TW201812198A - Damping valve and cylinder device - Google Patents

Damping valve and cylinder device Download PDF

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Publication number
TW201812198A
TW201812198A TW106130568A TW106130568A TW201812198A TW 201812198 A TW201812198 A TW 201812198A TW 106130568 A TW106130568 A TW 106130568A TW 106130568 A TW106130568 A TW 106130568A TW 201812198 A TW201812198 A TW 201812198A
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Taiwan
Prior art keywords
valve
path
bushing
fail
side chamber
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TW106130568A
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Chinese (zh)
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小川義博
鳥海拓
村田充
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日商Ｋｙｂ股份有限公司
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Publication of TW201812198A publication Critical patent/TW201812198A/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/06—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/10—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with auxiliary valve for fluid operation of the main valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid

Landscapes

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

Abstract

This damping valve (DV) comprises: a damping force adjusting path (TP) and a fail path (FP) that are arranged in parallel; a downstream path (DP) that is connected to the damping force adjusting path (TP) and the fail path (FP) on the downstream side thereof; a relief valve (RV) that is provided in the damping force adjusting path (TP); a normally opened opening-and-closing valve (OV) that is provided in the fail path (FP); a solenoid (Sol) that adjusts the open valve pressure of the relief valve (RV) and closes the opening-and-closing valve (OV) when energized; and an orifice (O) that is provided in the downstream path (DP).

Description

衰減閥及壓缸裝置Attenuation valve and pressure cylinder device

本發明，是關於衰減閥及壓缸裝置。The present invention relates to a damping valve and a cylinder device.

作為可調整衰減力之衰減閥者，已有例如揭示於JP2001-074154A，具備有：於殼體內作為釋放閥發揮功能之筒狀的閥座體、及自由滑動地***於閥座體內之閥體與切換閥、及使閥體朝向閥座體側施力之彈簧、以及對閥體與切換閥賦予推力之比例電磁線圈者。 　　該切換閥，係可開閉流路，並藉由比例電磁線圈可以將切換閥切換成開狀態或閉狀態，透過切換閥使比例電磁線圈的推力作用於閥體，來調節閥體從閥座離開的開閥壓。 　　並且，該衰減閥，係使用在抑制鐵路車輛的車體振動之阻尼器，設置於連通阻尼器的桿側室與貯油器之衰減力控制迴路的半途中，藉由比例電磁線圈控制前述的開閥壓，調整阻尼器所產生之衰減力。As a damping valve whose damping force can be adjusted, for example, it has been disclosed in JP2001-074154A and includes a cylindrical valve seat body functioning as a release valve in a housing, and a valve body slidably inserted into the valve seat body. Those with a switching valve, a spring that biases the valve body toward the valve seat body side, and a proportional solenoid that applies thrust to the valve body and the switching valve. The switching valve can open and close the flow path, and the switching valve can be switched to an open state or a closed state by the proportional solenoid. The switching valve is used to apply the thrust of the proportional solenoid to the valve body to adjust the valve body to leave the valve seat. Valve opening pressure. In addition, the damping valve is a damper for suppressing the vibration of the vehicle body of a railway vehicle. The damping valve is installed halfway through the damping force control circuit connecting the damper's rod chamber and the oil reservoir, and the aforementioned solenoid valve is controlled by a proportional solenoid Pressure to adjust the damping force generated by the damper.

[發明所要解決的問題] 　　於該以往之衰減閥，是以釋放閥控制衰減力，不過於開閥時，因桿側室的壓力變動等，閥體會有易於造成因高頻振動而產生振動的傾向。 　　當閥體產生振動時，於阻尼器所產生之衰減力的波形會造成紊亂，不僅藉由衰減力調整來進行車體減振控制時的控制性會惡化，再者起因於衰減力的驟變而產生異狀聲音，會有造成對在車體內知覺到異狀聲音的乘客給予不舒服感受的可能性。 [用以解決問題之手段] 　　在此，本發明，是為了改善上述缺失所研創提案的，其目的在於提供一種可以防止衰減閥的振動產生，在衰減力波形上不會產生紊亂的衰減閥以及應用此種衰減閥的壓缸裝置。 　　於本發明之衰減閥，具備有：並聯設置之衰減力調整通路與故障安全通路、及連接於衰減力調整通路與故障安全通路之下游的下游通路、及設置於衰減力調整通路的釋放閥、及設置於故障安全通路之常開型開閉閥、及在通電時調節釋放閥的開閥壓同時關閉開閉閥的電磁線圈、以及設置於下游通路的孔口。[Problems to be Solved by the Invention] The conventional damping valve uses a release valve to control the damping force. However, when the valve is opened, the valve body tends to cause vibration due to high-frequency vibration due to pressure fluctuations in the rod-side chamber. . When the valve body vibrates, the waveform of the damping force generated by the damper will cause chaos. Not only the controllability of the vehicle body vibration damping control will be deteriorated by the damping force adjustment, but also due to the sudden change of the damping force The generation of strange sounds may cause uncomfortable feelings to passengers who feel the strange sounds in the vehicle body. [Means to Solve the Problem] Here, the present invention was made to improve the above-mentioned deficiencies. The purpose of the present invention is to provide a damping valve that can prevent the damping valve from vibrating and that does not cause a disorder on the damping force waveform. Cylinder device using this damping valve. The damping valve of the present invention includes a damping force adjustment path and a fail-safe path provided in parallel, a downstream path connected downstream of the damping force adjustment path and the fail-safe path, and a release valve provided in the damping force adjustment path. And a normally-open type on-off valve provided in the fail-safe path, an electromagnetic coil that regulates the opening pressure of the release valve while closing the on-off valve while energizing, and an orifice provided in the downstream path.

