with a linear rather than a rotary or oscillating type actuator: and a force-increasing mechanism, which is to be from a line type After the driving force in the linear direction of the actuator is converted into the rotating direction and enhanced, the driving force in the linear direction acts on the crucible. In the case of the brake cylinder device, the force increase mechanism is complicated and the number of parts is increased as compared with the brake cylinder device of the present invention. Therefore, according to the present invention, the actuator of the wired type and the driving force for linearly driving the actuator are converted into the rotational direction, and the driving force of the linear direction is applied to the force-increasing mechanism of the lever. Compared with the device, it is also possible to reduce the weight and size of the parts by reducing the number of parts. According to a second aspect of the invention, in the cylinder device of the first aspect of the invention, the boosting mechanism includes: a rotating cam coupled to a driving force that rotates a driving direction of the actuating jaw or a swinging direction by a rotational force The output shaft 'have at the same time has a first cam surface that is arranged to extend in a circumferential direction centered on the axis center of the rod, and rotates together with the output shaft; a translation cam is coupled to the rod, At the same time, the second cam surface, 100138610 6 201221394, which is arranged to extend in the circumferential direction around the center of the axis of the rod, and which is resistant to the force of the rod biasing spring, moves the rod in a linear direction toward the forward direction; And a rolling cam disposed between the first cam surface and the second cam surface and capable of rolling with respect to the first cam surface and the second cam surface; and the first cam surface and the second surface At least one of the cam faces is disposed to be inclined with respect to the axial direction of the rod. According to the invention, in the boosting mechanism, the rolling cam is disposed between the first cam surface and the second cam surface facing each other, and at least one of the first cam surface and the second cam surface is aligned with the rod Set in the form of axial tilt. Therefore, the configuration in which the rod is accompanied by the rotation of the output shaft of the actuator and is moved in the forward direction by the rolling of the rolling cam can be realized with a simple structure. Then, regarding the driving force of the actuator, it is possible to efficiently switch from the rotating direction to the forward direction between the rotating cam and the translation cam. Further, the ratio of the boosting force can be easily adjusted by setting the arrangement of the radial direction (or the radial direction of the rod) of the cylinder body, the first cam surface, the second cam surface, and the rolling cam. According to a third aspect of the invention, in the cylinder device of the second aspect of the present invention, the first cam surface and the second cam surface are both disposed to be inclined with respect to an axial direction of the rod, and the rolling cam a plurality of roller cams rotatably supported, the side surfaces of the roller cams being arranged to extend in a circumferential direction so as to form one of the conical curved surfaces, and to be opposite to the first cam surface and the second cam The rolling surface of the surface is scrolled. According to the invention, both of the first cam surface and the second cam surface are disposed obliquely to the axial direction of the rod 100138610 7 201221394, and a rolling surface as a portion having a conical surface is disposed between the two. The rolling cam of the sub cam. Therefore, the contact surface pressure acting on the rolling cams can be reduced as compared with the case where the cam is provided as a spherical spherical cam. Moreover, regarding the rotation of the lever accompanying the rotation of the rotary cam and the movement of the rotary cam in the forward direction, the advance stroke (: two-pass) is achieved by the rotation of the (4) cam of the #" When the right side uses a spherical cam as the rolling cam, a large-diameter spherical cam is required, but the right side is a roller cam, so that it is not necessary to increase the size, and the steering wheel can be tilted to the first & tread and the second cam surface. The slope of the slope is determined to be the slope of the steeper mountain. Therefore, it is possible to efficiently and efficiently suppress the increase in the size of the brake cylinder device while ensuring the forward stroke arbitrarily and easily. In the fourth embodiment of the present invention, in the cylinder device of the third invention, in the above-mentioned rotary cam, only at least one of the above-mentioned translation cams is provided, and the δ is further guided by the above-mentioned rotary cam. According to the invention, it is possible to use; "the guiding wall of the rolling direction. The outer peripheral portion is provided with at least any direction of guiding the turning cam and the translation cam. Moreover, by (4) simple configuration, the rolling of the guide roller cam is freely rotatably cut: the guide bow wall guides the rolling of the roller cam, so that the structure of the device: the sub-cam structure can be realized It can also simplify its composition. By ^ C ^ ng step miniaturization and lightweight. According to a fifth aspect of the invention, the brake cylinder 穸f, 苴, 罝 is the third invention or the fourth invention, and the parking brake mechanism includes: a parking 煞100138610 201221394 vehicular spring, which is attached to the inner side of the cylinder body The inner circumference of the red body is disposed; and the parking wire is returned, the money is disposed on the inner side of the cylinder body, and the brake chamber is released by the brake for releasing the parking wire, and (4) the circumferential direction of the rod and the axis of the translation cam Arranging in a surrounding manner, and moving the crucible in a direction parallel to the moving direction of the rod, and using the above-described parking brake force to release the pressure fluid from the release pressure chamber with respect to the cylinder body toward the advancement ear Translating the cam to apply force. And (4) moving '(4) to the above-mentioned Zengjiao moving cam% force, and the above-mentioned booster holder 'superially supports the above-mentioned roller cam, which faces the above rotation (10) to the above retainer Force. According to the present invention, the brake mechanism of the brake cylinder device can be provided with a parking brake spring, which generates a vehicle mechanism, and the stop force; the piston for parking the brake is driven by the brake = brake The force is applied to the rod; and the brake is used to release the brakes and then the force chamber is paralleled by the movement of the rod. The space for the arrangement of the brakes for the 4" car pistons that surround the shaft and the translation cam is improved, and the configuration of the parking mechanism can be made "efficient" and the county can be parked and According to the invention, in the case of the force-increasing machine, the (4) is miniaturized. The retainer of the holder applies a force spring. Therefore, even if the cam cam is only biased to the translation cam in the direction of the == direction, The force _ is applied to the rotating cam side and the roller 100138610 is biased via the retainer, and the 201221394 holds the roller cam in a specific position to apply the force to the simple structure, and the parking brake machine:::::::: The position of the roller cam. The 褒 亦 亦 第 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如 如The main body is provided with a pressure fluid, and the output shaft is rotatably disposed in the casing; and the two blades are extended from the output shaft toward the radially outer side. The phase body is divided into a plurality of actuator pressure chambers. According to the present invention, since the actuator includes a casing fixed to the cylinder body, an output shaft that rotates in the casing, and two blades extending from the output shaft and partitioning the (four) pressure chamber, the actuator can be tightly closed. A rotary type actuator that is disposed to overlap the rod in the cylinder axis direction is formed. According to a seventh aspect of the present invention, in the vehicle-cylinder device of the sixth aspect of the present invention, the vehicle brake device of the sixth aspect of the present invention is further provided with a parking brake mechanism that is used when the handle of the brake cylinder device is parked, and the parking brake mechanism includes: a parking brake spring And disposed on the inner side of the cylinder body on the inner side of the cylinder body; and a parking brake piston disposed on the inner side of the cylinder body, and the vehicle is released from the parking brake to release the pressure chamber, and at the same time Arranging in a circumferential direction around the shaft of the rod and the translation cam, and being arranged to be movable in a direction parallel to a moving direction of the rod, and discharging the pressure fluid from the brake release chamber to utilize the parking brake The urging force phase of the magazine 100138610 10 201221394 is applied to the translation cam of the cylinder body moving in the forward direction of the cylinder; and ϊ is disposed on the brake mechanism of the booster mechanism, the spring, and the parking stack. According to the present invention, the direction of the axial parallel direction is different from that of the first cylinder device, and the vehicle is placed at the same time, and the space of the brake can be efficiently realized to realize the small size of the brake (4): = mechanism: configuration, parking The spring for the brake and the piston are arranged to overlap the direction in which the blades of the actuator are axially parallel. Therefore, the cam force-increasing mechanism of the cam is configured to have a rotating cam and a small tear. In addition, it is possible to effectively reduce the diameter of the rotating cam and the rolling cam by using the "direction s" of the parking brake mechanism and the "four" of the cylinder body. Number and actuation: diameter and rolling cam =. : 'Can be-faced to make the rotation of the wheel of the rotating cam. The load surface of each rolling cam is ensured to ensure the inclination of the square of the stroke in the forward direction, and the rotation angle of the actuator is optimized. . According to the eighth aspect of the present invention, in the brake device of the third aspect or the fourth aspect of the present invention, the above-mentioned miscellaneous device that constitutes a ride is provided in the cylinder body, and the supply and discharge of the pressure fluid are performed. The upper shaft is rotatably disposed in the casing; and two pieces are: one / 1 ', 100138610 11 201221394, etc., from the above output _ to the radially outer portion of the plurality of actuator pressures a protrusion is provided on one of the above-mentioned box cams in the middle of the day, and is in the above-mentioned rotation: another: a recess that can be embedded in the protrusion, and the upper = force spring is via the translation cam and the cup The application shaft applies a force to the rotating cam, and the decay cam is directed toward the above-described driving force. According to the present invention, the rod can be compactly formed in the direction in which the i-axis direction overlaps with the rod. _, according to the turn, the (four) protrusions ^ to the recesses can be easily grouped with the I rotating cam and the output shaft provided with the blade, 6 =: by the force of the lever biasing spring to the output of the rotating cam, such as = coffee wheel Fastened with the output wheel. Therefore, it is easy to assemble the output shaft of the booster mechanism (and the output shaft of the actuator). u and, the 'the month after the brake cylinder device is the vehicle red device of the eighth invention, among which #有有的'''''''''''''''''''''''''''''' The piston system for the parking brake is disposed inside the cylinder body, and is separated from the brake release brake chamber for parking the brake, and is disposed to surround the rod and the periphery of the translation cam shaft in the _ direction, and is arranged to be along Moving in the direction parallel to the movement direction of the rod, by releasing the Lili chamber from the brakes 100138610 12 201221394 from the brakes, the cylinder body of the parking brake is used to advance toward the forward side a## + force relative to Moving in the upward direction, and only applying force to the above-mentioned booster translation cam; and the above-mentioned boosting mechanism further has a retainer = freely supporting the roller cam; and a chest protection force Secondly, the rotating cam applies a force to the above-mentioned retainer. - The wheel cylinder is assembled in the same cylinder device as the upper w. The parking mechanism is assembled in the same cylinder device, ..., the vehicle is empty: the efficiency is realized, and the small-sized I-hunting of the brake cylinder device is realized. The force of the spring force is forced to the wheel _ force' and the rotating cam is fastened to the output shaft. (4) The cam is turned to the spring and the force is applied to the retainer by the rotating cam. 3 is operated by the holding 11 force, and it is given! Direction 剌 translation 卩 心 心 心 心 心 心 除了 除了 除了 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施 施The wire cylinder device is the same as the above-mentioned output shaft and the above two pieces of the above-mentioned output shaft, and the communication hole system is provided with the above-mentioned blades, the 卩& The actuator is connected to the pressure chamber of the other side of the blade; In the above-mentioned wheel-cylinder device of the eleventh invention, the above-mentioned wheel-out shaft and the above-mentioned 2:= invention brake-device, the communication hole_one...said one:==: 100138610 The 20122 1394 pressure chamber communicates with the above-described actuator pressure chamber on the high pressure side of the other of the blades. According to the fourth aspect of the invention, the braking device is configured to communicate one of the high pressure side actuator pressure chambers with the other high pressure side actuator pressure chamber via a communication hole provided in the output shaft and the vane. Therefore, the pressure chambers on the high pressure side of both sides can be operated at the same timing only by supplying the pressure fluid to the actuating n pressure chamber on either side of the high pressure side. Further, the thickness of the casing can be made thinner than in the case where the communication hole of the actuator pressure chamber on the high pressure side of the one side and the other side is provided in the casing. Therefore, the miniaturization of the actuator can be achieved by the miniaturization of the actuator. The brake cylinder device according to any one of the second to fourth aspects of the present invention, wherein the booster mechanism further includes a cylindrical guide member that is fixed to the cylinder body and simultaneously a cylindrical portion disposed around the shaft of the rod in a circumferential direction, and provided with a guide portion formed as a groove or a hole extending in a direction parallel to the axial direction of the rod; and a roller body, which is opposite to each other The translation cam disposed inside the cylindrical guiding member is rotatably supported, and is configured to be rollable along the guiding portion. According to the present invention, it is possible to provide a guide portion as a groove or a hole by a cylindrical guide member fixed around the shaft of the cylinder body and surrounding the rod, and at the same time, it is simple to set the roller body freely in the translational cam. According to a third aspect of the present invention, a brake cylinder device according to a thirteenth aspect of the present invention, wherein the booster mechanism further includes a cylindrical guide member, And a cylindrical portion disposed to surround the cylinder body while surrounding the shaft circumference of the rod in the circumferential direction, and provided with a groove or a hole formed to extend in a direction parallel to the two wheels a guiding portion; and a roller body rotatably supported relative to the translation cam disposed inside the cylindrical guiding member, and configured to be rollable along the guiding portion; and the actuator The step has two partition blocks 'these are fixed to the moving side of the box' and are disposed between the two leaves in the circumferential direction of the box; and the pin member, which is two end Separating the above-mentioned box body and the above-mentioned tube $ lead member respectively; and between the block body of one of the blocks and the block body of the other side, by the above-mentioned blade partitioning the high pressure side ^The above-mentioned actuator pressure of the upper pressure chamber and the low pressure side is [to Wang Yu; between the upper block of the force side and the block of the other side of the block, by the other side, the area Between the above-mentioned actuator pressure chamber on the high pressure side and the pressure generating chamber on the low pressure side, and in the block body, the elastic body abutted by the blade is inserted into the block body, and the block body and the elastic system are The pin member is fixed to the case and the cylindrical guide member in a state in which the pin member is penetrated. According to a thirteenth aspect of the present invention, in the brake device of the eighth aspect of the present invention, the booster mechanism further includes a cylindrical guiding member that is fixed to the cylinder body while being surrounded by a circumferential direction The cylindrical portion disposed in the manner of the shaft 2 of the shaft is provided with a guide w pair formed along the groove or hole of the above-mentioned 100100138610 15 201221394 == = the above-mentioned flat support of the inside of the cylindrical guide member The cow is configured to be rollable along the guiding portion; and the above-mentioned side, and in the circumferential direction of the box: is fixed to the inner end of the box and the cylindrical guiding member And being fixed; and, between - L _ , between the block body and the other block block of the other side, by the above-mentioned actuation of the actuator chamber and the healthy side - the high pressure side The above-mentioned partition block and the above-mentioned square force to the above-mentioned other side of the blade partition high-pressure side of the above::: two 'by the other side of the above 0 to find the force chamber and low pressure The above-mentioned actuation 2 force to the side, and the above-mentioned body is embedded in the above-mentioned compartment block and the above The system is fixed to the housing and the cylindrical guiding member by the lower side of the pin member. The invention is similar to the u-th invention, and the guiding portion of the cylindrical bow member can be provided. Translating the roller body of the cam, and the simple structure easily constructs a structure for stopping the translation cam. Further, according to the present invention, by embedding both ends to the cylindrical guiding member and the pin member of the case, The partition block between the blades on the south pressure side and the low pressure side of the actuator pressure chamber is embedded with the elastic system in which the blade abuts and is in contact with the blade in the through state. Between the member of the bow 1 and the case, it is possible to divide the number of parts by 100138610 16 201221394 without using a fastening mechanism fastened by a plurality of members such as a screw check and a nut. The smashing cylinder device according to the fifteenth aspect of the invention is the stern cylinder device according to the seventh aspect of the invention, wherein the actuator has two partition blocks, and the two The partition system is fixed to the inner side of the above casing, and at the same time Respectively, in the circumferential direction of the housing; the < between the two blades, and between the above-mentioned partition block and the other partition block, the above-mentioned blade is separated from the high pressure side by the above-mentioned blade to activate the pressure chamber and the low pressure The above-mentioned actuator pressure chamber on the side is between the above-mentioned partition block and the above-mentioned partition block of the other side, and the above-mentioned actuator pressure chamber of the high-pressure side is separated by the other f-piece The above-mentioned actuating pressure on the low pressure side is such that the supply and exhaust ports for supplying and discharging the outside air to the actuator pressure chambers on the low pressure side are connected to the spring in which the parking brake spring is disposed in the cylinder body room. * According to the present invention, the brake red device is arranged to actuate the low pressure side by dividing the block body between the blade and the south pressure side and the low pressure side of the actuating pressure chamber. The supply and exhaust port of the air supply and the external air is connected to the spring chamber in which the parking brake spring is disposed. For this reason, it is possible to easily construct a structure in which the actuator chambers of the respective low-altitude sides are communicated with the outside by means of a simple configuration in which only the vents that connect the springs to the outside are provided in the cylinder body. Further, as another aspect of the invention, the invention of the disc brake device including any of the above-described brake cylinder devices can be constructed. That is, the disc of the sixteenth invention is equipped with a vehicle 100138610 201221394 (four) 15 one-fabric... For the vehicle along the vehicle (four) Hong] is equipped with the brake & device and is capable of shifting into the cylinder with the cylinder U; According to the present invention, it is possible to increase the braking force of a small size such as a large-sized side of the horn (invention effect) according to the present invention. Provided is a crucible cylinder device capable of suppressing the increase of the crack surface from the rod-and-four (four) domain vehicle (10). In addition, it is possible to provide the same type of brake cylinder device::, brake mounting. [Embodiment] The following is a description of a mode for carrying out the invention. In addition, the case of the present invention is described as an example of a case where the present invention is used as a railway vehicle. Moreover, the drawings are produced with an accuracy equivalent to the design drawing. Fig. 1 is a side view of the disc brake device 1 according to an embodiment of the present invention as seen from the direction of the axle. Further, Fig. 2 is a plan view of the disc brake device 1 shown in Fig. 1 as viewed from above. The disc brake device shown in Fig. 1 and Fig. 2 is configured to include a brake device 2, a caliper body 11 equipped with the brake cylinder device 2, and relative to the vehicle body 100 in the direction of the axle. Shifting 100138610 18 201221394 way to install plate) (12, (13, 13) 〇, and as damper holding part 12) 'These are kept as a pair of damper back plates (one of the backs ..., the car piece (13, 13) is attached to the caliper body U via the back plate u. The H piece brake car I is set to be operated by the ram cylinder device 2, ..., the car piece (1), π) The rotation of the wheel (not shown) of the railway vehicle is clamped to the disc on the axle side of the railway vehicle, that is, the disc-shaped disc of the disc-shaped disc 1〇1, ..., the car force, the brake disc 1〇1 It is formed in a disk shape having a double-sided braking surface (10a, l〇la) formed in a manner orthogonal to the rotation axis. And by the operation of the brake device 2, the brake shoes (13, 13) are pressed against the brake disc 101 from both sides in a direction substantially parallel to the direction of the rotation axis of the disc 101. Brake surface (101a, l〇la). The caliper body is provided with a coupling member 14 and a pair of brake levers (15, 15). The coupling member 14 is attached to the bracket 10a fixed to the bottom surface of the vehicle body 1 via the swing pin 14a so as to be swingable around the axis parallel to the forward direction of the vehicle. Further, a pair of brake levers (15, 15) swingable via a pair of fulcrum pins 15a are provided substantially symmetrically with respect to the coupling member 14. The fulcrum pin 15a is provided to extend in a direction perpendicular to the axial direction of the swing pin 14a when viewed from the direction of the rotation axis of the disc brake ι. The pair of brake levers (15, 15) are configured such that the brake cylinder device 2 is attached to the one end side via the cylinder support pin Mb, and the brake cylinder device 2 is driven by the brake cylinder device 2 to the side. A pair of brake levers (15, 15) are attached to the other end side of the fulcrum pin 15a with respect to one end side of the brake cylinder device 2, and a back plate (12, 12) for holding the brake lining 13 is attached. The backing plate 12 is slidably attached to the brake rod 15 by a support pin 2a that extends flush with the fulcrum pin 15a. In the above-described disc brake disengagement i, the case 32 of the actuator 24 of the lower Uk device 2 is attached to one of the brake rails 15, and the brake output portion 21 is mounted on the other side of the brake cup 15*. And by the operation of the brake cylinder device 2, the brake output unit 21 is advanced relative to the cylinder body 20 (from the cylinder 脰 + 胄 action) or the backward movement (moving toward the cylinder body 2G) ^ Then, the cylinder support pin 15bP of the brake lever (15, 15) is driven close to or close to each other. = Driven in the above manner, the disc brake device is used to make a pair of cymbals (15, 15) act as a fulcrum, and the brake disc is lost by the use of the material 13 Take action. Then, at this time, the levers (15, 15) are disposed on one of the brake levers 15, and the I-piece 13 is first contacted with the brake surface of the brake disc 101. Further, the other side of the vehicle bar 15 is pressed against the braking surface 1〇u of the brake disc 101 by the reaction force received by the self-contacting square car 13 . Thereby, the 13 pieces of the car piece (!3, 13) hold the brake disc 1()1, and the frictional force generated between the brake pads (1GU, H) la by the 煞&~ (3) Rotating the brakes of the wheel of the railway vehicle that is set to be coaxial with the brake disc 101, with the rotary brake of the brake shoe 101 100138610 20 201221394. Next, a brake cylinder device 2 according to an embodiment of the present invention will be described in detail. Fig. 3 is a perspective view of the ram cylinder device 2, and shows a schematic view of the internal structure in a slit section. 