以下，根據圖示之實施形態，說明本發明。一實施形態之衰減閥DV，基本上，如第1圖所示，為具備有：並聯設置之衰減力調整通路TP與故障安全通路FP、及連接於衰減力調整通路TP與故障安全通路FP之下游的下游通路DP、及設置於衰減力調整通路TP的釋放閥RV、及設置於故障安全通路FP之常開型開閉閥OV、及在通電時調節釋放閥RV的開閥壓同時關閉開閉閥OV的電磁線圈Sol、以及設置於下游通路DP的孔口(orifice)O而構成，在本例中，是應用於壓缸裝置C。 　　壓缸裝置C，具備有：壓缸1、及自由滑動地***於壓缸1內之活塞2、及***於壓缸1內且連結於活塞2的桿3、及於壓缸1內藉由活塞2劃分之桿側室4與活塞側室5、及儲槽6、及設置於連通桿側室4與活塞側室5之第一通路7的半途中的第一卸載閥8、及設置於連通活塞側室5與儲槽6之第二通路9的半途中之第二卸載閥10、及僅容許從活塞側室5朝向桿側室4流動的整流通路11、及僅容許從儲槽6朝向活塞側室5流動的吸入通路12、以及衰減閥DV，其作為所謂單桿型的壓缸裝置而構成。衰減閥DV，是設置於位在壓缸裝置C之桿側室4與儲槽6之間，對從壓缸1內朝向儲槽6排出之液體的流動給予抵抗。 　　又，於桿側室4與活塞側室5充填有作為液體的作動油，並且，於儲槽6，除了作動油還充填有氣體。又，儲槽6內，並無特別需要將氣體壓縮充填作成加壓狀態。又，壓缸裝置C，其裝在介於台車與車體之間，雖圖面上無顯示，不過桿3是連結於鐵路車輛的台車及車體的一方，而壓缸1是連結於台車及車體的另一方。又，壓缸裝置C，因被設定為單桿型，故與雙桿型的壓缸裝置作比較，易於確保衝程長，可使壓缸裝置C的全長縮短，以提升對鐵路車輛的搭載性。又，作為壓缸裝置C之工作介質的液體，在本例中為作動油，不過根據壓缸裝置C的使用環境可為水或水溶液等，亦可利用其他的液體。 　　以下，詳細說明關於衰減閥DV及壓缸裝置C的各部位。壓缸1為筒狀，該第1圖中之右端為被蓋13封閉，於第1圖中之左端安裝有環狀的桿導14。又，於上述桿導14內，***有可自由滑動的桿3；上述桿3可自由移動地***於壓缸1內。該桿3，其一端朝向壓缸1外突出，其壓缸1內的另一端連結於活塞2；上述活塞2可自由滑動地***於壓缸1內。 　　又，桿導14的外周與壓缸1之間是藉由圖示省略之密封構件而密封，藉此壓缸1內維持密閉狀態。而，於壓缸1內藉由活塞2所劃分之桿側室4與活塞側室5，如前述般充填有作為液體的作動油。 　　又，於該壓缸裝置C之場合，將桿3的斷面積作成活塞2的斷面積的二分之一，使活塞2的桿側室4側的受壓面積成為活塞側室5側的受壓面積的二分之一，壓缸裝置C在伸長時與在縮短時，從壓缸1內通過衰減閥DV朝向儲槽6排出的流量為相等。 　　回到圖面，於桿3的第1圖中之左端及封閉壓缸1的右端之蓋13，具備有圖面上無顯示之安裝部，用以將該壓缸裝置C裝設在介於鐵路車輛之車體與台車之間的位置。 　　並且，對於本例之壓缸裝置C，桿側室4與活塞側室5是藉由第一通路7而連通，於該第一通路7的半途中，設置有第一卸載閥8。該第一通路7，於壓缸1外連通桿側室4與活塞側室5，不過亦可設置於活塞2。 　　第一卸載閥8，係設成電磁開閉閥，具備有：連通桿側室4與活塞側室5之連通位置、以及阻絕連通桿側室4與活塞側室5的阻斷位置，於通電時是開放第一通路7而將桿側室4與活塞側室5連通。 　　又，對於本例之壓缸裝置C，活塞側室5及儲槽6是藉由第二通路9而連通，於該第二通路9的半途中，設置有第二卸載閥10。第二卸載閥10，係設成電磁開閉閥，具備有：連通活塞側室5與儲槽6之連通位置、以及阻絕活塞側室5與儲槽6的連通之阻斷位置，於通電時是開放第二通路9而將活塞側室5與儲槽6連通。 　　又，如第1圖所示，本例之壓缸裝置C，具備有僅容許從活塞側室5朝向桿側室4流動的整流通路11。又，整流通路11，亦可設置在活塞2以外之處。再者，本例之壓缸裝置C，具備有僅容許從儲槽6朝向活塞側室5流動的吸入通路12。 　　因此，對於該本例之壓缸裝置C，第一卸載閥8及第二卸載閥10採取位在阻斷位置時，當受到外力伸長時，作動油會從被壓縮之桿側室4透過衰減閥DV朝向儲槽6被壓出，而於擴大之活塞側室5則是透過吸入通路12從儲槽6供給作動油。因此，於該伸長作動時，壓缸裝置C，係藉由衰減閥DV對通過之作動油的流動給予抵抗，使桿側室4內的壓力上昇而發揮對抗伸長的衰減力。又，於該情形下，通過衰減閥DV之作動油的流量，會是從活塞2的斷面積減掉桿3的斷面積的值再乘以活塞2的移動量之量。 　　相反的，第一卸載閥8及第二卸載閥10採取位在阻斷位置時，當壓缸裝置C受到外力縮短時，作動油經由整流通路11從被壓縮之活塞側室5朝向桿側室4移動。又，壓缸裝置C在縮短時，由於桿3侵入於壓缸1內，故桿3侵入於壓缸1內之體積份量的作動油在壓缸1內成為過剩而透過衰減閥DV朝向儲槽6排出。於該縮短動作時，壓缸裝置C，係藉由衰減閥DV對通過之作動油的流動給予抵抗，使壓缸1內的壓力上昇而發揮對抗縮短的衰減力。又，於該情形下，通過衰減閥DV之作動油量，是桿3的斷面積乘以活塞2的移動量之量。在此，桿3的斷面積，因設定為活塞2的斷面積的二分之一，故壓缸裝置C不論伸長或收縮，只要活塞2的移動量相同的話，則通過衰減閥DV之作動油量就會相等。因此，壓缸裝置C，係只要活塞2的移動速度在伸縮兩側為相同，則可發揮相等的衰減力。 　　又，第一卸載閥8與第二卸載閥10皆是於非通電時採取位在阻斷位置，故於電力無法供給之失能時，本例之壓缸裝置C，由於如前述般地對於伸縮必定可發揮衰減力，故可作為被動阻尼器發揮功能。 　　又，於本例之壓缸裝置C，在將第一卸載閥8位於連通位置而將第二卸載閥10位於阻斷位置之情形時，桿側室4與活塞側室5經由第一通路7而連通，但活塞側室5與儲槽6的連通被阻斷。於該狀態下，壓缸裝置C受到外力收縮時，桿3侵入於壓缸1內之體積份的作動油會被從壓缸1朝向衰減閥DV排出，與上述同樣地發揮對抗收縮之衰減力。另一方，於該狀態下，若壓缸裝置C伸長時，作動油經由第一通路7從縮小之桿側室4朝向擴大之活塞側室5移動，桿3從壓缸1退出之體積份的作動油會經由吸入通路12從儲槽6朝向壓缸1內被供給。因此，於該場合，作動油不會朝衰減閥DV流動，故壓缸裝置C不會發揮衰減力。 　　再者，於本例之壓缸裝置C，在將第一卸載閥8位於阻斷位置並將第二卸載閥10位於連通位置時，桿側室4與活塞側室5的連通被阻斷，不過活塞側室5及儲槽6經由第二通路9被連通。於該狀態下，壓缸裝置C受到外力伸長時，伴隨桿側室4的縮小，作動油被從桿側室4朝向衰減閥DV排出，與上述同樣地發揮對抗伸長之衰減力。另一方，於該狀態下，若壓缸裝置C收縮，則作動油會經由整流通路11從縮小之活塞側室5朝向擴大之桿側室4移動，桿3朝向壓缸1內侵入之體積份的作動油會經由第二通路9被從活塞側室5朝向儲槽6內排出。因此，於此情形下，由於作動油不會朝衰減閥DV流動，故壓缸裝置C不會發揮衰減力。如此地，於該壓缸裝置C，可以作為選擇伸長或收縮的任一方來發揮衰減力之單效阻尼器之功能。 　　又，該壓缸裝置C之場合，以使混入於壓缸1內之空氣可從桿側室4朝向儲槽6排出之方式設置有除氣用孔口15。 　　接著，衰減閥DV，如第1圖所示，為具備有：並聯設置之衰減力調整通路TP與故障安全通路FP、及下游通路DP、及釋放閥RV、及開閉閥OV、及電磁線圈Sol、以及設置於下游通路DP的孔口O而構成。於本例中，衰減閥DV，如前述般設置於桿側室4與儲槽6之間。具體上，並聯設置之衰減力調整通路TP與故障安全通路FP為連接於桿側室4與下游通路DP。下游通路DP，其一端連接於衰減力調整通路TP與故障安全通路FP，另一端連接於儲槽6。因此，桿側室4與儲槽6，為經由衰減力調整通路TP、故障安全通路FP以及下游通路DP而連通。 　　釋放閥RV，是設置於衰減力調整通路TP，開閉閥OV，是設置於故障安全通路FP。開閉閥OV，係藉由彈簧施力而開閥，且於受到來自電磁線圈Sol的推力時，成為閉閥之電磁閥。又，開閉閥OV，於電磁線圈Sol非通電時，藉由彈簧被施力而將故障安全通路FP連通，於對電磁線圈Sol供給特定量的電流時，則成為將故障安全通路FP阻斷之常開型開閉閥。 　　釋放閥RV，是經由開閉閥OV而藉由來自電磁線圈Sol的推力所驅動，於電磁線圈Sol非通電時，藉由彈簧被施力，使開閥壓成為最大。又，對電磁線圈Sol通電而使開閉閥OV位於阻斷位置時，電磁線圈Sol的推力會經由開閉閥OV來對釋放閥RV發揮作為對抗上述彈簧之力的作用。因此，若對電磁線圈Sol通電，則對應通電量，可調整釋放閥RV的開閥壓，通電量變大時，釋放閥RV的開閥壓會變小，相反的，在沒有對電磁線圈Sol通電的狀態下，釋放閥RV的開閥壓為最大。如此，於本例之衰減閥DV，可藉由同一個電磁線圈Sol就可進行釋放閥RV之開閥壓的調整以及開閉閥OV的開閉。 　　又，在本例中，於故障安全通路FP，設置有故障安全閥FV以及與故障安全閥FV並聯之故障用孔口A。該故障安全閥FV，是在故障安全通路FP藉由開閉閥OV作用而處於連通之狀態下，上游側的壓力若來到預定壓力則會開閥，該開閥壓是設定成比釋放閥RV的最大開閥壓還小之值。 　　因此該衰減閥DV，在可以正常發揮功能的正常時，對電磁線圈Sol通電時，可阻斷開閉閥OV來調節釋放閥RV的開閥壓，而可以控制壓缸裝置C進行伸縮時之桿側室4內的壓力。於下游通路DP的半途中，設置有孔口O，孔口O是用以對作動油的流動給予抵抗。因此，由釋放閥RV進行控制之桿側室4的壓力，是孔口O的抵抗壓力成分作為過載(override)而加疊於釋放閥RV的開閥壓。然而，起因於孔口O的壓力過載，是有顧慮到不要對釋放閥RV所形成之桿側室4之壓力的控制性會造成重大的影響。 　　衰減閥DV，如上述般地構成，於壓缸裝置C進行伸長時，因應給予電磁線圈Sol的電流量來調節釋放閥RV的開閥壓，藉此桿側室4內的壓力受到控制，而使抑制壓缸裝置C所產生之伸長的衰減力受到控制。又，於壓缸裝置C進行收縮時，因應給予電磁線圈Sol的電流量來調節釋放閥RV的開閥壓，藉此桿側室4及桿側室4內的壓力受到控制，而使抑制壓缸裝置C所產生之收縮的衰減力受到控制。 　　又，在不能對電磁線圈Sol通電之故障時(非正常時)，開閉閥OV為開閥而連通故障安全通路FP，使故障安全閥FV發揮功效，藉由故障安全閥FV及孔口O，發揮壓缸裝置C在伸縮時的衰減力。 　　因此，具備有本例之衰減閥DV的壓缸裝置C在正常時的衰減力特性，是在活塞速度於低速區域之情況時，如第2圖中線a所示，顯示除氣用孔口15的平方特性，而當活塞速度上升而釋放閥RV開閥時，則如第2圖中之線b所示，顯現出對釋放閥RV的開閥壓，疊加有作為孔口O之壓力損失成分之過載的特性。又，孔口O的過載，由於是隨著活塞速度越高速而變得越大，故會有釋放閥RV開閥後，對應活塞速度的上升而衰減係數慢慢變大的特性。又，前述的衰減力特性是在沒有變更釋放閥RV的開閥壓之情形下的特性，藉由釋放閥RV之開閥壓的調節，可以調節壓缸裝置C之衰減力的高低。 　　而且，如此所構成之壓缸裝置C，在將第一卸載閥8及第二卸載閥10作為位於阻斷位置時，當受外力而伸縮時，作動油會經由釋放閥RV及孔口O而從壓缸1內朝向儲槽6排出。而且，當調節對開閉閥OV供給之通電量來調節釋放閥RV的開閥壓時，則可調節壓缸裝置C所產生之衰減力。因此，於正常時將第一卸載閥8及第二卸載閥10作為位於阻斷位置時，壓缸裝置C，是可以發揮作為在伸縮兩側可調整衰減力的阻尼器之功能。 　　又，於將第一卸載閥8作為位於連通位置並將第二卸載閥10作為位於阻斷位置之情形，以及將第一卸載閥8作為位於阻斷位置並將第二卸載閥10作為位於連通位置之情形時，如前述般地，是成為壓缸裝置C僅對於伸長或收縮之任一方發揮衰減力之模式。因此，例如，若選擇此種模式的話，發揮衰減力的方向會成為由鐵路車輛之台車的振動造成對車體加振之方向的情形時，可將壓缸裝置C作為單效的阻尼器來使衰減力不會形成在如此的方向上。因此，該壓缸裝置C，在正常時，可以容易實現依據卡諾普(Karnopp)理論的半主動控制，可發揮作為半主動阻尼器的功能。 　　另一方面，在因某種理由中斷了對壓缸裝置C供給電力的故障時，第一卸載閥8及第二卸載閥10會採取位在阻斷位置，如前述般地，壓缸裝置C會發揮作為被動阻尼器之功能。於該狀態下，若壓缸裝置C伸縮，則作動油必定會從壓缸1內排出。此時，由於開閉閥OV為開閥，故被排出的作動油會通過故障安全閥FV、故障用孔口A以及孔口O朝向儲槽6流入。因此，在該故障時，故障安全閥FV、故障用孔口A以及孔口O會對作動油的流動給予抵抗，壓缸裝置C會發揮衰減力。又，當壓缸裝置C的伸縮速度為高速，桿側室4的壓力超過釋放閥RV的開閥壓時，釋放閥RV也會開閥而容許作動油的通過。 　　如此地，壓缸裝置C，在正常時可以發揮作為可調整衰減力之雙效的阻尼器或單效的半主動阻尼器之功能，在故障時可以發揮作為被動阻尼器之功能。 　　而且，對於本發明之衰減閥DV，是於釋放閥RV的下游設有孔口O。孔口O，是在欲通過孔口O之作動油的流量因高頻而變動時，具備有妨礙作動油的流量變化的特性。在此，釋放閥RV的閥體急遽開閉動作時，由於欲通過下游的孔口O之作動油的流量會因高頻而振動性地變化，故可發揮抑制孔口O流量的變動之功能。而於釋放閥RV打開時，作用於釋放閥RV的閥體之背壓會增加，相反地，於釋放閥RV關閉之場合，作用於釋放閥RV的閥體之背壓會減少，以妨礙釋放閥RV的急遽開閉。如此，孔口O，會呈現妨礙釋放閥RV的閥體的急遽開閉動作而使動作緩慢之阻尼作用。因此，於本發明之衰減閥DV，在以釋放閥RV來控制壓缸裝置C的衰減力時，即使於桿側室4產生壓力變動，也可藉由孔口O所發揮之阻尼作用來抑制釋放閥RV的高頻振動。因此，根據本發明之衰減閥DV，可抑制釋放閥RV產生震動，不會使壓缸裝置C所產生之衰減力產生波形的紊亂，可以提升因衰減力調整所改善之車體的減震控制的控制性，並避免衰減力的驟變也可以阻止異狀聲音的產生。 　　又，在本例之衰減閥DV中，具備有：於故障安全通路FP中對作動油的流動給予抵抗的故障安全閥FV、以及故障用孔口A。在如此所構成之衰減閥DV中，在中斷了對電磁線圈Sol的電流供給之故障時，不僅孔口O，故障安全閥FV及故障用孔口A也會對作動油的流動給予抵抗。孔口O的特性，雖是被設定成在正常時不會因有效發揮功能的釋放閥RV而形成對控制性造成影響的特性，不過對於故障安全閥FV，是能夠將其特性獨立於其他的閥來加以設定。因此，根據本例之衰減閥DV，可以將故障時的衰減力特性調整成如所期望的特性，而在故障時可以發揮如預期般的衰減力特性。又，於開閉閥OV的連通位置，亦可作成對流動在故障安全通路FP之作動油的流動給予抵抗的方式，將故障安全閥FV的功能統合於開閉閥OV。又，在故障時藉由孔口O發揮衰減力之情形時，亦可以廢止故障安全閥FV。故障安全閥FV，是被作為釋放閥或是調壓閥。又，如第4圖所示，故障安全閥FV，可以作成帶有孔口的釋放閥，也可以將孔口作成不同個體。 　　再者，在本例之壓缸裝置C中，係具備有：藉由活塞2將內部劃分成桿側室4與活塞側室5的壓缸1、及儲槽6、及設置於將桿側室4與活塞側室5連通之第一通路7中的第一卸載閥8、及設置於將活塞側室5與儲槽6連通之第二通路9中的第二卸載閥10、及僅容許從活塞側室5朝向桿側室4流動的整流通路11、及僅容許從儲槽6朝向活塞側室5流動的吸入通路12、以及衰減閥DV。根據如此所構成之壓缸裝置C，在正常時，可發揮作為能夠調整衰減力之雙效的阻尼器或單效的半主動阻尼器之功能，而在故障時可發揮作為被動阻尼器之功能。 　　又，於壓缸裝置C，如第3圖所示，若設置從儲槽6吸入作動油並朝桿側室4供給之泵浦P，則可使壓缸裝置C發揮作為積極伸縮驅動之致動器的功能。又，如此地壓缸裝置C藉由第一卸載閥8及第二卸載閥10之開閉的切換，可發揮作為僅在伸長或收縮時發揮推力之單效的致動阻尼器之功能。