4 and 5 are cross-sectional views of the brake cylinder device 2. 4 and 5, there is shown a section including the center axis P of the brake cylinder device 2 (the center axis indicated by the one-point chain line P in Figs. 4 and 5) and having different positions. 5 is a cross-sectional view of the position of the arrow line of the AA line in FIG. 4, and the actuator 24 described below is different from the other portions in the circumferential direction centered on the central axis P. section. Further, the brake cylinder device 2 shown in Figs. 3, 4, and 5 is configured in the same manner as the brake cylinder device 2 shown in Figs. 1 and 2, but is shown as a part of the outer shape. The brake cylinder device 2 is connected to the cylinder support pin 15b at both ends of the brake operation direction. Further, as shown in FIGS. 3 to 5, the brake cylinder device 2 includes a cylinder main body 20, a brake output portion 21, a lever 22, a lever biasing magazine 23, an actuator 24, a boosting mechanism 25, and a parking brake mechanism. 26 and so on. Among these constituent elements, the member provided as a structural member is formed, for example, of a metal material such as an iron-based material. Further, in Figs. 4 and 5, the outer shape of the rod 22 is shown instead of the cross section. The cylinder body 20 shown in FIGS. 3 to 5 includes the first tubular portion 20a and the second tubular portion 20b, and is internally hollow. Inside the cylinder body 20, a rod 22, a rod biasing spring 23, a boosting mechanism, a parking brake mechanism 26, and the like are disposed on the side of the 100138610 21 201221394. The first! The main portion of the tubular portion is a tubular member, and is axially coupled (in the middle: two second cylindrical portions 2〇b are connected in series. u, the line p is parallel). The tubular portion 20a is provided with a cylinder (four) portion 27 portion 27b formed in a flange shape in which the end portion of the cylindrical portion is oriented in a direction in which (10) the convex portion is parallel to the central axis. A through hole is formed in the circumferential direction of the flange-shaped portion, and the through hole is attached to the rod 22, the connecting portion, the shape 28, and the parking brake mechanism of the parking brake mechanism described below. Configured in the state of the axis. The second tubular portion 20b penetrated by the earth 58 temple is in the axial direction (the end portion with the center _, and is integrally joined by the bolt 29, and the direction of the 仃), and the second cylindrical portion 20b is attached to In the axial direction, another H is applied in the same shape. The cylindrical guiding member 5 of the boosting mechanism 25 is coupled to the cylindrical guiding member 50 of the lower boosting mechanism U, and the lower Z2 cylindrical portion, and the casing of the actuator 24 32, by the screw test 3 〇 combined into a body. Further, the actuator 32 is coupled to the brake lever 15 by the red cutting pin 15b. The rod 22 shown in Figs. 3 to 5 is provided as a cylindrical member disposed inside the cylinder body 20. Further, the rod 22 is movably disposed in a linear direction along the direction of the red axis (the direction parallel to the central axis P) and the forward direction from the cylinder body 20 advances in the reverse direction in the opposite direction. Further, as shown in FIGS. 4 and 5, the forward direction is referred to as "forward direction XI" (in the direction indicated by arrow XI in the drawing), and the backward direction is referred to as "reverse direction X2". (In the direction indicated by the arrow X2 in the figure), the following description will be made. The rod 22 is provided with a step portion 22a formed on the side in the advancing direction XI so as to be partially expanded in a flange shape. Further, a clutch unit 31 is disposed around the shaft around the step portion 22a of the rod 22 so as to be in contact with the step portion 22a from both sides of the rod 22 in the direction parallel to the axial direction. The clutch unit 31 is fixed to the translation cam 46 of the booster mechanism 25 described below. Further, when the translation cam 46 moves toward the XI in the forward direction, the clutch unit 31 abuts against the step portion 22a of the rod 22 from the cylinder body 20 side and urges the rod 22 in the forward direction XI. On the other hand, when the shift cam 46 moves toward the X2 in the backward direction, the clutch unit 31 abuts against the step portion 22a of the lever 22 from the side of the brake output portion 21 described later, and urges the lever 22 in the backward direction X2. The rod urging spring 23 shown in FIGS. 3 to 5 is provided as a spiral spring disposed inside the cylindrical guide member 50 and surrounding the translation cam 46, and is opposed to the cylindrical guide member. The 50 is set in such a manner as to bias the translation cam 46 toward the backward direction X2. Thereby, the lever biasing spring 23 is configured to urge the lever 22 in the backward direction XI via the translation cam 46 and the clutch unit 31. Further, in the present embodiment, the rod biasing spring 23 is exemplified as two coil springs (23, 23), but this is not the case, and 100138610 23 201221394 can be set as one coil spring or 3 More than one spiral spring. The brake output portion 21 shown in Figs. 3 to 5 is coupled to the rod 22 via a screw shaft 28, and is provided to be movable together with the rod 22. Thereby, the brake output portion 21 is configured to be movable in the forward direction 自 from the cylinder body 20 and to retreat in the backward direction Χ 2 in proximity to the cylinder body 20, and is configured to move the rod 22 toward the forward direction X1. Move and output the braking force. Further, the brake output unit 21 is coupled to the other brake lever 15 by the cylinder support pin 15b. Further, a gap adjustment mechanism is provided on the inner side and the outer circumference of the rod 22, and the gap adjustment mechanism includes a screw shaft 28 and a clutch. The unit 31 and a spring member (not shown) built in the rod 22 are formed. When the gap between the brake release state and the brake operation position is increased due to wear of the brake shoe 13 of the disc material device 1, etc., the gap can be automatically adjusted by the gap adjustment mechanism. In addition, the description of the detailed structure is omitted, but in the gap & week, the mechanism is configured to be connected to the rod 22 in a state where no gap due to abrasion or the like of the brake piece is generated. The relative position of the rod 22 of the screw shaft 28 does not change. If the gap is generated, the screw shaft 28 will protrude from the rod when the vehicle is in the braking operation, and the rods 28 are opposite to each other. The relative position of the glaze changes, and the gap is automatically adjusted. Fig. 6 is a cross-sectional view showing the position of the B-B line of the B-B line of the cylinder device 2, Fig. 7 is an exploded perspective view showing the actuator 24 and the boosting mechanism 25. The actuator 24 is configured as a rotary actuator which is disposed at a position "heavy" in the cylinder axis direction with respect to the rod u 100138610 24 201221394 and is rotated by supplying and discharging compressed air as a pressure fluid. Further, the actuator 24 includes a housing 32 output shaft 33, two blades (34, 35), two partition blocks (36, 37), a plurality of elastic bodies 38, and a plurality of lock members 39. Composition. Further, Fig. 6 shows the outer shape of the output shaft 33, the two blades (34, 35, the two partition blocks (10), 37) and the plurality of pin members 39, not the cross section. FIG. 8 is a perspective view showing a portion of the actuator 24. The cypress body 32 shown in FIGS. 3 to 8 is formed into a substantially cylindrical casing having a bottom portion and an opposite side of the bottom portion, and is fixed to the cylinder via the cylindrical guiding member 50 of the boosting mechanism 25 described below. Body 20. Further, the casing 32 is configured such that the supply of the compressed air as the pressurized fluid to the inside and the discharge to the outside are performed through the supply and exhaust port 32a formed through the wall portion of the casing 32. Further, the air supply and exhaust port 32a is connected to a compressed air supply and exhaust pipe (not shown), and is further connected to a compressed air supply source (not shown) and compressed air by switching a connection path by a switching valve (not shown). Exhaust port (not shown) β FIG. 9 is a perspective view showing the output shaft 33 and the blades (34, 35). The output shaft 33 shown in Figs. 3 to 7 and Fig. 9 is provided as a cylindrical member and is rotatably disposed in the casing 32. This output shaft 33 is provided as a member that outputs the driving force in the rotational direction of the actuator 24 as a rotational force. Further, a sleeve 40 provided as a cylindrical member is fixed to a central portion of the bottom of the inner side of the casing 32. Further, the output shaft 33 is disposed concentrically with respect to the sleeve 4A and is freely arranged to rotate 100138610 25 201221394 centering on the center axis ρ of the shaft center of the rod 22. That is, in a state in which the sleeve 40 is fitted to the output shaft 32, the inner circumference of the transmission_32 is slidably disposed relative to the outer circumference of the sleeve 40, and the output shaft 33 is disposed at the end of the output shaft 33. Between the bottoms of the cabinet 32. Further, a bearing 41 (see Figs. 4 and 5) for rotating the branch output shaft 33 with respect to the casing 32 is provided. The blades (34, 35) shown in Fig. 3 to Fig. 7 and Fig. 9 are provided in two pieces, and are separately formed into a flat plate shape, and are configured to extend from the output shaft % toward the radially outer side. The inner plurality of actuator pressure chambers (42a, 42b, 43a, 43b) are separated by 32. Further, the two blades (34, 35) are disposed at positions shifted by 18 degrees in the circumferential direction of the output shaft 33, and are fixed to the output shaft 33, respectively. Further, the blade 34 is provided with two rectangular plate-shaped bodies (34a, 34b) made of metal, and sandwiched between the plate-like bodies (34a, 34b) and combined with the plate-like bodies (34a, 34b). The resin rectangular sealing member 34c is formed. The sealing member 34c is slidably disposed on the inner wall of the casing 32, and is spaced apart from the following actuator pressure chambers (42a, 42b) in an airtight state. Similarly, the blade 35 is provided with two rectangular plate-shaped bodies (35a, 35b) made of metal, and sandwiched between the plate-like bodies (35a, 35b) and combined with the plate-like bodies (35a, 35b). The resin is made of a rectangular sealing member 35c. The sealing member 35c is configured to be slidably disposed on the inner wall of the casing 32, and is spaced apart from the following actuator pressure chambers (43a, 43b) in an airtight state. The partition blocks (36, 37) shown in Figs. 3 to 8 are provided with two 'and fixed to the inner side of the casing 32' and are disposed at the same time in the circumferential direction of the casing 32, respectively. 100138610 26 201221394 for 2 blades Between (34, 35). * Each of the partition blocks (36, 3) is disposed on the outer wall of the casing 32 and the outer periphery of the output shaft 33. The partition block 36 is made of metal and is formed into a substantially triangular column. The block body 36a and the second block body 36b and the rectangular sealing member 36c made of resin sandwiched between the block body 36a and the second block body 36b and joined to the second block body 36a and the second body member The sealing member 3 & is configured to be closely disposed on the inner circumference and the bottom surface of the casing 32, the outer circumference of the output shaft 33, and the end surface of the cylindrical guiding member 5 of the boosting mechanism 25, and is separated by an airtight state. Similarly, the partition body 37 is provided with a third block body 37a and a second block body 37a which are formed of a metal and formed into a substantially triangular column shape, and are sandwiched between the second ghost body 37a and the second block body. A resin-made rectangular sealing member 3 is formed between 37b and the first block 37a and the second block 37b. The sealing member 37C is configured to be closely disposed on the inner circumference and the bottom surface of the case 32, and the wheel The outer circumference of the shaft 33 and the end surface of the cylindrical guiding member 5〇 of the boosting mechanism 25 are disposed in the air-hanging state to partition the inside of the casing 32. Further, as shown in FIG. In the actuator 24, between one of the partition blocks 36^ and the other partition block 37, the one side vane 34 area ρ has the high pressure side actuator pressure chamber 42a and the low pressure side. The actuator pressure is 42b. Thus, the actuator pressure chamber on the high pressure side is composed of the first block %&, the inner circumference and the bottom surface of the blade phase body 32, the outer circumference of the output shaft 33, and the meandering V-shaped member. The end face of the 5 。 is separated. The actuator pressure chamber 々a on the low pressure side is composed of the second block 37b, the vane 34, the inner circumference and the bottom surface of the case 32, the outer circumference of the wheel shaft 100138610 27 201221394 33, and the end surface of the cylindrical guide member 50. Separate. Further, the supply and exhaust port 32a for supplying and discharging compressed air is provided so as to communicate with the actuator pressure chamber 42a on the high pressure side. Further, between the other partition block 37 and one of the partition blocks 36, the other side of the vane 35 is partitioned by the high pressure side actuator pressure chamber 43a and the low pressure side actuator pressure chamber. 43b. Thereby, the actuator pressure chamber 43a on the high pressure side is partitioned by the first block 37a, the vane 35, the inner circumference and the bottom surface of the casing 32, the outer circumference of the output shaft 33, and the end surface of the cylindrical guide member 50. The actuator pressure chamber 43b on the low pressure side is partitioned by the second block 36b, the vane 35, the inner circumference and the bottom surface of the casing 32, the outer circumference of the output shaft 33, and the end surface of the cylindrical guide member 50. Further, in Fig. 6, the blades (34, 35) in the state before the compressed air is supplied into the casing 32 are indicated by solid lines, and are in a state of being rotated after the compressed air is supplied into the casing 32. The blades (34, 35) are represented by two-point chain lines. Further, in the actuator 24, as shown in Figs. 3 to 6 and 9, a plurality of communication holes 44 are provided inside the output shaft 33 and the two blades (34, 35). Each of the communication holes 44 is provided to communicate with a hole of the actuator pressure chamber 42a on the high pressure side separated by one of the vanes 34 and the actuator pressure chamber 43a on the high pressure side partitioned by the other vane 35. In the present embodiment, two communication holes 44 are provided, and are formed to be bent once and extended inside the output shaft 33 and the two blades (34, 35). Further, two communication holes 44 are arranged in two in the cylinder axis direction, and the shape 100138610 28 201221394 extends in parallel along a plane perpendicular to the central axis P. Further, in Figs. 4 and 5, the position of the two communication holes 44 in the cylinder axis direction is indicated by a two-dot chain line. Further, each of the communication holes 44 is formed to communicate with the actuator pressure chamber 42a at the opening 44a of the opening of the vane 34, and communicates with the actuator pressure chamber 43a at the opening 44b of the opening of the vane 35. Thereby, the compressed air supplied from the supply and exhaust port 32a into the casing 32 is supplied to the actuator pressure chamber 42a, and is also supplied to the actuator pressure chamber 43a via the communication hole 44. The elastic body 38 shown in Figs. 6 to 8 is provided with a plurality of rubber members which are respectively provided in a block shape. Further, each of the elastic members 38 is configured by being inserted into a rectangular hole formed in the partition block (36, 37), and is disposed in a state in which the end portion is in the state of being separated from the partition block aa (36 37). Further, the blade attached to the blade (34, 35) is further configured such that the elastic body 38 that has been inserted into the first block 36a is placed in contact with the plate-like body 34 of the blade, and is inserted into the second block. The 36b bullet! In the manner of 35a, the spring I and the body 38 that are fitted into the second block 37b are placed in contact with the plate-like body of the blade 35. The pin member 39 shown in Fig. 4 and Fig. 6 to Fig. 8 is provided with a plurality of members which are elongated in a cylindrical shape and which are made of metal. Then, the bottom of each of the guide members and the cylinder are placed in the casing 32 and the cylindrical 100138610 29 201221394 guiding member 50 in a state in which the 'blocking body (36, 37) and the elastic body 30 are penetrated. In other words, the first block 36a and the elastic body 38, the second block 36b, the elastic body 38 embedded in the second block 36b, the first block 37a, and the first block embedded in the first block 36a are embedded in the first block. The elastic body 38 of 37a, the second block 37b, and the elastic body 38 fitted in the second block 37b are respectively penetrated by one pin member 39. Further, in Fig. 4, a two-point chain line is used. The position of the pin member 39 in the cylinder axis direction is shown. The force increasing mechanism 25 shown in Figs. 3 to 5 and 7 is provided as follows: If the actuating benefit 24 is rotated, the actuator 24 is placed. The driving force of the generated rotational direction is converted into a driving force in a linear direction parallel to the moving direction of the rod 22, and the rod 22 is moved in the forward direction XI against the urging force of the rod biasing spring 23, so that the actuator 24 is driven. The driving force is enhanced and acts on the rod 22°. The boosting mechanism 25 is provided with a rotating cam 45, a translation cam 46, a rolling cam 47, and a retainer. 48. A retainer biasing spring 49, a cylindrical guide member 50, a roller body 51, and the like. The figure shows a perspective view of the rotary cam 45, and shows a perspective view of a state in which the end portion on the actuator 24 side faces downward. (Fig. 10 (a)) and a perspective view showing a state in which the end portion on the actuator 24 side faces upward (Fig. 1 (b)). The rotary cam 45 shown in Fig. 3 to Fig. 5, Fig. 7, Fig. 10 It is provided as an annular member, and is provided as a member that is coupled to the output shaft 33 of the actuator 24 and rotates together with the output shaft 33. The rotary cam 45 is attached to the opposite side of the actuator 24 side (ie, the advancing direction) The end portion of the XI side is provided with a plurality of (six in the present embodiment) first 100138610 30 201221394 cam surface 45a. Further, the plurality of first cam faces 45a are arranged along the axis center of the rod 22 (that is, the central axis p) is arranged in the circumferential direction of the center, and each of the first cam faces 45a is also arranged to extend in the circumferential direction around the axis center of the rod 22. Further, each of the first cam faces The 45a is disposed in an inclined manner with respect to the axial direction of the rod 22. Further, the actuator 24 of the rotating cam 45 A plurality of (four in the present embodiment) concave portions 45b (see FIG. 10) are provided at the end portions of the side (that is, the 'reverse direction X2 side). The plurality of concave portions 45b are arranged side by side in the circumferential direction. A plurality of (four in the present embodiment) projections 33a are provided at the end of the rotating cam 45 side of the output shaft 33 (i.e., in the forward direction χι side), and the plurality of projections 33a are along the same Arranged in the circumferential direction (see Fig. 9). Each of the projections 33 & is provided corresponding to each of the recesses 45b, and each of the projections 33a is configured to be fitted into each recess. In the starting portion 33a, the pattern is formed by & _ into a columnar projection which is lower in the south, and = is formed as a recessed portion of the rectangular section. Further, in the state of the second vehicle, the IT is configured to bias the protrusion 22 toward the concave portion toward the wheel 46 and the roller 47 to apply the force to the rod 22. The wheel 45 is urged' to thereby translate the perspective view of the cam 46 in the reverse direction X2. Fig. 11 shows the Pingmen MJ to Fig. 5 and Fig. 5, and the outer cam 46 is in the forward direction χι side cylindrical portion 卩M, a % becomes a straight straight light 100138610 straight "shaped portion 52, and the backward direction Χ 2 side is formed The annular portion of the diameter of 31 201221394 is the large-diameter annular portion 53. On the inner side of the end portion on the advancing direction XI side, a solid portion: 52, as shown in Figs. 4 and 5). The second early warning element is coupled to the rod 22. The 0-state early 31 and the large-diameter annular portion 53 of the translation cam 46 are arranged to oppose the rotating cam 45 in a direction parallel to the rod direction. The shaft 53 is attached to the side of the rotary cam 45 (that is, the plurality of large-diameter annular portions in the backward direction have a plurality of (in the present embodiment, six) second to 卩, and the second cam surface 53a is slid along the rod 22 ^^^Rim 53& The plurality of central circumferential directions are arranged in order, and the central axis P) is also disposed along the center of the axis of the pair of rods 22 and each of the second cam faces 53a. Further, the direction in which the second cam faces 53 extend in the circumferential direction is set so as to be opposite to each other. The axial direction of the rod 22 is inclined. In the forward direction γ 1 y of the large-diameter annular portion 53, the end surface of the large-diameter annular portion 53 is disposed so as to be placed on the end surface of the small-shaped portion, and the rod biasing spring 23 is used. Moreover, the operation of the spiral 24 around the Sai, 52 52, and the direction of the forward direction of the squirting moxibustion, the straight spurs 53 are formed as the H叩 exert force; p π starts to move along the straight line 2 toward the forward direction and the clutch unit 31 as shown! 2 shows the rolling cams 47 and 2. Figure 5, Figure 7, and Figure 12 < Stereogram. In the embodiment of Fig. 3 to the embodiment, the roller system is slid into a plurality of (under the __ coffee, also referred to as "roller cam 47j", 32 201221394 and is rotatably supported by the holder 48. The retainer 48 is provided as an annular member, and a plurality of (six in the present embodiment) rotating shaft portions 48a extending toward the outer side in the radial direction are provided on the outer circumference thereof. Further, the rollers are provided. The cam 47 is rotatably supported by the respective rotating shaft portions 48a. Further, on the inner side of the retainer 48, the end portion facing the rotating cam 45 is formed so as to protrude inward in the radial direction and extend in the circumferential direction. The flange-shaped inner flange portion 48b. The plurality of roller cams 47 are rotatably held by the retainer 48, and are disposed between the first cam surface 45a and the second cam surface 53a. The sub cam 47 is rotatably disposed on each of the first cam faces 45a and the second cam faces 53a disposed in the opposing direction. Further, the side faces of the roller cams 47 are provided as rolling surfaces 47a, and the rolling faces 47a are configured a part of the conical surface in the circumferential direction The cam 47 extends in the circumferential direction and rolls with respect to the first cam surface 45a and the second cam surface 53a. Further, a plurality of roller cams 47 are disposed so as to be located along the center of the axis of the rod 22 On the circumference, it is disposed at a position equal to the circumferential direction of the retainer 48. Further, as shown in FIGS. 5, 10, and 11, a guide roller cam 47 is provided on the outer peripheral portion of the rotary cam 45. The guide wall 45c in the rolling direction, and also in the outer peripheral portion of the large-diameter annular portion 53 of the translation cam 46, is provided with a guide wall 53b for guiding the rolling direction of the roller cam 47. Each guide wall 45c is provided as Each of the first cam faces 45a has a wall portion that protrudes slightly in a direction orthogonal to the first cam faces 45a, and the 100138610 33 201221394 guide walls 53b are provided for each second. The radially outer side of the cam surface 仏 positive* cam surface 53a is along the wall portion which is less protruded as shown by the human air in Fig. 4 and Fig. 5. Between the annular annular portions 53, the retainer 48 and the translation cam 46 of the big. „ ^ There is a retainer force force, the Xianli force force 49 series is set to be placed on the pole I 49. The retainer applies and the retainer biases the spring 49. A spiral spring. The loop member 54 of the loop is cut and the end portion of the square is placed on the other side of the spring-side end portion; the end surface in the direction of the direction XI is supported by the retainer. The cyanine is configured to hold the core toward the rotating cam material: the holder is biased. FIG. 13 is a perspective view showing the cylindrical guiding member 5Q, and the cylindrical guiding centering mechanism shown in FIG. 13 is used to advance the direction of the drawing. 