因此，在該壓缸裝置C中，對於致動器與半主動阻尼器之狀態的切換，是不用進行泵浦P的停止與驅動的切換。 　　於前述中就原理性說明了衰減閥DV，以下則對於第4圖所示之具備有具體構造的衰減閥DV進行說明。具體的衰減閥DV，如第4圖所示，其構成是具備有：具有中空部21的殼體H、及串聯(直列)排列地***於中空部21之第一襯套22與第二襯套23、及容納於第一襯套22內的第一滑閥24、以及容納於第二襯套23內的第二滑閥25。 　　以下，詳細說明關於衰減閥DV的各部位。首先，殼體H，在本例中，是具備有第一殼體H1、以及裝設於第一殼體H1的側部之第二殼體H2。並且，中空部21，是設置於第一殼體H1，從第一殼體H1的外部開口，此情形時，從第一殼體H1的軸向兩端朝向外部開通。該中空部21，在本例中，為從第一殼體H1的兩端開口，不過亦可從一端側開口來作成袋孔。 　　又，設置於第一殼體H1的中空部21，於第4圖中從右端側依序具備有：裝設有彈簧支承27的彈簧支承裝設部21a、及容納有第一襯套22與第二襯套23的襯套容納部21b、以及裝設有第二襯套23的第二襯套裝設部21c。 　　彈簧支承裝設部21a，於第4圖中，形成於第一殼體H1的右端，於第4圖中之左方設置有螺紋部21d，並將第4圖中之右方的內徑作成比起該螺紋部21d還大口徑，形成中空部21的一部分。 　　襯套容納部21b，係由：在第4圖中之螺紋部21d的左鄰，其內徑形成得比螺紋部21d還大口徑的前端部21e、及在第4圖中之前端部21e的左鄰，其內徑形成得比前端部21e還大口徑的中間部21f、以及在第4圖中之中間部21f的左鄰，其內徑形成得比中間部21f還大口徑的後端部21g所構成，而成為中空部21的一部分。於襯套容納部21b的前端與彈簧支承裝設部21a的後端之間，形成有階段部21h。第二襯套裝設部21c，於第4圖中，是形成在第一殼體H1的左端，成為中空部21的一部分。 　　又，第一殼體H1，在本例中，具備有：從外周側朝向徑向開口且連通於前端部21e之第一通口21i、及從外周側朝向徑向開口並連通於中間部21f之第二通口21j、及從外周側朝向徑向開口並連通於後端部21g之第三通口21k、以及從外周朝向內周開口之第四通口21m。又，於圖面上無顯示，第一通口21i，是連接於位於壓缸裝置C之儲槽6；第二通口21j與第四通口21m，是連接於位於壓缸裝置C之桿側室4。又，於第一殼體H1的第一通口21i的內周裝設有具備有孔口O的插栓50。 　　再者，裝設於第一殼體H1之側部的第二殼體H2，是與第一殼體H1協力形成殼體H。第二殼體H2，具備有：從第4圖中之左端的外側，作為與中空部21並聯地開口之孔的閥孔28、以及從內周開口並通往閥孔28的通路29。又，在本例中，由於藉由從第二殼體H2之第4圖中之右端開口之孔形成通路29的一部分，故該孔之第4圖中之右端開口端是由栓33所閉塞。又，於第二殼體H2，設置有從內周開口並通往閥孔28的第五通口31。 　　將第二殼體H2裝設於第一殼體H1時，是通路29與第二通口21j相向而使此等連通，第五通口31與第三通口21k相向而使此等連通。又，第一殼體H1及第二殼體H2亦可以設成同一零件而不是各別的個體。 　　閥孔28的內徑，是設成比通路29中之往閥孔28連接之開口端的內徑還大口徑，於閥孔28內，是以朝向該通路29之閥孔28的開口端作為閥座34，並容納有可離開與就座於該閥座34的閥體35。再者，於閥孔28內，容納有將閥體35朝向閥座34側施力之彈簧16，並且於閥孔28的左端側螺鎖有作為彈簧支承而發揮功能之蓋體37，來閉塞閥孔28。彈簧16，是以壓縮狀態被夾持在蓋體37與閥體35之間，若調節蓋體37相對於閥孔28的裝設位置，就可調節施力於閥體35之彈簧16的施壓力。而且，故障安全閥FV是藉由此等閥座34、閥體35、彈簧16、以及蓋體37所構成。 　　又，於閥體35，設置有故障用孔口A，該故障用孔口A，是並聯於故障安全閥FV，即使故障安全閥FV為閉閥狀態亦與通路29連通。 　　因此，作動油是透過第四通口21m從外側被導入，當通路29內的壓力超過故障安全閥FV的開閥壓時，則閥體35會從閥座34後退而開閥，以使通路29連通往第五通口31。 　　第一襯套22，係設成使在第4圖中為右端側之前端側的外徑比在第4圖中為左端側之後端側的外徑還小徑之帶有階段的筒狀，於外周具備有排列於軸向所形成之兩個環狀溝槽22a、22b。 　　又，第一襯套22，具備有：設於前端側內周的內周大徑部22c、以及比設於後端側內周之內周大徑部22c還小徑的內周小徑部22d。再者，第一襯套22，具備有：從環狀溝槽22a開口且連通至內周大徑部22c的通孔22e、及從環狀溝槽22b開口且連通至內周小徑部22d的通孔22f、以及從後端開口且開口至形成於內周大徑部22c與內周小徑部22d之間的階段部22g之通孔22h。 　　又，於第一襯套22的外周，亦即於環狀溝槽22a與環狀溝槽22b之間沿著周方向，裝設有密封環38，於比環狀溝槽22b更靠後端側，沿著周方向裝設有密封環39。 　　如此構成之第一襯套22，是從小徑側***於第一殼體H1的中空部21內，小徑部分為嵌合於前端部21e內，大徑部分為嵌合於位於第一殼體H1的中間部21f內，並容納於位於中空部21之襯套容納部21b內。如此一來，密封環38、39緊密接觸於第一殼體H1的襯套容納部21b之內周而將環狀溝槽22a與環狀溝槽22b之間密封。又，環狀溝槽22a，是與設置於第一殼體H1的第一通口21i相向並與之連通，環狀溝槽22b，是與設置於第一殼體H1的第二通口21j相向並與之連通。因此，通路29，是經由第二通口21j、環狀溝槽22b、以及通孔22 f而連通於第一襯套22內。又，第一通口21i，是經由環狀溝槽22a及通孔22e而連通於第一襯套22內，再進一步地連通於第四通口21m。 　　第二襯套23，係設成使在第4圖中為右端側之前端側的外徑比在第4圖中為左端側之後端側的外徑還小徑之帶有階段的筒狀，其具備有：設置於後端側且朝向第4圖中之左方立起之筒狀的套管23a、及設置於套管23a的後端外周的凸緣23b、及設置於小徑部分與大徑部分之間的環狀溝槽23c、以及設置於套管23a的外周之作為固定部的螺紋部23d。 　　又，將第二襯套23作成筒狀，於該內側形成有滑閥孔Sh，於該滑閥孔Sh，設置有在半途中將內周作成大徑的內周大徑部23e。再者，第二襯套23，具備有從環狀溝槽23c開口並連通於內周大徑部23e的通孔23f。又，於第二襯套23的外周，亦即相對於環狀溝槽23c在軸向前後分別沿著圓周方向，裝設有密封環40、41。 　　如此構成之第二襯套23，其凸緣23b為朝向第一殼體H1之在第4圖中為左端面的後端面抵接而決定軸向的位置，並裝設於第一殼體H1的中空部21的開口端。具體上，第二襯套23，係使作為固定部的螺紋部23d螺合於形成在中空部21的第二襯套裝設部21c，而被固定於第一殼體H1。如此一來，第二襯套23，係使其小徑部分被嵌合在第一殼體H1中的中間部21f內，使其大徑部分被嵌合在第一殼體H1中的後端部21g內，而容納於中空部21內。於第二襯套23之在第4圖中的右端，設置有凹部23g，凹部23g，是與朝第一襯套22之在第4圖中為左端的後端開口的通孔22h相向，經由通孔22h連通於第一襯套22內的內周大徑部22c。又，位於凹部23g的內徑，係作成比第一襯套22的外徑還小徑而比第二襯套23的內徑還大徑，第二襯套23之在第4圖中為右端的端面是與第一襯套22的後端面相向。因此，第二襯套23，當裝設於第一殼體H1時，可發揮作為容納於中空部21內之第一襯套22的防脫功能。 　　第二襯套23如上述般地容納於中空部21內時，密封環40、41緊密接觸於第一殼體H1之襯套容納部21b的內周，環狀溝槽23c藉由第二襯套23的外周而沒有連通於他處。又，環狀溝槽23c，是與設置於第一殼體H1的第三通口21k相向並與之連通。因此，第二殼體H2的第五通口31，為經由第三通口21k、環狀溝槽23c、以及通孔23f而連通於第二襯套23內。 　　又，凸緣23b，係塞住作為孔的閥孔28之在第1圖中為左端的開口端的一部分，藉此可阻止裝設於閥孔28的蓋體37從第二殼體H2脫落。因此，設置於第二殼體H2的故障安全閥FV不會有從第二殼體H2脫離的虞慮。 　　又，在本例中，在第二襯套23被裝設於第一殼體H1並被定位在軸向位置的狀態下，第一襯套22之軸向的長度，係設定成比從第二襯套23之在第4圖中為右端的端面至中空部21內的階段部21h之軸向的長度還短。因此，即使將第二襯套23裝設於第一殼體H1，第一襯套22也不會被第二襯套23與階段部21h夾持在壓縮狀態下，第一襯套22及第二襯套23是設成不會承受軸向力。又，亦可將第一襯套22之軸向的長度，設定成與從第二襯套23之在第4圖中為右端的端面至中空部21內的階段部21h之軸向的長度相等。即使如此實施，亦可阻止第一襯套22及第二襯套23負載軸向力。 　　又，第二襯套23，在本例中，其凸緣23b為抵接於第一殼體H1並定位軸向位置，定位部是以凸緣23b實施。而且，第二襯套23的固定部，在本例中，是設成螺紋部23d。滑閥孔Sh，相對於第二襯套23，是被設置在：從設成定位部的凸緣23b到作為固定部的螺紋部23d之間的範圍以外。於此情形時，凸緣23b(定位部)及螺紋部23d(固定部)以及滑閥孔Sh為串聯(直列)排列地配置於軸向，故滑閥孔Sh，相對於第二襯套23，只要設置在：與凸緣23b(定位部)及螺紋部23d(固定部)錯開於軸向的位置即可。 　　如此一來，可使壓縮荷重和拉伸荷重不會負載在第二襯套23之滑閥孔Sh的部位。也就是說，由於定位部是將第二襯套23定位於軸向，固定部是將第二襯套23固定於第一殼體H1的部分，故與第二襯套23的兩者之間會作用有壓縮荷重或拉伸荷重之情形。然而，當如前述方式配置滑閥孔Sh時，則不會有任何荷重負載於第二襯套23之設有滑閥孔Sh的部位，而可以阻止滑閥孔Sh的變形。 　　於第4圖中，第二襯套23雖是以螺紋鎖緊連結於第一殼體H1，不過亦可以廢止第二襯套裝設部21c的螺紋溝及螺紋部23d，而以螺栓鎖緊連結凸緣23b與殼體H來將第二襯套23固定於第一殼體H1。於此情形時，定位部及固定部為凸緣23b，滑閥孔Sh，相對於第二襯套23仍是被設在從定位部至固定部的範圍以外。即使如此實施，也可阻止對於第二襯套23之設有滑閥孔Sh的部位作用有軸向的荷重。 　　又，如第5圖所示，亦可廢止第二襯套裝設部21c的螺紋溝以及第二襯套23的套管23a之外周的螺紋部23d，而於凸緣23b的外周設置筒狀的內周螺紋部60，使上述內周螺紋部60螺鎖於第一殼體H1的外周來將第二襯套23固定於第一殼體H1。於此情形時，由於凸緣23b抵接於第一殼體H1的端部而使第二襯套23定位於軸向位置，故位於第二襯套23的定位部為凸緣23b，固定部為內周螺紋部60。滑閥孔Sh，在第二襯套23上，是被設置在定位部的凸緣23b與固定部的內周螺紋部60之間的範圍以外。即使如此實施，也可阻止對於第二襯套23之設有滑閥孔Sh的部位作用有軸向的荷重。又，於凸緣23b的外周設置內周螺紋部60之情形時，即使從徑向觀察是將滑閥孔Sh設置在與內周螺紋部重疊的位置，由於在第二襯套23上，仍是設置在定位部的凸緣23b與內周螺紋部60之間的範圍以外，故可阻止對於第二襯套23之設有滑閥孔Sh的部位作用有軸向的荷重。 　　第一滑閥24，為容納於第一襯套22內並可被引導朝向軸向移動。詳細而言，第一滑閥24，係具備有：可自由滑動地***於第一襯套22之內周小徑部22d的滑動軸部24a、及從滑動軸部24a之在第4圖中為右端朝向右方延伸之小徑軸部24b、以及設置於小徑軸部24b之在第4圖中為右端的圓錐梯狀的閥體24c。 　　滑動軸部24a，其外徑設得比小徑軸部24b還大徑，並滑接於第一襯套22的內周小徑部22d，藉由第一襯套22，使第一滑閥24之軸向的移動不會有軸晃動地被引導。小徑軸部24b，其外徑是比內周小徑部22d的內徑還小徑，且與設於第一襯套22的通孔22f相向。又，第一滑閥24，雖是相對於第一襯套22朝軸向移動，不過滑動軸部24a並沒有完全將通孔22f的開口閉塞。 　　閥體24c，其外徑設為比內周小徑部22d的內徑還大徑，將內周小徑部22d之在第4圖中為右端的開口緣作為閥座42，藉由第一滑閥24的軸向移動，能夠離開及就座於該閥座42。 　　又，在位於第一殼體H1的中空部21中的彈簧支承裝設部21a，裝設有彈簧支承27。彈簧支承27，為有底筒狀並於外周設有螺紋部27a，將該螺紋部27a螺合於設於第一殼體H1之中空部21的螺紋部21d而可裝設於第一殼體H1。又，彈簧支承27，係具備有：在避開螺紋部27a的外周位置並沿著周方向所裝設的密封環43。當將彈簧支承27如上述般地裝設於第一殼體H1時，則密封環43緊密接觸於中空部21中之彈簧支承裝設部21a的內周，藉由彈簧支承27，第一殼體H1的中空部21之在第4圖中的右端會閉鎖成液密狀態。 　　於該彈簧支承27與第一滑閥24的閥體24c之在第4圖中的右端之間，中介地安裝有彈簧S，藉由該彈簧S的施力，第一滑閥24，其閥體24c被施力往就座於閥座42的方向。如此地，藉由具備有閥體24c的第一滑閥24、及具備有閥座42的第一襯套22、以及彈簧S，而構成釋放閥RV。而且，在除了彈簧S以外沒有外力作用於第一滑閥24的狀態下，閥體24c被推壓於閥座42而閉閥，使釋放閥RV的開閥壓成為最大。而且，若在朝向將閥體24c開閥之方向施予推壓第一滑閥24的推力來對抗彈簧S的施力，調節該推力就可以調節閥體24c之朝向閥座42的施力，而可以調節釋放閥RV的開閥壓。 　　當釋放閥RV開閥時，會開放由：第四通口21m、環狀溝槽22b、通孔22f、以及內周小徑部22d內所構成的衰減力調整通路TP。另一方面，當閥體24c就座於閥座42而使釋放閥RV閉閥時，則會中斷內周小徑部22d內與內周大徑部22c的連接，使衰減力調整通路TP成為阻斷狀態。又，在本例中，下游通路DP，是由：內周大徑部22c內、通孔22e、環狀溝槽22a、以及第一通口21i所構成，如前述般，於下游通路DP，藉由於第一通口21i裝設的插栓50設有孔口O。又，如前述般，第一通口21i，是連接於位於壓缸裝置C中的儲槽6，第四通口21m，是連接於位於壓缸裝置C中的桿側室4。因此，設置有釋放閥RV之衰減力調整通路TP的上游，係與第1圖所示的壓缸裝置C同樣地連通於桿側室4，下游通路DP的下游是連通於儲槽6，藉由釋放閥RV之開閥壓的調整，可調整壓缸裝置C的衰減力。 　　