1 is a small-diameter cylindrical portion, that is, a small portion 55, and the ^X2 side is formed into a large-diameter annular portion, that is, a large-diameter annular portion, the annular portion 56 is connected to the casing 32 from the bolt (10) The second cylindrical portion 2 0 b is fixed to the body 20 . The small-diameter cylindrical portion 5 5 is provided as a cylindrical portion which is disposed so as to surround the axis of the rod 22 in the circumferential direction. Further, the two small-diameter cylindrical portions 55 are provided with guide portions 55a formed as holes having a long hole shape extending in a direction parallel to the axial direction of the rod 22. Furthermore, guide? In the present embodiment, the crotch portion 5 is provided at a position shifted by 180 degrees in the circumferential direction of the small-diameter cylindrical portion 55. The parent body 51 shown in Fig. 3, Fig. 4, Fig. 7, and Fig. 11 is provided in a cylindrical shape of 100138610 34 201221394, and is rotatably supported on the inner side of the small-diameter free portion 55 of the cylindrical guiding member 50. The flat Λ Λ Ί Ί . . . 多 多 多 多 多 多 多 多 多 多 多 多Two roller bodies 51 are provided. Further, 5〇 TM , the roller limbs 51 are arranged in the circumferential direction of the cylindrical guiding member 50, are disposed corresponding to the respective guide rollers 55a, and are arranged to roll each of the guide portions. Further, in order to smoothly roll the respective roller bodies 51 on the wall surfaces of the i-parts:: guide portions 55a, the width of each of the guide vanes is set to be slightly larger than the diameter of each of the light (four) outer circumferences. Further, in the case where the guide (four) 55a is formed as a hole as in the present embodiment, when the small-diameter cylindrical portion 52 of the translation cam 46 is inserted into the inner side of the J straight cylindrical portion 55 of the cylindrical guide member (4), Each of the light body members can be rotatably attached to the translation cam 46 from the outside of each of the guide portions 100 from the outside of the cylindrical guide member 50. Further, as shown in FIG. 5, in the boosting mechanism 25, the distance from the position of the central portion of the actuator 24 from the central portion of each of the blades (34, 35) to the central axis P is set to be larger than The distance from the position of the plurality of roller cams 47 to the central axis P is arranged. Thereby, it is configured to enhance the driving force generated by the actuator 24 and output from the lever 22. The brake cylinder device 2 rotates the blades (34, 35) and the output shaft by supplying compressed air to the actuator pressure chambers (42a, 43a) on the high pressure side via the supply and exhaust port 32a, and the rotation of the output shaft 33. The driving force is enhanced by the boosting mechanism 25 and transmitted to the rod 22, and the rod 22 is advanced toward the forward direction XI and the screw shaft 28 to thereby output the braking force from the brake output portion 21. Further, in the 100138610 35 201221394 brake cylinder device 2, the brake mechanism for generating the braking force by utilizing the operation of the actuator 24 to operate the power-increasing mechanism 22 is used for normal running of the railway vehicle. With respect to the above, the parking brake mechanism % shown in Figs. 3 to 5 is provided as a brake mechanism used when the railway vehicle equipped with the brake cylinder device 2 is parked. Further, the parking brake mechanism 26 includes a plurality of parking brake springs 57, a parking brake piston 58, and the like. A plurality of (two in the present embodiment) springs for parking brakes are respectively provided as spiral springs. Further, each of the parking brake springs 5 γ is disposed between the rainbow body 20 and the cylindrical guide member 50. That is, each of the parking brake springs 57 is attached to the inside of the cylinder main body 20 and disposed along the inner circumference of the cylinder main body 2, and is outside the small-diameter cylindrical portion of the meandering guide member 50 and along the small diameter. The cylindrical portion 55 is disposed on the outer circumference. Further, each of the parking brakes 57 is supported such that the end portion on one end side abuts against the parking brake piston %, and the other end portion abuts against the large diameter ring of the cylindrical guide member 5 The shape portion 56 is supported by the end surface of the front side X direction. Further, in the large-diameter annular portion 56 of the cylindrical guiding member 5, two supply and exhaust ports 59 (see FIG. 3 and FIG. 13) are provided, and each of the air supply and exhaust ports 59 is connected. The cylinder body 2 (four) is formed such that the spring chamber 60 of the brake spring 57 is placed. Further, each of the supply and exhaust ports 59 is provided as a through-hole (4) for supplying and discharging external air to the actuator chambers (4) and 43b) of the lower (four) actuators 24, and is placed in the pulse guiding member 100138610 36 201221394 50. Further, in each of the second blocks (36b, 37b) opposed to the respective vents 59, at a position opposed to each of the vents 59, a region for allowing air to pass through the vent 59 is formed in a recessed manner. The vent facing area 61 (see FIGS. 6 and 8). Further, in the second cylindrical portion 2b of the cylinder main body 2, a vent port that communicates with the spring chamber 60 and the outside is provided at a position (not shown), and the vent hole is formed to penetrate through the second portion. The hole in the tubular section. The brake lever 58 is disposed inside the cylinder body, and is disposed to be airtightly connected to the cylindrical portion of the cylinder body 2Q, the inner peripheral surface thereof and is movable along the cylindrical portion 27a. Axial sliding. By utilizing the space in which the parking brake piston 58 and the second tubular portion are separated, the cylinder body 20 is formed to release the parking brake-type brake release chamber 62. Further, the brake release chamber & is configured to supply and discharge compressed air as a pressure fluid via a communication path (not shown). Further, the parking brake piston 58 is provided with a disk-shaped portion Na, a cylindrical projection portion 58, and a translational cam coupling portion 58c. The circumscribing portion is provided in a disk-shaped portion that is slidably attached to the inner peripheral portion of the cylindrical portion of the i-th tubular portion on the sealing member embedded in the outer periphery. Further, in the disk-shaped portion, the through-holes are formed in the central portion, and the cylindrical projections 58b projecting from the edge portion of the through-holes toward the forward direction X! are formed in a cylindrical shape. For the body. On the outer circumference of the cylindrical projecting portion 58b, a sealing member that describes the inner circumference of the flange-like portion 27b of the i-th tubular portion 20a is slidably attached. Further, the disc-shaped portion 1 and the cylindrical projection portion of the parking brake piston 58 are 10 〇 13861 〇 _ 20122 1394 around the small-diameter cylindrical portion 55 surrounding the cylindrical guide member 5 around the translation cam 46. Configured. Thereby, the parking brake piston % is disposed so as to surround the shaft of the rod 22 and the translation cam 46 in the circumferential direction, and is provided to be movable in a linear direction parallel to the moving direction of the rod 22. The translational cam coupling portion 58c is attached to the parking brake piston %, and is provided in the cylindrical projection portion 5 as a portion opposite to the disk-shaped portion 58a, and is configured to have a convex portion from the end portion of the cylindrical projection portion 58b. A member having a rim shape formed on the inner side, a plurality of disk-shaped members having a large through-hole formed therein, and a tubular member disposed inside the rib. Further, the plural-disk-shaped member is fastened to the inside of the cylindrical projecting portion by a bolt and formed into a flange-like portion. Further, a plurality of disc-shaped connecting members "connecting members t and (10) are formed in a plurality of in-disk configurations via a joint. The member 63 is respectively slidably attached to the inner peripheral side of the camera and the outer peripheral side of the tubular member, and the translation member ώ钤 joint portion 58c is connected via the connecting member by the connecting member 63 + the human 牛 丄 卡 5 63 1 ground even #. Further, the cam cam is extended to the outside from the inner side of the end portion of the translational cam coupling portion 58e_^ from the forward direction XI side, thereby shifting the stepped groove of the cylinder η inside the cam coupling portion 58C. The ram-receiving piston 58 is oriented forward. The R-shaped member is configured to move only to the XI to engage the slidable cam 52, and is inserted into the slot 64 in the slot. The dam 52 is fixed around the circumference. Since the ring constitutes the parking brake mechanism 26 100138610 as described above, the brake is released by the brake release device 38 201221394 pressure chamber 62, and the parking brake force is generated by the action of the parking brake piston 5 > s 57 in the reverse direction X2. With the spring 57's parking brake/yoke force, it can maintain the state of not stopping the vehicle.) On the other hand, with the state of 7 car power (the dust is reduced, the parking spring is used, and the car is used. The pressure chamber 62 is released. The vehicular piston 58 is moved forward relative to the cylinder body 2, so that the parking swaying cam coupling portion 58c moves only to the booster X1, and is shifted by the Pingcheng 楫25.
藉此，自平移凸輪46經由離合器單元3ι 网6¼力。 對桿22施力，且使螺桿軸28與桿22〜朝向則進方向XI 移動，藉此，自煞車輸出部21產生作起朝則進方向X1 力。 為停車煞車之煞車 再者，於煞車缸裝置2中，如圖3乃闻 u J及圖4所示，於 輪連結部58c設置有解除停車煞車操作 、 、用環65。解除停車 煞車操翻環65係設置為利科動操作切除停車煞車用 之操作部。而且，於煞車缸裝置2中，播 冓成為藉由對此解除 停車煞車齡料65進雜扯操作，而,_未_之連桿 機構’使形成為環狀之連結構件63以朝徑向擴徑之方式運 作三藉此，解除停車煞車用活塞58之平移凸輪連結部地 之筒狀構件與連結構件63之卡纟，而解除平移凸輪連結部 58c之複數個圓盤狀之構件與筒狀構件之連結。而且，亦解 除停車煞車用活塞58之圓盤狀部58a側與平移凸輪46側之 連結，即便在自煞車解除壓力室62排出壓縮空氣之狀態， 100138610 39 201221394 之 亦成為不對平移凸輪46作用由停車煞車用彈簧W戶 作用力之狀態。 斤產生 若如上述解除停車料用活塞58之圓盤狀部I側邀、， 移凸輪46側之連結，則藉由桿施力彈篑23之作用、、平 移凸輪46朝後退方向X2移動，在受停車煞車^使平 力之圓盤狀部58a之位置未產生變化之狀態下 ^施 平移凸輪46 -起朝後退方向Μ移動。藉此，螺I 22與 煞車輸出部2!與桿22 一起朝後退方向幻移動而8及 煞車。由此’㈣社裝置2中，構成為於 57之煞車力發揮作心使停車煞車運作之狀態;·=脊 對煞車解除壓力室62供給麼縮空氣，亦可藉由對解除^ 煞輪作用環65進行拉扯操作，而解除停車敏車。τ 又，由於煞車缸裝置2係如上述方式所構成，因此，車 煞車物簧57、停車煞車用活塞％及致動器24之τ 35)係於與桿22之軸向平行之方向上重疊地配置。又，於敏 車缸裝置2中，設定為於致動器24之旋轉動作中^轉角 度、即各葉片（34、35)之旋轉角度為90度。 接著，一面參照作為煞車紅裝置2之立體圖之利用切明 面表示内部結構之圖式即圖3、圖14至圖18，一面對敦車 缸裝置2之運作進行說明。圖3係表示對應於圖4及圖5 之剖面圖之狀態之圖式，且係自供排氣口 32a並未對箱體 32内供給壓縮空氣’而對煞車解除壓力室62供給壓縮空氣 100138610 201221394 之狀態。即，圖3所示狀態之煞車缸裝置2係未產生煞車力 之狀態。 若自上述圖3所示之狀態經由供排氣口 32a開始對箱體 32内供給壓縮空氣，則自圖3所示之狀態就會轉變為圖14 所示之狀態，而經由圖15所示之狀態，最終將轉變為圖16 所示之狀態。再者，圖14所示之狀態係表示桿22朝前進方 向XI前進至其所有步驟（全衝程）中三分之一左右之步驟之 狀態。又，圖15所示之狀態係表示桿22朝前進方向XI前 進至其所有步驟中三分之二左右之步驟之狀態。又，圖16 所示之狀態係表示桿22朝前進方向XI前進至其所有步 驟，而自煞車輸出部21中輸出煞車力之狀態。 再者，若自供排氣口 32a將壓縮空氣供給至箱體32内， 則所供給之壓縮空氣將於箱體32内填充至高壓側之致動器 壓力室42a，並且經由連通孔44亦填充至高壓側之致動器 壓力室43a。然後，藉由填充至致動器壓力室（42a、43a)之 壓縮空氣，對各葉片（34、35)施力，而使輸出軸33旋轉。 此時，各低壓側之致動器壓力室（42b、43b)内之空氣係經由 各供排氣口 59流動至彈簧室60,進一步經由連通將彈簧室 60與外部之通氣口流出至外部。藉此，葉片（34、35)係自 抵接於安裝在第1塊體(36a、37a)之彈性體38之位置起， 直至抵接於安裝在第2塊體（36b、37b)之彈性體38之位置 為止，沿箱體32之圓周方向旋轉，而使輸出軸33旋轉90 100138610 41 201221394 度。 若如上述使致動器24運作而使輸出軸33旋轉，則如圖 14至圖16所示，增力機構25係抵抗自桿施力彈簧23傳遞 之作用力而運作。即，旋轉凸輪45將與輸出軸33〜起沪既 疋之旋轉方向（自煞車輸出部21側觀察為沿著逆時針方向 旋轉之方向）旋轉，且第丨凸輪面45a亦與旋轉凸輪45 —起 以桿22之軸中心為中心進行旋轉。藉此，使滾子凸輪π 相對於第1凸輪面45a與第2凸輪面53a—面滾動一面旋轉。 若滾子凸輪47隨著旋轉凸輪45之旋轉而旋轉，則滾子凸 輪47將一面沿著相對於桿22之袖向傾斜地設置之第2凸輪 面53a旋轉一面朝前進方向χ1移動。此時，相對於桿22 之軸向傾斜所設置之第2凸輪面53a，將隨著滾子凸輪47 之旋轉而進一步被推向前進方向X1。又.，此時，一面沿著 筒狀導引構件55之長孔狀之導引部55a滾動面移動之輥 體51之移動方向被限制在與桿22之軸向平行之方向。因 此，僅被容許與桿22之轴向平行之方向上之移動的平移凸 輪46，將抵抗桿施力彈簧23之作用力而朝向刖進方向XI 移動。 若平移凸輪46朝向前進方向XI移動，則經由離合器單 元31連結於平移凸輪46之桿22與平移凸輪46將一起朝向 前進方向XI移動。