又，在彈簧S與第一滑閥24之間，中介安裝有閥體側彈簧支承44。在本例中，彈簧S是設成線圈彈簧，閥體側彈簧支承44之在第4圖中的右端為鬆嵌合於彈簧S的內周，可藉由閥體側彈簧支承44吸收彈簧S及第一滑閥24之軸芯的偏位。藉此，由於彈簧S的施力在徑向上沒有偏離地作用於第一滑閥24，所以使第一滑閥24的開閥壓安定而不會不均。 　　第二滑閥25，是容納於第二襯套23內並被引導朝向軸向移動。又，在第4圖中，其右端為可朝向第一滑閥24之在第4圖中的左端進行抵接。詳細而言，第二滑閥25，係具備有：可自由滑動地***於第二襯套23之滑閥孔Sh的滑動軸部25a、及從滑動軸部25a之在第4圖中的右端朝向右方延伸之圓柱狀的閥部25b、以及設置於閥部25b之在第4圖中的右端並朝向軸向突出的凸部25c。 　　滑動軸部25a，是滑接於第二襯套23的滑閥孔Sh，並藉由第二襯套23使第二滑閥25之軸向的移動不會軸晃動地被引導。 　　閥部25b，其外徑係設定為與設於第二襯套23的滑閥孔Sh進行滑接之大小，當其右端配置在比位於滑閥孔Sh中之內周大徑部23e還要右方處時，則由設置於第二襯套23的通孔23f及滑閥孔Sh所形成之流路的連通會被阻斷。 　　又，在作為滑動軸部25a之在第4圖中為左端的後端，設置有凸緣25d，凸緣25d之在第4圖中的右端與第二襯套23之間，中介安裝有線圈彈簧45。第二滑閥25藉由該線圈彈簧45而被朝向第4圖中的左方施力。在除了線圈彈簧45的施力以外沒有外力作用的狀態下，第二滑閥25，如第4圖所示，其閥部25b相對於第二襯套23定位於內周大徑部23e內，而將由通孔23f及滑閥孔Sh所形成的流路予以連通。 　　再者，於第二襯套23之在第4圖中的左方，裝設有電磁線圈Sol，藉由對電磁線圈Sol的通電，以電磁線圈Sol的柱塞51對第二滑閥25施予朝在第4圖中的右方向的推力。又，藉由調節電磁線圈Sol的通電量，能夠調節施予第二滑閥25的推力。該推力，由於是對第二滑閥25施予對抗線圈彈簧45之方向的力，故得以使第二滑閥25抗過線圈彈簧45的施力而使閥部25b的前端朝向比第二襯套23內的內周大徑部23e更右方處移動。因此，藉由對電磁線圈Sol通電之有無，使第二滑閥25朝向軸向移動，而可以連通或阻斷上述流路。如此地，第二襯套23、第二滑閥25，以及線圈彈簧45，係構成了開閉上述流路之設定為常開型的開閉閥OV，該開閉閥OV，是設成藉由對電磁線圈Sol的通電而開閉上述流路的電磁閥。 　　當開閉閥OV為開閥時，會使由：通路29、閥孔28、第五通口31、第三通口21k、環狀溝槽23c、通孔23f、滑閥孔Sh、凹部23g、以及通孔22h所構成的故障安全通路FP成為連通狀態。故障安全通路FP，由於連通於第一襯套22的內周大徑部22c，因此故障安全通路FP，會在內周大徑部22c與衰減力調整通路TP合流，並且連通於下游通路DP。當故障安全通路FP處於連通狀態時，則設置於閥孔28內的故障安全閥FV亦處於可開閥狀態，從第四通口21m導入的壓力當達於故障安全閥FV的開閥壓力時故障安全閥FV會開閥，透過故障安全通路FP及下游通路DP可將桿側室4的壓力往儲槽6排出。又，在開閉閥OV為閉閥的狀態中，則由通孔23f及滑閥孔Sh所形成的流路的連接會中斷，使故障安全通路FP成為阻斷狀態。 　　又，藉由電磁線圈Sol的通電量，可以調整施予第二滑閥25的推力，當藉由第二滑閥25將上述流路閉閥再進一步地使第二滑閥25抵接於第一滑閥24時，則經由第二滑閥25亦可以將電磁線圈Sol的推力傳遞至第一滑閥24。 　　如此地，由於使與彈簧S對抗之方向的電磁線圈Sol的推力作用於第一滑閥24，故藉由對電磁線圈Sol之通電量的調節，可調節令第一滑閥24作用的推力，而能夠調節釋放閥RV的開閥壓。 　　如此地，衰減閥DV，藉由應用於壓缸裝置C，可發揮作為衰減力產生源的功能。而且，在本發明中的衰減閥DV中，於釋放閥RV的下游設有孔口O。孔口O，在欲通過孔口O之作動油的流量以高頻變動之情形時，具備有妨礙作動油之流量的變化的特性。在此，在釋放閥RV的閥體急遽地進行開閉動作之情形時，由於欲通過下游的孔口O之作動油的流量以高頻振動地變化，故孔口O會發揮其抑制流量的變動的功能。而且，於釋放閥RV為打開之情形時，作用於釋放閥RV之閥體的背壓會增加，相反地，於釋放閥RV為關閉之情形時，作用於釋放閥RV之閥體的背壓會減少，來妨礙釋放閥RV的急遽開閉。如此地，孔口O，係呈現妨礙釋放閥RV之閥體的急遽開閉動作，使動作緩慢地進行之阻尼作用。因此，對於具體的衰減閥DV中，藉由釋放閥RV在控制壓缸裝置C的衰減力時，即使在桿側室4產生壓力變動，藉由孔口O發揮的阻尼作用可以抑制釋放閥RV的高頻振動。因此，根據此具體的衰減閥DV，可以抑制釋放閥RV產生震動，對於壓缸裝置C所產生之衰減力不會產生波形的紊亂，可以提升由衰減力調整所改善之車體的減震控制的控制性，並可以避免衰減力的驟變並阻止異狀聲音的產生。 　　又，於具體的衰減閥DV中，由於在故障安全通路FP具備有對作動油的流動給予抵抗的故障安全閥FV，因此可依所期望特性來調整故障時的衰減力特性，並於故障時可發揮期望目標之衰減力特性。 　　又，於具體的衰減閥DV中，具備有：具有中空部21的第一殼體H1(殼體H)、及串聯(直列)排列地***於中空部21的第一襯套22與第二襯套23、及容納於第一襯套22內的第一滑閥24、以及容納於第二襯套23內的第二滑閥25。又，第二襯套23具備有：用以定位相對於第一殼體H1(殼體H)之軸向位置的凸緣23b(定位部)、及用以固定於第一殼體H1(殼體H)的螺紋部23d(固定部)、以及設置於從凸緣23b(定位部)至螺紋部23d(固定部)的範圍以外的滑閥孔Sh。如此地構成衰減閥DV時，阻止對於第二襯套23之設有滑閥孔Sh的部位作用有軸向的荷重之負載，亦不用使容納於中空部21內的第一襯套22負載軸向上的拉伸荷重或壓縮荷重，而可使防止此等脫落。因此，在第一襯套22與第二襯套23之用以容納第一滑閥24與第二滑閥25的內周形狀，不會產生應變。藉此，不需要對第一襯套22、第二襯套23、以及第一殼體H1的尺寸進行高精度的管理，不用將第一襯套22及第二襯套23的內周施以整形之加工，也可以保障第一滑閥24及第二滑閥25之朝向軸向的移動。藉由以上說明，根據衰減閥DV，是能夠實現加工容易且第一滑閥24及第二滑閥25的圓滑作動。 　　又，在本例中的衰減閥DV中，其滑閥孔Sh是設置在：相對於第二襯套23，要比凸緣23b(定位部)及螺紋部23d(固定部)更靠近第一殼體H1(殼體H)內側的位置。當如此地構成衰減閥DV時，可將用以設置第二襯套23之滑閥孔Sh的部位容納於第一殼體H1(殼體H)內，亦可以縮短衰減閥DV的全長。 　　又，在本例中的衰減閥DV，第一襯套22之軸向的長度，是以比從第二襯套23的端面至中空部21內的階段部21h為止的軸向長度還短的方式所設定的。因此，即使將第二襯套23裝設於第一殼體H1，第一襯套22也不會在壓縮狀態下受到第二襯套23與階段部21h所夾持，可以確實地實現軸向力不會對第一襯套22及第二襯套23產生作用的狀態。又，對於第一襯套22、第二襯套23、以及第一殼體H1之尺寸管理變得更加容易。 　　而且，在本例中的衰減閥DV中，定位部，為設置於第二襯套23外周的凸緣23b，也就是凸緣23b抵接於第一殼體H1(殼體H)的端面，來使第二襯套23相對於第一殼體H1(殼體H)被定位。當如此地構成衰減閥DV時，可以藉由簡單的構成，將第二襯套23定位於殼體H。又，在以螺栓將凸緣23b固定於第一殼體H1之情形時，使凸緣23b發揮既作為定位部，亦作為固定部之功能，而可以縮短第二襯套23的全長乃至於衰減閥DV的全長，無需負載對第二襯套23及第一襯套22作用的力矩，可以更加有效地阻止兩者的內周形狀的應變。 　　又，孔口O，由於只要設於：從衰減力調整通路TP與故障安全通路FP到儲槽6的下游通路DP即可，故也可以與殼體H為另外個別獨立地設置。 　　以上，雖然詳細地說明了本發明之較佳的實施形態，但只要實質沒有超出申請專利範圍下，是能夠改造、變形、及變更。 　　本案，是依據2016年9月9日對日本特許廳所申請的特願2016-176299主張優先權，並參照該專利申請案的全部內容來組構於本專利說明書中。the following, According to the illustrated embodiment, The present invention will be described. An embodiment of the damping valve DV, basically, As shown in Figure 1, To have: Attenuation force adjustment path TP and fail-safe path FP, And downstream paths DP, downstream of the damping force adjustment path TP and the fail-safe path FP, And a release valve RV provided in the damping force adjustment passage TP, And normally open on-off valves OV, And solenoid coil Sol, which adjusts the opening pressure of the release valve RV and closes the on-off valve OV at the time of energization, And an orifice O provided in the downstream passage DP, In this example, It is applied to the cylinder device C.  Pressure cylinder device C, Have: Pressure cylinder 1, And piston 2 slidably inserted into the cylinder 1 And a rod 3 inserted into the cylinder 1 and connected to the piston 2, And the rod-side chamber 4 and the piston-side chamber 5, which are divided by the piston 2 in the cylinder 1, And storage tank 6, And a first unloading valve 8 provided halfway through the first passage 7 connecting the rod-side chamber 4 and the piston-side chamber 5, And a second unloading valve 10 provided halfway through the second passage 9 connecting the piston-side chamber 5 and the storage tank 6; And a rectification passage 11 that allows only flow from the piston-side chamber 5 to the rod-side chamber 4, And the suction passage 12, which allows only the flow from the reservoir 6 to the piston-side chamber 5, And the damping valve DV, It is configured as a so-called single-rod type cylinder device. Attenuation valve DV, Is located between the rod-side chamber 4 and the storage tank 6 of the cylinder device C, Resistance is given to the flow of the liquid discharged from the pressure cylinder 1 toward the storage tank 6.  Alas, The rod-side chamber 4 and the piston-side chamber 5 are filled with a hydraulic oil as a liquid, and, In storage tank 6, In addition to the working oil, it is filled with gas. also, In the storage tank 6, There is no particular need to compress the gas into a pressurized state. also, Cylinder device C, It is installed between the trolley and the body. Although not shown on the drawing, However, the pole 3 is connected to the trolley and the body of the railway vehicle. The pressure cylinder 1 is connected to the other side of the trolley and the vehicle body. also, Cylinder device C, Because it is set to a single lever type, Therefore, compared with the double rod type cylinder device, Easy to ensure long strokes, Can shorten the overall length of the cylinder device C, In order to improve the loadability of railway vehicles. also, The liquid as the working medium of the cylinder device C, In this case, it ’s oil. However, depending on the use environment of the cylinder device C, water or an aqueous solution may be used. Other liquids can also be used.   the following, Each part of the damping valve DV and the cylinder device C will be described in detail. The cylinder 1 is cylindrical, The right end of the first figure is closed by the cover 13, An annular rod guide 14 is attached to the left end of the first figure. also, In the above-mentioned rod guide 14, A freely sliding rod 3 is inserted; The rod 3 is inserted into the pressure cylinder 1 in a freely movable manner. The rod 3, One end protrudes toward the outside of the pressure cylinder 1, The other end in the pressure cylinder 1 is connected to the piston 2; The piston 2 is slidably inserted into the pressure cylinder 1.  Alas, The space between the outer periphery of the rod guide 14 and the pressure cylinder 1 is sealed by a sealing member (not shown). Thereby, the inside of the pressure cylinder 1 is maintained in a sealed state. and, The rod-side chamber 4 and the piston-side chamber 5 divided by the piston 2 in the pressure cylinder 1, It is filled with a working oil as a liquid as described above.  Alas, In the case of the cylinder device C, Let the cross-sectional area of the rod 3 be a half of the cross-sectional area of the piston 2, Making the pressure-receiving area on the rod-side chamber 4 side of the piston 2 one-half the pressure-receiving area on the piston-side chamber 5 side, When the cylinder device C is extended and shortened, The flow rates discharged from the cylinder 1 through the damping valve DV toward the storage tank 6 are equal.  Back to the picture, A cover 13 at the left end of the rod 3 in the first figure and the right end of the pressure cylinder 1, Equipped with a mounting section with no display on the drawing, The cylinder device C is installed at a position between the body of the railway vehicle and the trolley.  And, For the cylinder device C of this example, The rod-side chamber 4 and the piston-side chamber 5 communicate with each other through a first passage 7. Halfway through the first path 7, A first unloading valve 8 is provided. The first path 7, Connect the rod-side chamber 4 and the piston-side chamber 5 to the outside of the pressure cylinder 1, However, it may be provided on the piston 2.  First unloading valve 8, It is set as an electromagnetic on-off valve, Have: The communication position between the connecting rod-side chamber 4 and the piston-side chamber 5, And the blocking position that blocks the communication between the rod-side chamber 4 and the piston-side chamber 5, When the current is applied, the first passage 7 is opened to communicate the rod-side chamber 4 and the piston-side chamber 5.  Alas, For the cylinder device C of this example, The piston-side chamber 5 and the storage tank 6 communicate with each other through a second passage 9. Halfway through the second path 9, A second unloading valve 10 is provided. Second unloading valve 10, It is set as an electromagnetic on-off valve, Have: The communication position between the piston-side chamber 5 and the storage tank 6, And a blocking position that prevents communication between the piston-side chamber 5 and the storage tank 6, When the current is applied, the second passage 9 is opened to communicate the piston-side chamber 5 with the storage tank 6.  Alas, As shown in Figure 1, The cylinder device C of this example, A rectification passage 11 is provided that allows only flow from the piston-side chamber 5 to the rod-side chamber 4. also, Rectifying path 11, It may be provided outside the piston 2. Furthermore, The cylinder device C of this example, The suction passage 12 is provided to allow only the flow from the reservoir 6 to the piston-side chamber 5.  Therefore, For the cylinder device C of this example, When the first unloading valve 8 and the second unloading valve 10 are in the blocking position, When stretched by external force, The working oil will be pushed out from the compressed rod-side chamber 4 through the damping valve DV toward the storage tank 6, On the other hand, the enlarged piston-side chamber 5 is supplied with working oil from the storage tank 6 through the suction passage 12. therefore, When the elongation is activated, Cylinder device C, The damping valve DV resists the flow of the passing oil, The pressure in the rod-side chamber 4 is increased to exert a damping force against elongation. also, In that case, The flow of the hydraulic oil through the damping valve DV, It will be the value obtained by subtracting the cross-sectional area of the rod 3 from the cross-sectional area of the piston 2 and multiplying it by the amount of movement of the piston 2.   The opposite of, When the first unloading valve 8 and the second unloading valve 10 are in the blocking position, When the cylinder device C is shortened by external force, The working oil moves from the compressed piston-side chamber 5 toward the rod-side chamber 4 via the rectifying passage 11. also, When the cylinder device C is shortened, Since the rod 3 penetrates into the pressure cylinder 1, Therefore, the volume of hydraulic oil that the rod 3 intrudes into the cylinder 1 becomes excessive in the cylinder 1 and is discharged toward the storage tank 6 through the damping valve DV. During this shortening action, Cylinder device C, The damping valve DV resists the flow of the passing oil, The pressure in the cylinder 1 is increased to exert a damping force against shortening. also, In that case, The oil volume through the damping valve DV, It is the amount by which the cross-sectional area of the rod 3 is multiplied by the amount of movement of the piston 2. here, The cross-sectional area of the rod 3, Since it is set to one-half the cross-sectional area of the piston 2, Therefore, whether the cylinder device C is extended or contracted, As long as the amount of movement of the piston 2 is the same, The amount of oil flowing through the damping valve DV will be equal. therefore, Cylinder device C, As long as the moving speed of the piston 2 is the same on both sides of the telescope, It can exert equal attenuation force.  