然後，螺桿軸28與桿22將一起朝前進 方向XI移動，而連結於螺桿轴28之煞車輸出部21亦沿前 100138610 42 201221394 進方向xi移動。然後，—對煞車片（13、13)按壓煞車碟片 ιοί，使煞車輸出部21與桿22 一起朝前進方向χι移動既 疋里直至使致動器24之葉片（34、35)成為旋轉90度後停 止之圖16所示之狀態為止，而輸出所需之煞車力。 於自煞車運作之圖16所示之狀態解除煞車之情形時，進 行與上述相反之動作。即，自供排氣口 32a排出壓縮空氣， 藉由桿施力彈簧23之作用力使平移凸輪46與桿22 —起朝 後退方向X2開始移動，且藉由第2凸輪面53&所推動之滾 子凸輪47朝與煞車運作時之相反方向旋轉。然後，使滾子 凸輪47 —面於第i凸輪面45a上滾動一面朝後退方向χ2 移動’而使旋轉凸輪45朝與煞車運作時相反之旋轉方向（自 煞車輸出部21側觀察時為沿順時針方向旋轉之方向）旋 轉。藉此，使輸出軸33及葉片（34、35)亦與旋轉凸輪45 一 起朝與煞車運作時相反之旋轉方向旋轉。 再者，於上述過程中，自高壓側之致動器壓力室42a將壓 縮空氣經由供排氣口 32a排出，且自高壓側之致動器壓力室 43a將壓I®空氣經由連通孔44、致動器壓力室42a及供排氣 口 32a排出。然後大氣壓之空氣係經由連通缸本體2〇之外 部與彈簧室60之通氣口而自外部流入彈簧室6〇内。然後， 此空氣進一步經由各供排氣口 59流入各低壓側之致動器壓 力室（42b、43b)。而且，於結束將壓縮空氣自箱體32内排 出之狀態下，返回至圖3所示之狀態。再者，若桿22朝後 100138610 43 201221394 ，方向X2移動’則螺桿轴28及連結於螺縣2 出部21亦朝後退方向χ2移動。 …、車輸 再者，上賴車動作及煞車解除動作· 作，且於煞車解除壓力室62中維持隨時供給2之動 態。相對於此’於進行鐵路車輛之停車而車：：之狀 %之情形時，自煞車解除壓力室 了車」，、、車機構 係表示停車煞車機構26進行運空氣。圖η 車力之狀態。 知運作而產生作為停車煞車之煞 若自煞車解除壓力室62排出壓縮空氣， 用彈簧57之作用力將朝前進方向 9 τ車煞車 施力。然後，藉由停車 、，Τ煞車用活塞58 將使受此停車煞車用活=用^ 58朝前進方向X!移動， a w 塞58施力之平移凸輪46亦知么 向X1移動。若平移凸輪46朝前進方向幻移：進方 合:單元31而連結於平移凸輪46之桿22進則:由離 移動’且煞車輪出部21亦朝前進方向χι:進方向X1 生作為停車煞車之煞車力。 。错此，產 又’若自圖17郎·- 進行拉扯操作，料；對獅停車煞車縣用環6 即，連結構件㈣作:Γ成為解除停車煞車之狀態。 5 8 a側與平移凸鈐 “T車煞車用活塞5 8之圓盤狀部 用力，使平移凸輪而藉由桿施力彈普23之作 停車煞車用彈菩 k方向X2移動。然後，在受到 100138610 -、力之圓盤狀部58a之位置未產生變化 44 201221394 46 —起朝後退方向χ2移 之狀態下’使桿22與平移凸輪 而解除停車 動，使煞車輸出部21亦朝後退方向χ2移動， 敏車。 “、、-} 如以上所說明’根據煞車缸農置2，其構成為使桿Μ於 沿缸轴方向之直線方向上進行前進動作及後退動作，而且， 旋轉型之致動器24係以於紅軸方向上與桿22重疊之方式所 配置。因此’可使致㈣24及桿22之配置^於缸讀 20之徑向及軸向上有效率地變小。而且，可於利用致動器 24及桿22之配置空間之效率化所確保之區域中，配置使來 自致動器24之旋轉方向之驅動力轉換為直線方向而增強並 作用於桿22之增力機構25。然後，自與經増強 作用之桿22—起移動之煞車輸出部輸出煞車力。如此， 動::4及桿22之配置空間之效率化而她 二增力二力化，從而實現小型化，並且可藉由增力機構 置之大型 所輸出之 因此，根據本實施形態，可提供能夠—面抑制農 化’一面增加自與桿22-起移動之煞車輸出部21、 煞車力的小型之煞車缸裝置2。 =’根據煞輪農置2，與設置有_之致動器及將此致 動益之直線方向之驅動力轉換為婦方向而增強後使直線 方向之驅動力彻於桿之增力機構賴輪裝置相比，亦可 因零件個數之削減而實現輕量化及小型化。 100138610 45 201221394 又，根據煞車缸裝置2，於增力機構25中，設置為在相 互對向之第1凸輪面45a與第2凸輪面53a之間配置有滾動 凸輪47，且使第〗凸輪面45a及第2凸輪面朝桿之 軸向傾斜。因此，可彻簡單之結構實現使桿22伴隨致動 器24之輸出軸33之；$疋轉而經由滾動凸輪47之滾動朝前進 方向X1移動之構成。然後，亦可使致動器24之驅動力， 於方疋轉凸輪45與平移凸輪47之間有效率地由旋轉方向轉換 為則進方向X1 °而且’可藉由設本體2G之徑向（或桿 22之徑向）之致動器24、第i凸輪面45a、第2凸輪面^ 及滚動凸輪47之配置’而容易地調整增力之比率。 又’根據煞秘裝置2,第1凸輪面及第2凸輪面53a 之又方係傾斜於梓22之軸向所設置，且於其等之間配置有 作為具有構成圓錐 滚動凸輪47。因此，邀a 興將滾動凸輪47設置為球狀之球面凸 輪之情形相比，可降低你m # 低作用於1個滾動凸輪47之接觸面壓。 而且，關於使桿22伴隨旋轉凸輪衫之旋轉而經由滾動凸輪 47朝前進方向XI移動時之前進衝程(前進輯），在可利用 較少之旋轉凸輪45之旋轉量達成較大之前進衝程之情形 下’於將球面凸輪用作滾動凸輪47之情形時，原本需要大 直徑者，但若使用浪子凸輪47，則不會形成大型化，而可 將與桿22之軸向傾斜之第1凸輪面W及第2凸輪面53a 之傾斜之斜率設定為更_之斜率。因此，可-面有效率地 100138610 46 201221394 抑制煞車虹裝置2之大型化，一面任意且容易地確保前進衝 程。 又’根據煞車缸裝置2，可利用如於旋轉凸輪45及平移 凸輪46之外周部分設置導引壁(45c、53b)的簡單構成，導 引滾子凸輪47之滾動方向。而且，由於利用導引壁(45c、 53b)導引滾子凸輪47之滾動，因此’對於旋轉自如地支樓 滾子凸輪47之結構體(於本實施形態中為保持器48)，亦可 使構成簡化。藉此’可實現裝置之更小型化及輕量化。 又，根據本實施形態，可將如下之停車煞車機構26組裴 於煞車缸裝置2，該停車煞車機構26係具備產生停車煞車 之煞車力之停車煞車用彈簧57、藉由受到停車煞車用彈簧 57施力而經由平移凸輪46對桿Μ施力之停車煞車用活塞 58、及解除停車煞車用之煞車解除壓力室62。而且，由於 與桿22之移動方向平行地移動之料煞車黯塞％係以包 圍桿22及平移凸輪46之軸周圍之方式所配置，因此，對^ 停車煞車用活塞58之配置空間亦可進行效率化 缸軸方向上使停車鮮機構26之二、 車缸奘罟7夕丨別 罝工门欢旱化而貫現煞 車#置之小型化。又，根據煞車置2 25中設置有朝向輯凸輪 、日力機構 七㈣μ门 保待盗48施力之保持哭施 因此，即便於停車煞車機_運 ^ 凸輪46朝前進方向χ1施力之情形日士 僅對千移 彈菩49，姊由彳n ^ ^ ，、错由保持器施力 由保持器48於旋轉凸輪45侧對滾子凸輪47施 100138610 201221394 力’而將5亥滾子凸輪47保持於既定之位置。藉此’可藉由 如設置有保持器施力彈簧49的簡單構成，而於停車煞車機 構26之運作時保持滾子凸輪47之位置。 又’根據煞車缸裝置2，由於致動器24係異備固定於缸 本體20之箱體32、於箱體32内進行旋轉之輸出軸33、及 自輸出軸33延伸且區隔致動器壓力室（42a、42b、43a、43b) 之2片葉片（34、35)所構成’因此，可緊凑地構成於缸軸方 向上與桿22重疊地配置之旋轉型致動器24。 又，根據煞車缸裝置2，停車用煞車用彈簧57及停車煞 車用活塞58與致動器24之葉片（34、35)，係於與桿22之 軸向平行之方向上重疊地配置。因此，可使彈簧煞車形式之 停車煞車機構26、葉片型之旋轉型致動器24、及具有旋轉 凸輪45與滾動凸輪47之增力機構25之配置空間於缸本體 20之徑向上有效率地變小。又，藉此，可利用與有效率地 配置之停車煞車機構26之配置空間之關係，更有效地活用 缸本體20之徑向之空間，而可有效率地設定旋轉凸輪μ 之直径、滚動凸輪47之數量及致動器24之旋轉角卢，使辦 力機構25之構成最佳化。即，可一面使旋轉凸輪β之直徑 與滾動凸輪47之數量最佳化而充分地降低作用於各滾動凸 輪47之負載，一面可以充分地確保前進方向之衝程之方式 設定凸輪面（45a、53a)之斜度而實現致動器24 <旋轉角度 之最佳化。 100138610 48 201221394 又，根據煞車缸裝置2,可藉由將突起部33a嵌入凹部45b 而容易地組裝旋轉凸輪45與設置有葉片（34、35)之輸出轴 33，而且，可藉由利用桿施力彈簧23之作用力沿輸出軸33 對旋轉凸輪45施力而將旋轉凸輪45與輸出軸33緊固。因 此，對於增力機構25之旋轉凸輪45與致動器24之輸出轴 33，可利用簡單之結構進行緊固，並且可容易地進行組裝。 又，根據煞車缸裝置2，可藉由利用桿施力彈簧23之作 用力沿輸出軸33對旋轉凸輪45施力而將旋轉凸輪45與輸 出軸33緊固，並且可藉由保持器施力彈簧49朝向旋轉凸輪 45對保持器48施力。因此，即便於停車煞車機構26運作 而僅朝前進方向XI對平移凸輪46施力之情形時，亦可除 了藉由桿施力彈簧23之外並藉由如設置保持器施力彈簧49 的簡單構成，保持滾子凸輪47之位置。 又，根據煞車缸裝置2，其構成為經由設置於輸出軸33 及葉片（34、35)内部之連通孔44，使一方之高壓側之致動器 壓力室42a與另一方之高壓側之致動器壓力43a連通。因 此，可僅藉由對高壓侧之致動器壓力室42a供給壓縮空氣， 而使雙方之高壓側之致動器壓力室（42a、43a)以相同之時序 運作。而且，與在箱體32内設置連通一方及另一方之高壓 側之致動器壓力室（42a、43a)之連通孔44之情形相比，可 使箱體32之壁厚變薄。因此，可實現致動器24之小型化， 藉此，可實現煞車缸裝置2之更小型化。 100138610 49 201221394 又，根據煞車缸裝置2，可藉由如在固定於缸本體2〇且 包圍桿22之軸周圍之筒狀導引構件50設置作為孔之導引部 55a，並且於平移凸輪46旋轉自如地設置輥體51的簡單結 構’而容易地構築使平移凸輪46停止轉動之結構。 又，根據煞車缸裝置2，可藉由將兩端嵌入筒狀導引構件 50與箱體32之銷構件39，而將與葉片（34、35)之間所區隔 高壓側及低壓側之致動器壓力室（42a、43a、42b、43b)之區 隔塊體（36、37)、及嵌入此區隔塊體(36、37)且葉片（34、35) 抵接之彈性體38於貫通狀態下進行固定。因此，於筒狀導 引構件50與箱體32之間，無需使用藉由如螺栓及螺帽的複 數個構件來緊固之緊固機構，便可將區隔塊體(36、37)及彈 性體38加以固定。由此，可實現零件個數之削減，而實現 煞車缸裝置2之更輕量化。 又，根據煞車缸裝置2 ’其設置為藉由區隔塊體(36、37)， 而與葉片（34、35)之間區隔高壓側及低壓側之致動器壓力室 (42a 43a、42b、43b)，且可使對各低壓側之致動器壓力室 (42b、43b)供給及排出外部空氣之供排氣口 ％連通於配置 有停車煞車用彈簧57之彈簧室60。因此，可藉由簡單之結 構谷易地構築藉由於缸本體2〇中僅設置丨個將彈簧室 連通至外部之通氣口，而使各低壓側之致動器壓力室(42b、 43b)與外部連通之構成。 又，根據本實施形態，可提供一種能夠一面抑制裝置之大 100138610 50 201221394 型化一面增加煞車力之小型之碟片煞車裝置1。 以上’雖然已針對本發明之實施形態進行說明，但本發明 並不限定於上述實施形態，可於申請專利範圍所記載之範圍 内進行各種變更後並加以實施。例如，可實施如下之變形例。 (1) 於上述實施形態中，雖然已經以藉由壓力流體進行作 •動之形態之致動器為例進行說明，但並不限定於此形態，亦 - 可實施設置有各種形態之旋轉型或擺動型之致動器的煞車 缸裝置。例如，亦可實施設置具有電動馬達之形態之致動 器、或具有油壓馬達之形態之致動器等的煞車缸裝置。 (2) 於上述實施形態中，雖然已經以旋轉型之致動器為例 進行說明，但亦可實施設置有擺動型而非旋轉型之致動器的 煞車缸裝置。又，於上述實施形態中，作為葉片型之致動器 雖然已經以具有2片葉片之致動器之形態為例進行說明，但 亦可並非如此，亦可實施設置有具有1片葉片或3片以上葉 片之致動器的煞車缸裝置。再者，於對輸出軸設置有1片懸 • 臂狀葉片之致動器之形態之情形時，亦可定義為旋轉型之致 . 動器及擺動型之致動器中之任一者。 (3) 又’於上述實施形態中，雖然已針對旋轉型致動器之 旋轉角度為90度之情形進行例示，但亦可並扑如此，亦可 實施設置有未達90度之旋轉角度之致動器、或超過90度之 旋轉角度之致動器的煞車缸裝置。又，於此情形時，亦可實 施設置有旋轉360度以上之致動器的煞車缸裝置。 100138610 51 201221394 (4)關於增力機構，並 形態，亦可進行各種變更 "上述實施形態中所例示之 態中，雖然已經以使用铲並加以實施。又，於上述實施形 行說明，但亦可並非如此 _作為滚動凸輪之形態為例進 球面凸輪之滾動凸輪之开3 1 亦可為使用構成為球狀之 及第2凸輪面，亦可構成^為4。於此情形時，關於第1凸輪面 狀並且具有相對於桿之·康東面凸輪之形狀形成為曲面 關於滾動凸輪之配置或2傾斜之面的傾斜槽之形態。又， 例示之㈣，'村進行各於上述實施形態中所 ⑷於上述實施形態中，雜然更二並加以實施。 仏品夕不土 、、工以第1凸輪面及第2凸 輪面之兩者均設置為柏對於 ° 干〈軸向傾斜之形態為例進行 由亦可亚非如此。亦可實施將^凸輪面及第2凸輪 面之至少任一凸輪面設置為相對於桿之轴向傾斜之形態。 ⑺於上述實施形態中，_已經以於旋轉凸輪及平移凸 輪雙方之外周部分設置有料滾子凸輪之滾動方向之導引 壁之形態為例進行朗，但亦可鱗如此。例如，亦可為於 旋轉凸輪及平移凸輪之一方之外周部分設置有導引滾子凸 輪之滾動方向之導引壁之形態。 (6)於上述實施形態中，雖然已經以將突起部設置於輸出 軸’且將嵌入突起部之凹部設置於旋轉凸輪之形態為例進行 說明’但亦可並非如此。亦可為將突起部設置於旋轉凸輪， 且將凹部設置於輸出軸之形態。 10013S610 52 201221394 ⑺關於連結平移凸輪與桿之結構，並不限定於上述實施 形態中所例示之形態，亦可進行各種變更後並加以實施。 又，關於連結桿與煞車輸出部之結構，並不限定於上述實施 形態中所例示之形態，亦可進行各種變更後並加以實施。 (產業上之可利用性） 本發明可廣泛應用於藉由使桿自缸本體前進而輸出煞車 力之煞車缸裝置、及具備該煞車缸裝置之碟片煞車裝置。 【圖式簡單説明】 圖1係本發明一實施形態之碟片煞車裝置之側視圖。 圖2係圖1所示碟片煞車裝置之俯視圖。 圖3係本發明一實施形態之煞車缸裝置之立體圖，且係以 切口剖面表示内部結構之圖式。 圖4係圖3所示煞車缸裝置之剖面圖。 圖5係圖4所示煞車缸裝置之A-A線箭線位置之剖面圖。 圖6係圖4所示煞車缸裝置之B-B線箭線位置之剖面圖。 圖7係表示圖3所示煞車缸裝置之致動器與增力機構之分 解立體圖。 圖8係表示圖7所示致動器之一部分之立體圖。 圖9係表示圖7所示致動器之輸出軸及葉片之立體圖。 圖10係圖7所示增力機構之旋轉凸輪之立體圖、及表示 其反向之旋轉凸輪之立體圖。 圖11係表不圖7所不增力機構之手移凸輪之立體圖。 100138610 53 201221394 圖12係表示圖7所示增力機構之滾子凸輪及保持器之立 體圖。 圖13係表示圖7所示增力機構之筒狀導引構件之立體圖。 圖Η係用以說明圖3所示煞車缸裝置之運作之立體圖， 且係以切口剖面表示内部結構之圖式。 圖15係用以說明圖3所示煞車虹裝置之運作之立體圖， 且係以切口剖面表示内部結構之圖式。 圖16係用以說明圖3所示煞車缸展置之運作之立體圖， 且係以切口剖面表示内部結構之圖式。 圖17係用以說明圖3所示煞車缸裝置之運作之立體圖， 且係以切口剖面表示内部結構之圖式。 圖18係用以說明圖3所示煞車紅裝置之運作之立體圖， 且係以切口剖面表示内部結構之圖式。 【主要元件符號說明】 1 2 11 12 12a 13 14 14a 碟片煞車裝置 煞車缸裝置 卡鉗本體 背板 支撐銷 煞車片 結合構件 擺動銷 100138610 54 201221394 15 煞車槓桿 15a 支點銷 15b 缸支撐銷 20 缸本體 20a 第1筒狀部 20b 第2筒狀部 21 煞車輸出部 22 桿 22a 階部 23 桿施力彈簧 24 致動器 25 增力機構 26 停車煞車機構 27a 筒狀部分 27b 凸緣狀部分 28 螺桿軸 29、30 螺栓 31 離合器單元 32 箱體 32a 供排氣口 33 輸出軸 33a 突起部 100138610 55 201221394 34、35 葉片 34a、34b、35a、35b 板狀體 34c 、 35c 、 36c 、 37c 密封構件 36、37 區隔塊體 36a、37a 第1塊體 36b ' 37b 第2塊體 38 彈性體 39 銷構件 40 套筒 41 軸承 42a、42b、43a、43b 致動器壓力室 44 連通孔 44a、44b 開口 . 45 旋轉凸輪 45a 第1凸輪面 45b 凹部 45c ' 53b 導引壁 46 平移凸輪 47 滾動凸輪 47a 滾動面 48 保持器 48a 旋轉軸部 100138610 56 201221394 48b 内側凸緣部 49 保持器施力彈簧 50 筒狀導引構件 51 輥體 52 小直徑筒狀部 53 大直徑環狀部 53a 第2凸輪面 54 環構件 55 小直徑筒狀部分 55a 導引部 56 大直徑環狀部分 57 停車煞車用彈簧 58 停車煞車用活塞 58a 圓盤狀部 58b 筒狀突起部 58c 平移凸輪連結部 59 供排氣口 60 彈簀室 61 通氣口對向區域 62 煞車解除壓力室 63 連結構件 64 環 100138610 57 201221394 65 解除停車煞車操作用環 100 車輛本體 100a 托架 101 煞車碟片 101a 制動面 A-A 剖·面線 B-B 剖面線 P 中心軸線 XI 前進方向 X2 後退方向 100138610 58Thereby, the self-translation cam 46 is biased by the clutch unit 3⁄4. The lever 22 is biased, and the screw shaft 28 and the rod 22 are moved in the forward direction XI, whereby the braking force output portion 21 generates a force in the forward direction X1. Further, in the vehicle-cylinder device 2, as shown in Fig. 3, as shown in Fig. 3 and Fig. 4, the wheel connecting portion 58c is provided with a parking brake operation and a ring 65. Disengage the parking The 65-inch brake ring is set to operate the Ricoh operation to remove the parking brake. Further, in the crucible cylinder device 2, the sowing is caused by the unloading of the parking age of the vehicle age 65, and the link mechanism of the "not" is formed in a ring-shaped connecting member 63 in the radial direction. The method of expanding the diameter is three, thereby releasing the latch of the cylindrical member of the translational cam coupling portion of the parking brake piston 58 and the coupling member 63, and releasing the plurality of disc-shaped members and the cylinder of the translational cam coupling portion 58c. The connection of the members. Further, the connection between the disk-shaped portion 58a side of the parking brake piston 58 and the translation cam 46 side is released, and even if the compressed air is discharged from the brake release pressure chamber 62, the 100138610 39 201221394 does not act on the translation cam 46. The state of the W-home force of the parking brake. When the pulsation is released as described above, the disk-shaped portion I of the parking material piston 58 is released, and the movement of the cam 46 side is caused by the action of the rod biasing force 23 and the translation cam 46 moving in the backward direction X2. The translation cam 46 is moved in the backward direction Μ in a state where the position of the disc-shaped portion 58a of the flat force is not changed by the parking brake. Thereby, the screw I 22 and the brake output unit 2! are moved in the backward direction together with the lever 22, and the vehicle is braked. Therefore, in the apparatus (4), the vehicle is configured to operate in a state in which the vehicle is operated at a speed of 57; and the ridges supply the air to the brake chamber 62, and the air can be released by the brake wheel. The ring 65 performs a pulling operation to release the parking sensitive vehicle. τ Further, since the brake cylinder device 2 is configured as described above, the ram body spring 57, the parking brake piston %, and the actuator 24 τ 35) are overlapped in the direction parallel to the axial direction of the rod 22. Ground configuration. Further, the Yumin cylinder device 2 is set such that the rotation angle of the actuator 24, that is, the rotation angle of each of the blades (34, 35) is 90 degrees. Next, the operation of the Dun Cart cylinder device 2 will be described with reference to Figs. 3 and 14 to 18, which are schematic views showing the internal structure, which is a perspective view of the vehicle red device 2. 3 is a view showing a state corresponding to the cross-sectional views of FIGS. 4 and 5, and the compressed air is supplied to the brake release pressure chamber 62 from the supply and exhaust port 32a without supplying compressed air to the inside of the casing 32. 2012381394 State. That is, the brake cylinder device 2 in the state shown in Fig. 3 is in a state in which the braking force is not generated. When the compressed air is supplied into the casing 32 from the state shown in FIG. 3 via the air supply and exhaust port 32a, the state shown in FIG. 3 is changed to the state shown in FIG. 14, and as shown in FIG. The state will eventually change to the state shown in Figure 16. Further, the state shown in Fig. 14 indicates the state in which the rod 22 is advanced in the advancing direction XI to about one-third of all the steps (full stroke). Further, the state shown in Fig. 15 indicates a state in which the rod 22 advances to the forward direction XI to about two-thirds of all the steps. Further, the state shown in Fig. 16 indicates the state in which the lever 22 is advanced to the forward direction XI to all of its steps, and the braking force is output from the brake output portion 21. Further, when compressed air is supplied into the casing 32 from the supply and exhaust port 32a, the supplied compressed air is filled into the actuator pressure chamber 42a of the high pressure side in the casing 32, and is also filled via the communication hole 44. To the actuator pressure chamber 43a on the high pressure side. Then, the blades (34, 35) are biased by the compressed air filled in the actuator pressure chambers (42a, 43a) to rotate the output shaft 33. At this time, the air in the actuator pressure chambers (42b, 43b) on the respective low pressure sides flows through the respective supply and exhaust ports 59 to the spring chamber 60, and further flows out of the spring chamber 60 and the external vent to the outside via communication. Thereby, the blades (34, 35) are abutted against the elastic body 38 attached to the first block (36a, 37a) until they abut against the elasticity attached to the second block (36b, 37b). The position of the body 38 is rotated in the circumferential direction of the casing 32, and the output shaft 33 is rotated by 90 100138610 41 201221394 degrees. When the actuator 24 is operated to rotate the output shaft 33 as described above, as shown in Figs. 14 to 16, the boosting mechanism 25 operates against the urging force transmitted from the lever biasing spring 23. In other words, the rotating cam 45 rotates in the direction of rotation of the output