Alas, Both the first unloading valve 8 and the second unloading valve 10 are in the blocking position when they are not energized. Therefore, in the event of inability to supply electricity, The cylinder device C of this example, Since the attenuation force must be exerted on the expansion and contraction as described above, Therefore, it can function as a passive damper.  Alas, In the cylinder device C of this example, When the first unloading valve 8 is in the communication position and the second unloading valve 10 is in the blocking position, The rod-side chamber 4 and the piston-side chamber 5 communicate with each other via a first passage 7, However, the communication between the piston-side chamber 5 and the storage tank 6 is blocked. In this state, When the cylinder device C is contracted by an external force, The volume of hydraulic oil that the rod 3 penetrates into the cylinder 1 is discharged from the cylinder 1 toward the damping valve DV. The damping force against shrinkage is exhibited in the same manner as described above. The other side, In this state, If the cylinder device C is extended, The hydraulic oil moves from the reduced rod-side chamber 4 to the enlarged piston-side chamber 5 via the first passage 7, A part of the working oil withdrawn from the cylinder 1 by the rod 3 is supplied from the reservoir 6 into the cylinder 1 through the suction passage 12. therefore, On that occasion, The hydraulic oil does not flow towards the damping valve DV, Therefore, the cylinder device C does not exert a damping force.  And again, In the cylinder device C of this example, When the first unloading valve 8 is in the blocking position and the second unloading valve 10 is in the communicating position, The communication between the rod-side chamber 4 and the piston-side chamber 5 is blocked, However, the piston-side chamber 5 and the storage tank 6 are communicated via a second passage 9. In this state, When the cylinder device C is extended by an external force, With the reduction of the rod-side chamber 4, The working oil is discharged from the rod-side chamber 4 toward the damping valve DV. A damping force against elongation is exhibited in the same manner as described above. The other side, In this state, If the cylinder device C is contracted, Then, the hydraulic oil moves from the reduced piston-side chamber 5 to the enlarged rod-side chamber 4 through the rectification passage 11, A part of the hydraulic oil that has entered the rod 3 into the cylinder 1 is discharged from the piston-side chamber 5 into the storage tank 6 through the second passage 9. therefore, In this case, Since the hydraulic oil does not flow towards the damping valve DV, Therefore, the cylinder device C does not exert a damping force. So In the cylinder device C, It can be used as a single-effect damper that can attenuate the force by choosing either to expand or contract.  Alas, In the case of the cylinder device C, A degassing orifice 15 is provided so that the air mixed in the cylinder 1 can be discharged from the rod-side chamber 4 toward the storage tank 6.  Then, Attenuation valve DV, As shown in Figure 1, To have: Attenuation force adjustment path TP and fail-safe path FP, And downstream channels DP, And release valve RV, And on-off valve OV, And Solenoid Sol, And an orifice O provided in the downstream passage DP. In this example, Attenuation valve DV, As described above, it is provided between the rod-side chamber 4 and the storage tank 6. Specifically, The damping force adjustment path TP and the fail-safe path FP provided in parallel are connected to the rod-side chamber 4 and the downstream path DP. Downstream pathway DP, One end is connected to the attenuation force adjustment path TP and the fail-safe path FP, The other end is connected to the storage tank 6. therefore, Rod side chamber 4 and storage tank 6, To adjust the path TP through the attenuation force, The fail-safe path FP and the downstream path DP communicate with each other.  Release valve RV, Is set in the attenuation force adjustment path TP, On-off valve OV, It is set on the fail-safe path FP. On-off valve OV, The valve is opened by the force of a spring. And when it receives thrust from Solenoid Sol, Become a closed solenoid valve. also, On-off valve OV, When the solenoid Sol is not energized, The fail-safe path FP is connected by the force of the spring, When a certain amount of current is supplied to the electromagnetic coil Sol, It becomes a normally open on-off valve that blocks the fail-safe path FP.  Release valve RV, It is driven by the thrust from the solenoid Sol through the on-off valve OV, When the solenoid Sol is not energized, By the force of the spring, Maximize valve opening pressure. also, When the solenoid Sol is energized and the on-off valve OV is in the blocking position, The thrust of the solenoid Sol exerts an action against the release valve RV via the on-off valve OV as a force against the spring. therefore, If the solenoid Sol is energized, Corresponding to the amount of electricity, Adjustable opening pressure of the release valve RV, When the amount of power is increased, The opening pressure of the release valve RV will become smaller, The opposite of, When the solenoid Sol is not energized, The release valve RV has a maximum opening pressure. in this way, In this example, the damping valve DV, The same solenoid Sol can be used to adjust the opening pressure of the release valve RV and open and close the on-off valve OV.  Alas, In this example, For the fail-safe path FP, Provided with fail-safe valve FV and fail-safe port A in parallel with fail-safe valve FV. The fail-safe valve FV, Is in a state where the fail-safe path FP is connected by the action of the on-off valve OV, When the pressure on the upstream side reaches a predetermined pressure, the valve will open. This valve opening pressure is set to a value smaller than the maximum valve opening pressure of the release valve RV.  