shaft 33 to the starting point (the direction in which the vehicle is rotated in the counterclockwise direction as viewed from the side of the brake output unit 21), and the second cam surface 45a is also coupled to the rotating cam 45. The rotation is centered on the center of the shaft of the rod 22. Thereby, the roller cam π is rotated while rolling on the first cam surface 45a and the second cam surface 53a. When the roller cam 47 rotates in accordance with the rotation of the rotary cam 45, the roller cam 47 moves in the forward direction χ1 while rotating along the second cam surface 53a which is disposed obliquely with respect to the sleeve 22. At this time, the second cam surface 53a provided to be inclined with respect to the axial direction of the rod 22 is further pushed in the forward direction X1 in accordance with the rotation of the roller cam 47. Further, at this time, the moving direction of the roller body 51 which moves along the rolling surface of the long hole-shaped guide portion 55a of the cylindrical guiding member 55 is restricted in the direction parallel to the axial direction of the rod 22. Therefore, only the translation cam 46 that is allowed to move in the direction parallel to the axial direction of the rod 22 moves against the urging force of the rod urging spring 23 toward the plunging direction XI. When the translation cam 46 moves toward the forward direction XI, the lever 22 coupled to the translation cam 46 via the clutch unit 31 and the translation cam 46 move together toward the forward direction XI. Then, the screw shaft 28 and the rod 22 will move together in the forward direction XI, and the brake output portion 21 coupled to the screw shaft 28 also moves in the front direction 100138610 42 201221394. Then, the brake disc (13, 13) is pressed against the brake disc ιοί, so that the brake output portion 21 and the rod 22 move in the forward direction χ to move the ridge until the blades (34, 35) of the actuator 24 are rotated 90. After the degree is stopped, the state shown in Fig. 16 is stopped, and the required braking force is output. When the brake is released in the state shown in Fig. 16 of the brake operation, the reverse operation is performed. That is, the compressed air is discharged from the supply and exhaust port 32a, and the translational cam 46 and the rod 22 start to move in the backward direction X2 by the urging force of the lever biasing spring 23, and are pushed by the second cam surface 53 & The sub cam 47 rotates in the opposite direction to when the brake is in operation. Then, the roller cam 47 is rolled on the i-th cam surface 45a while moving in the backward direction χ2, and the rotary cam 45 is rotated in the opposite direction to the brake operation (the side is viewed from the brake output portion 21 side). Rotate in the direction of clockwise rotation). Thereby, the output shaft 33 and the blades (34, 35) are also rotated together with the rotary cam 45 in the opposite rotation direction as when the brake is being operated. Further, in the above process, the compressed air is discharged from the high pressure side actuator pressure chamber 42a via the supply and exhaust port 32a, and the pressure I® air is passed from the high pressure side actuator pressure chamber 43a via the communication hole 44, The actuator pressure chamber 42a and the supply and exhaust port 32a are discharged. Then, the atmospheric pressure air flows into the spring chamber 6〇 from the outside via the vent opening of the communication cylinder body 2 and the spring chamber 60. Then, this air further flows into the actuator pressure chambers (42b, 43b) on the respective low pressure sides via the respective supply and exhaust ports 59. Then, in a state where the compressed air is discharged from the inside of the casing 32, the state returns to the state shown in Fig. 3 . Further, when the lever 22 is moved toward the rear 100138610 43 201221394 and the direction X2 is moved, the screw shaft 28 and the screw portion 28 connected to the screw county 2 are also moved in the backward direction χ2. ..., the vehicle is transported, and the vehicle is operated and the vehicle is released and the vehicle is released, and the dynamic state of the supply 2 is maintained in the brake release pressure chamber 62. On the other hand, when the vehicle is parked and the vehicle is in the case of %, the vehicle is released from the pressure chamber, and the vehicle mechanism indicates that the parking brake mechanism 26 carries the air. Figure η The state of the car. Knowing the operation as a parking brake If the compressed air is discharged from the brake release chamber 62, the force of the spring 57 is applied to urge the vehicle in the forward direction. Then, by the parking, the brake piston 58 is moved by the parking brake to the forward direction X!, and the translation cam 46 biased by the aw plug 58 is moved to X1. If the translation cam 46 is distorted in the forward direction: the combination: the unit 31 and the rod 22 connected to the translation cam 46 enters: the movement is moved away and the wheel exit portion 21 is also moved in the forward direction :: the direction X1 is generated as parking The car power of the car. . If this is the case, the production will be carried out as shown in the figure. If the lion is parked, the ring is used in the county, and the connecting member (4) is used as the state of the vehicle. 5 8 a side and translational 钤 "T-car brake piston 5 8 disc-shaped part of the force, so that the translation of the cam and the force of the lever 23 to stop the car, use the ball to move the direction X2. Then, The position of the disc-shaped portion 58a of the force is not changed. In the state where the lever 22 and the translation cam are moved in the backward direction, the parking lever 22 and the translation cam are released, and the brake output unit 21 is also moved backward. Χ2 moves, the car is sensitive. ",, -} As explained above, 'according to the brake tank farm 2, the rod is placed in the direction of the cylinder axis in the direction of the line forward and backward movement, and the rotary type The actuator 24 is disposed so as to overlap the rod 22 in the red axis direction. Therefore, the arrangement of the (four) 24 and the rod 22 can be made smaller in the radial direction and the axial direction of the cylinder reading 20. Further, in a region secured by the efficiency of the arrangement space of the actuator 24 and the rod 22, the driving force from the rotational direction of the actuator 24 is converted into a linear direction to enhance and act on the rod 22. Force mechanism 25. Then, the brake output is output from the brake output unit that is moved from the lever 22 that has been forced to move. In this way, the efficiency of the arrangement of the movements: 4 and the rods 22 is increased, and the second force is increased, so that the miniaturization is achieved, and the output can be made large by the boosting mechanism. Therefore, according to the embodiment, Provided is a small-sized crucible cylinder device 2 that can increase the braking output portion 21 and the braking force that can be moved from the lever 22 while suppressing agrochemicals. = 'According to the 煞 wheel farm 2, and the actuator with the _ set and the driving force of the linear direction of the actuating benefit is converted into the direction of the woman, and the driving force of the linear direction is increased to the force of the rod. Compared with the device, it is also possible to reduce the weight and size of the parts due to the reduction in the number of parts. 100138610 45 201221394 Further, according to the brake cylinder device 2, the boosting mechanism 25 is provided with a rolling cam 47 disposed between the first cam surface 45a and the second cam surface 53a facing each other, and the first cam surface is provided. The 45a and the second cam face are inclined toward the axial direction of the rod. Therefore, the rod 22 can be configured to follow the output shaft 33 of the actuator 24 in a simple configuration; the crucible is rotated by the rolling of the rolling cam 47 in the forward direction X1. Then, the driving force of the actuator 24 can be efficiently converted from the rotation direction to the forward direction X1 ° between the square rotation cam 45 and the translation cam 47 and can be set by the radial direction of the body 2G ( The arrangement of the actuator 24, the i-th cam surface 45a, the second cam surface ^, and the rolling cam 47 in the radial direction of the rod 22 easily adjusts the ratio of the boosting force. Further, according to the secreting device 2, the first cam surface and the second cam surface 53a are disposed obliquely to the axial direction of the crucible 22, and a conical rolling cam 47 is disposed between them. Therefore, compared with the case where the rolling cam 47 is set as the spherical spherical cam, the contact surface pressure of the one rolling cam 47 can be lowered. Further, regarding the advance stroke (progress) when the lever 22 is moved in the forward direction XI via the rolling cam 47 in association with the rotation of the rotary cam plate, the stroke is advanced before the rotation amount of the rotary cam 45 can be made larger. In the case where the spherical cam is used as the rolling cam 47, a large diameter is originally required. However, if the prodigal cam 47 is used, the enlargement is not performed, and the first cam which is inclined to the axial direction of the rod 22 can be formed. The slope of the inclination of the surface W and the second cam surface 53a is set to a slope of more _. Therefore, it is possible to efficiently and efficiently ensure the forward stroke while suppressing the enlargement of the vehicle red device 2 by the high-efficiency of the 100138610 46 201221394. Further, according to the brake cylinder device 2, a simple configuration in which the guide walls (45c, 53b) are provided in the outer peripheral portion of the rotary cam 45 and the translation cam 46 can be used to guide the rolling direction of the roller cam 47. Further, since the rolling of the roller cam 47 is guided by the guide walls (45c, 53b), the structure of the roller cam 47 that is rotatably supported (in the present embodiment, the holder 48) can also be used. The composition is simplified. This makes it possible to further reduce the size and weight of the device. Further, according to the present embodiment, the parking brake mechanism 26 can be grouped in the brake cylinder device 2, and the parking brake mechanism 26 is provided with a parking brake spring 57 that generates a braking force for parking the vehicle, and a spring for parking the brake. The parking brake piston 58 that biases the lever via the translation cam 46 and the brake release brake chamber 62 for releasing the parking brake are applied. Further, since the % of the brakes that move in parallel with the moving direction of the rod 22 are disposed so as to surround the shafts of the rods 22 and the translation cams 46, the arrangement space of the pistons 58 for parking the brakes can also be performed. In the direction of the efficiency of the cylinder axis, the second parking mechanism 26, the cylinder 奘罟 7 丨 罝 罝 欢 欢 欢 欢 欢 欢 欢 欢 欢 欢 欢 欢 欢 欢 欢 欢 。 。 。 。 。 。 。 。 。 。 In addition, according to the brake device 2, there is a case where the cam is placed, and the seven-fourth (four) μ-force of the Japanese-made force mechanism is used to hold the force. Therefore, even if the parking brake machine _ transporting the cam 46 is biased toward the forward direction χ1, The Japanese singer only applies the force of the retainer to the roller cam 45 on the side of the rotating cam 45 to apply 100138610 201221394 force to the roller. 47 remains in the established position. Thereby, the position of the roller cam 47 can be maintained during the operation of the parking brake mechanism 26 by a simple configuration in which the retainer biasing spring 49 is provided. Further, according to the brake cylinder device 2, the actuator 24 is externally fixed to the casing 32 of the cylinder body 20, the output shaft 33 that rotates in the casing 32, and the extension from the output shaft 33 and the compartment actuator The two blades (34, 35) of the pressure chambers (42a, 42b, 43a, 43b) are configured. Therefore, the rotary actuator 24 disposed to overlap the rod 22 in the cylinder axis direction can be compactly formed. Further, according to the brake cylinder device 2, the parking brake spring 57 and the parking brake piston 58 and the blades (34, 35) of the actuator 24 are arranged to overlap each other in the direction parallel to the axial direction of the rod 22. Therefore, the parking brake mechanism 26 in the form of a spring brake, the rotary actuator 24 of the blade type, and the arrangement space of the boosting mechanism 25 having the rotary cam 45 and the rolling cam 47 can be efficiently disposed in the radial direction of the cylinder body 20. Become smaller. Further, by utilizing the relationship with the arrangement space of the parking brake mechanism 26 that is efficiently disposed, the radial space of the cylinder body 20 can be utilized more effectively, and the diameter and rolling of the rotary cam μ can be efficiently set. The number of cams 47 and the angle of rotation of the actuator 24 optimize the composition of the mechanism 25. In other words, the cam surface (45a, 53a) can be set such that the diameter of the rotary cam β and the number of the rolling cams 47 are optimized, and the load acting on each of the rolling cams 47 is sufficiently reduced, and the stroke in the forward direction can be sufficiently ensured. The inclination of the actuator 24 < rotation angle is optimized. 