The damping valve DV, When it works properly, When the solenoid Sol is energized, The opening and closing valve OV can be blocked to adjust the opening pressure of the release valve RV, On the other hand, it is possible to control the pressure in the rod-side chamber 4 when the cylinder device C performs expansion and contraction. Halfway through the downstream path DP, Is provided with an orifice O, The orifice O is used to provide resistance to the flow of the working oil. therefore, The pressure of the lever side chamber 4 controlled by the release valve RV, The pressure-resistance component of the orifice O superimposes the opening pressure of the release valve RV as an override. however, Due to pressure overload of orifice O, There is a concern that the controllability of the pressure of the rod-side chamber 4 formed by the release valve RV will not have a significant influence.  Attenuation valve DV, Structured as above, When the cylinder device C is extended, The opening pressure of the release valve RV is adjusted according to the amount of current given to the solenoid Sol, With this, the pressure in the rod-side chamber 4 is controlled, The damping force that suppresses the elongation generated by the cylinder device C is controlled. also, When the cylinder device C is retracted, The opening pressure of the release valve RV is adjusted according to the amount of current given to the solenoid Sol, Thereby, the pressure in the rod-side chamber 4 and the rod-side chamber 4 is controlled, The damping force that suppresses the contraction generated by the cylinder device C is controlled.  Alas, When the solenoid coil Sol cannot be energized (when abnormal), The on-off valve OV communicates with the fail-safe path FP for opening the valve, Make the fail-safe valve FV work, With fail-safe valve FV and orifice O, The damping force of the cylinder device C during expansion and contraction is exerted.  Therefore, The damping force characteristic of the cylinder device C provided with the damping valve DV of this example under normal conditions, When the piston speed is in the low speed region, As shown by line a in Figure 2, Shows the square characteristic of the outgassing orifice 15, When the piston speed increases and the release valve RV opens, As shown by line b in Figure 2, Showing the opening pressure of the release valve RV, An overload characteristic is added as a pressure loss component of the orifice O. also, Overload of orifice O, Since it becomes larger as the piston speed becomes higher, Therefore, after the release valve RV is opened, The characteristic that the attenuation coefficient gradually increases in response to an increase in the piston speed. also, The aforementioned damping force characteristics are characteristics without changing the opening pressure of the release valve RV. By adjusting the opening pressure of the release valve RV, The damping force of the cylinder device C can be adjusted.  And, The cylinder device C thus constituted, When the first unloading valve 8 and the second unloading valve 10 are located at the blocking position, When it is stretched by external force, The hydraulic oil is discharged from the inside of the pressure cylinder 1 toward the storage tank 6 through the release valve RV and the orifice O. and, When the amount of current supplied to the on-off valve OV is adjusted to adjust the opening pressure of the release valve RV, Then, the damping force generated by the cylinder device C can be adjusted. therefore, When the first unloading valve 8 and the second unloading valve 10 are located in the blocking position under normal conditions, Cylinder device C, It can function as a damper with adjustable damping force on both sides of the telescope.  Alas, In the case where the first unloading valve 8 is positioned at the communication position and the second unloading valve 10 is positioned at the blocking position, When the first unloading valve 8 is located at the blocking position and the second unloading valve 10 is located at the communication position, As before, This is a mode in which the cylinder device C exerts a damping force only on either the extension or contraction. therefore, E.g, If you choose this mode, When the direction in which the damping force is exerted is the direction in which the vibration of the car body is caused by the vibration of the trolley of the railway vehicle, The cylinder device C can be used as a single-effect damper so that the damping force is not formed in such a direction. therefore, The cylinder device C, In normal times, It is easy to realize semi-active control according to Karnopp theory, Can function as a semi-active damper.   on the other hand, When the failure to supply power to the cylinder device C is interrupted for some reason, The first unloading valve 8 and the second unloading valve 10 will be in the blocking position. As before, The cylinder device C functions as a passive damper. In this state, If the cylinder device C expands and contracts, Then, the hydraulic oil must be discharged from the cylinder 1. at this time, Since the on-off valve OV is an open valve, Therefore, the discharged hydraulic oil will pass through the fail-safe valve FV, The failure orifice A and the orifice O flow into the storage tank 6. therefore, At that time, Fail-safe valve FV, The orifice A and orifice O for failure will resist the flow of the hydraulic oil, The cylinder device C exerts a damping force. also, When the expansion and contraction speed of the cylinder device C is high speed, When the pressure of the rod-side chamber 4 exceeds the opening pressure of the release valve RV, The release valve RV is also opened to allow the passage of hydraulic oil.  