100138610 48 201221394 Further, according to the brake cylinder device 2, the rotary cam 45 and the output shaft 33 provided with the vanes (34, 35) can be easily assembled by fitting the projection 33a into the recess 45b, and The urging force of the force spring 23 urges the rotating cam 45 along the output shaft 33 to fasten the rotating cam 45 and the output shaft 33. Therefore, the rotating cam 45 of the boosting mechanism 25 and the output shaft 33 of the actuator 24 can be fastened by a simple structure and can be easily assembled. Further, according to the brake cylinder device 2, the rotary cam 45 can be fastened to the output shaft 33 by the force applied to the rotary cam 45 by the urging force of the lever biasing spring 23, and can be biased by the retainer. The spring 49 biases the retainer 48 toward the rotating cam 45. Therefore, even when the parking brake mechanism 26 is operated and only the translation cam 46 is biased in the forward direction XI, it is possible to apply the force spring 49 in addition to the lever spring 23 and by the provision of the retainer. The configuration maintains the position of the roller cam 47. Further, the brake cylinder device 2 is configured such that one of the high pressure side actuator pressure chambers 42a and the other high pressure side are formed via the communication holes 44 provided in the output shaft 33 and the vanes (34, 35). The actuator pressure 43a is in communication. Therefore, the actuator pressure chambers (42a, 43a) on both sides of the high pressure side can be operated at the same timing only by supplying the compressed air to the actuator pressure chamber 42a on the high pressure side. Further, the thickness of the casing 32 can be made thinner than in the case where the communication hole 44 of the actuator pressure chambers (42a, 43a) on the high pressure side of one of the other sides is provided in the casing 32. Therefore, the miniaturization of the actuator 24 can be achieved, whereby the further miniaturization of the brake cylinder device 2 can be achieved. 100138610 49 201221394 Further, according to the brake cylinder device 2, the guide portion 55a as a hole can be provided by the cylindrical guide member 50 as fixed around the shaft of the cylinder body 2 and surrounding the rod 22, and the translation cam 46 The structure of the roller body 51 is rotatably provided, and the structure in which the translation cam 46 is stopped is easily constructed. Further, according to the brake cylinder device 2, the high-pressure side and the low-pressure side can be separated from the blades (34, 35) by fitting the both ends into the cylindrical guide member 50 and the pin member 39 of the case 32. The partitioning blocks (36, 37) of the actuator pressure chambers (42a, 43a, 42b, 43b) and the elastomers 38 embedded in the partitioning blocks (36, 37) and the blades (34, 35) abutting Fix in the through state. Therefore, between the cylindrical guiding member 50 and the case 32, the partition block (36, 37) can be separated without using a fastening mechanism fastened by a plurality of members such as bolts and nuts. The elastomer 38 is fixed. Thereby, the number of parts can be reduced, and the weight of the brake cylinder device 2 can be reduced. Further, according to the brake cylinder device 2', it is arranged to separate the high pressure side and the low pressure side actuator pressure chamber (42a 43a) from the vanes (34, 35) by the partition block (36, 37). 42b and 43b), the supply and exhaust port % for supplying and discharging the external air to the actuator pressure chambers (42b, 43b) on the low pressure side can be communicated with the spring chamber 60 in which the parking brake spring 57 is disposed. Therefore, it is possible to construct the actuator pressure chambers (42b, 43b) of the respective low pressure sides by simply providing a vent which connects the spring chamber to the outside by the simple structure of the tank body. The composition of external connectivity. Moreover, according to the present embodiment, it is possible to provide a small disc brake device 1 which can increase the braking force while suppressing the large size of the apparatus 100138610 50 201221394. The above description of the embodiments of the present invention has been made, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the invention. For example, the following modifications can be implemented. (1) In the above embodiment, the actuator that has been operated by the pressure fluid has been described as an example. However, the present invention is not limited to this embodiment, and a rotary type in which various forms are provided may be implemented. Or the brake cylinder device of the swing type actuator. For example, a brake cylinder device having an actuator having an electric motor or an actuator having a hydraulic motor or the like may be provided. (2) In the above embodiment, the rotary actuator has been described as an example. However, the brake cylinder device provided with the swing type instead of the rotary actuator may be implemented. Further, in the above-described embodiment, the blade type actuator has been described as an example of an actuator having two blades, but this may not be the case, and one blade or three may be provided. The brake cylinder device of the actuator of the blade above the blade. Further, in the case of an actuator in which one output arm is provided with a suspension arm blade, it may be defined as either a rotary type actuator or a swing type actuator. (3) In the above embodiment, the case where the rotation angle of the rotary actuator is 90 degrees is exemplified, but the rotation angle may be set to be less than 90 degrees. Actuator, or brake cylinder device for actuators with a 90 degree rotation angle. Further, in this case, a brake cylinder device provided with an actuator that rotates 360 degrees or more can also be implemented. 100138610 51 201221394 (4) Regarding the boosting mechanism, various forms can be changed. " In the state exemplified in the above embodiment, it has been implemented by using a shovel. In addition, although the above embodiment is described in the above-described embodiment, it may not be the case. As a form of a rolling cam, the opening of the rolling cam of the goal surface cam may be used as a spherical shape and a second cam surface. It can be composed of ^4. In this case, the shape of the first cam surface and the shape of the Cameron cam with respect to the rod is formed as a curved surface with respect to the arrangement of the rolling cam or the inclined surface of the inclined surface. Further, in the above (4), the 'village' is carried out in each of the above-described embodiments (4), and is implemented in the above-described embodiment. In the case of the product, the first cam surface and the second cam surface are both set to be the same as the shape of the dry (axial tilt). At least one of the cam surface and the second cam surface may be disposed to be inclined with respect to the axial direction of the rod. (7) In the above embodiment, the form of the guide wall in which the rolling direction of the material roller cam is provided in the outer peripheral portion of both the rotary cam and the translational cam is exemplified as an example, but it may be scaled. For example, the outer peripheral portion of one of the rotary cam and the translation cam may be provided with a guide wall for guiding the rolling direction of the roller cam. (6) In the above embodiment, the configuration in which the projection is provided on the output shaft ′ and the recessed portion in which the projection is fitted is provided in the rotary cam has been described as an example. However, this is not the case. Alternatively, the protrusion may be provided on the rotating cam, and the recess may be provided in the form of the output shaft. 10013S610 52 201221394 (7) The configuration for connecting the translation cam and the lever is not limited to the embodiment illustrated in the above embodiment, and various modifications can be made and implemented. Further, the configuration of the connecting rod and the brake output portion is not limited to the embodiment illustrated in the above embodiment, and various modifications can be made and implemented. (Industrial Applicability) The present invention can be widely applied to a brake cylinder device that outputs a brake force by advancing a lever from a cylinder body, and a disk brake device including the brake cylinder device. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a side view of a disc brake device according to an embodiment of the present invention. Figure 2 is a plan view of the disc brake device of Figure 1. Fig. 3 is a perspective view of a brake cylinder device according to an embodiment of the present invention, and shows a schematic view of the internal structure by a slit cross section. Figure 4 is a cross-sectional view of the brake cylinder device shown in Figure 3. Figure 5 is a cross-sectional view showing the position of the arrow line of the A-A line of the brake cylinder device shown in Figure 4. Figure 6 is a cross-sectional view showing the position of the B-B line of the brake cylinder device shown in Figure 4. Fig. 7 is an exploded perspective view showing the actuator and the boosting mechanism of the brake cylinder device shown in Fig. 3. Figure 8 is a perspective view showing a portion of the actuator shown in Figure 7. Figure 9 is a perspective view showing the output shaft and the blade of the actuator shown in Figure 7. Figure 10 is a perspective view of the rotating cam of the boosting mechanism shown in Figure 7, and a perspective view showing the rotating cam in the opposite direction. Figure 11 is a perspective view showing the hand-moving cam of the non-energizing mechanism of Figure 7. 100138610 53 201221394 Fig. 12 is a perspective view showing the roller cam and the retainer of the boosting mechanism shown in Fig. 7. Fig. 13 is a perspective view showing the cylindrical guiding member of the boosting mechanism shown in Fig. 7. Fig. 3 is a perspective view for explaining the operation of the brake cylinder device shown in Fig. 3, and shows a schematic view of the internal structure by a slit section. Figure 15 is a perspective view for explaining the operation of the brake device shown in Figure 3, and showing a schematic view of the internal structure by a slit section. Fig. 16 is a perspective view for explaining the operation of the brake cylinder of Fig. 3, and shows a schematic view of the internal structure by a slit section. Figure 17 is a perspective view for explaining the operation of the brake cylinder device shown in Figure 3, and shows a schematic view of the internal structure in a slit section. Figure 18 is a perspective view for explaining the operation of the brake red device shown in Figure 3, and showing a schematic view of the internal structure by a slit cross section. [Main component symbol description] 1 2 11 12 12a 13 14 14a Disc brake device 煞 Cylinder device caliper body Back plate support pin 煞 Car piece coupling member Swing pin 100138610 54 201221394 15 Brake lever 15a Pendant pin 15b Cylinder support pin 20 Cylinder body 20a First tubular portion 20b Second tubular portion 21 Brake output portion 22 Rod 22a Step 23 Rod biasing spring 24 Actuator 25 Force boosting mechanism 26 Parking brake mechanism 27a Cylindrical portion 27b Flange portion 28 Screw shaft 29 30 bolt 31 clutch unit 32 housing 32a air supply port 33 output shaft 33a projection 100138610 55 201221394 34, 35 blades 34a, 34b, 35a, 35b plate-like bodies 34c, 35c, 36c, 37c sealing members 36, 37 Block block 36a, 37a 1st block 36b' 37b 2nd block 38 Elastomer 39 Pin member 40 Sleeve 41 Bearings 42a, 42b, 43a, 43b Actuator pressure chamber 44 Connecting holes 44a, 44b Opening. 45 Rotation Cam 45a first cam surface 45b recess 45c' 53b guide wall 46 translation cam 47 rolling cam 47a rolling surface 48 holder 48a rotating shaft portion 1001 38610 56 201221394 48b inner flange portion 49 retainer biasing spring 50 cylindrical guide member 51 roller body 52 small-diameter cylindrical portion 53 large-diameter annular portion 53a second cam surface 54 ring member 55 small-diameter cylindrical portion 55a Guide portion 56 Large diameter annular portion 57 Parking brake spring 58 Parking brake piston 58a Disc portion 58b Cylindrical projection 58c Translation cam coupling portion 59 Venting port 60 Magazine chamber 61 Vent port facing region 62 Brake release pressure chamber 63 Connecting member 64 Ring 100138610 57 201221394 65 Release parking brake operation ring 100 Vehicle body 100a Bracket 101 Brake disc 101a Brake surface AA section, upper line BB Section line P Center axis XI Forward direction X2 Back direction 100138610 58