So, Cylinder device C, Under normal conditions, it can function as a double-effect damper or a single-effect semi-active damper with adjustable attenuation. Can function as a passive damper in the event of a failure.  And, For the damping valve DV of the present invention, An orifice O is provided downstream of the release valve RV. Orifice O, When the flow rate of the hydraulic oil that is going to pass through the orifice O fluctuates due to high frequency, It has the characteristics of hindering the change of the flow rate of the hydraulic oil. here, When the valve body of the release valve RV is suddenly opened and closed, Because the flow rate of the working oil that is going to pass through the downstream orifice O changes oscillatingly due to high frequency, Therefore, the function of suppressing the fluctuation of the flow rate of the orifice O can be exerted. When the release valve RV is opened, The back pressure acting on the valve body of the release valve RV will increase, Instead, Where the release valve RV is closed, The back pressure acting on the valve body of the release valve RV will be reduced, This prevents the rapid opening and closing of the release valve RV. in this way, Orifice O, A damping effect that slows down the rapid opening and closing operation of the valve body of the release valve RV is exhibited. therefore, In the damping valve DV of the present invention, When the damping force of the cylinder device C is controlled by the release valve RV, Even if pressure fluctuations occur in the rod-side chamber 4, The high-frequency vibration of the release valve RV can also be suppressed by the damping effect exerted by the orifice O. therefore, According to the damping valve DV of the present invention, Can suppress the vibration of the release valve RV, Does not cause waveform disturbance of the damping force generated by the cylinder device C, Can improve the controllability of the shock absorption control of the vehicle body improved by the damping force adjustment, And to avoid sudden changes in the attenuation force can also prevent the generation of strange sounds.  Alas, In the damping valve DV of this example, Have: Fail-safe valves FV, which resist the flow of hydraulic oil in the fail-safe path FP, And orifice A for failure. In the damping valve DV thus constituted, When the current supply to the solenoid Sol is interrupted, Not only the orifice O, The fail-safe valve FV and fail-safe orifice A also resist the flow of the hydraulic oil. Properties of orifice O, Although it is set such that it does not affect the controllability due to the release valve RV that functions effectively in normal conditions, But for the fail-safe valve FV, It is possible to set its characteristics independently of other valves. therefore, According to the damping valve DV of this example, The damping force characteristics at the time of failure can be adjusted to the desired characteristics, In the event of a failure, the damping force characteristics can be exhibited as expected. also, In the communication position of the on-off valve OV, It can also be made to resist the flow of the working oil flowing in the fail-safe path FP, The function of the fail-safe valve FV is integrated with the on-off valve OV. also, When the damping force is exerted by the orifice O during a failure, It is also possible to abolish the fail-safe valve FV. Fail-safe valve FV, Is used as a relief valve or a pressure regulator. also, As shown in Figure 4, Fail-safe valve FV, Can be made into a release valve with an orifice, Orifices can also be made as different individuals.  And again, In the cylinder device C of this example, The department has: The inside is divided into a rod-side chamber 4 and a piston-side chamber 5 by a piston 2. And storage tank 6, And a first unloading valve 8 provided in a first passage 7 that communicates the rod-side chamber 4 with the piston-side chamber 5, And a second unloading valve 10 provided in a second passage 9 communicating the piston-side chamber 5 with the storage tank 6, And a rectification passage 11 that allows only flow from the piston-side chamber 5 to the rod-side chamber 4, And the suction passage 12, which allows only the flow from the reservoir 6 to the piston-side chamber 5, And the damping valve DV. According to the cylinder device C thus constituted, In normal times, Can be used as a dual-effect damper or single-effect semi-active damper that can adjust the attenuation force. In the event of a failure, it can function as a passive damper.  Alas, In the cylinder device C, As shown in Figure 3, If a pump P is provided which sucks the working oil from the storage tank 6 and supplies it to the rod-side chamber 4, Then, the cylinder device C can be made to function as an actuator for actively telescopic driving. also, In this way, the cylinder pressing device C is switched by the opening and closing of the first unloading valve 8 and the second unloading valve 10, It can function as a single-acting actuating damper that exerts thrust only when it is extended or contracted. therefore, In this cylinder device C, For switching between the actuator and the semi-active damper, There is no need to switch between stopping and driving the pump P.  The damping valve DV was explained in principle in the foregoing, The damping valve DV having a specific structure shown in FIG. 4 will be described below. Specific attenuation valve DV, As shown in Figure 4, Its composition is: A housing H having a hollow portion 21, And the first bushing 22 and the second bushing 23 inserted in the hollow part 21 in series (in-line), And the first spool valve 24 housed in the first bushing 22, And a second slide valve 25 housed in the second bushing 23.   the following, Each part of the damping valve DV will be described in detail. First of all, Housing H, In this example, Is equipped with the first case H1, And a second casing H2 mounted on a side of the first casing H1. and, Hollow section 21, Is provided in the first case H1, Opening from the outside of the first case H1, In this case, It opens from the axial ends of the first case H1 toward the outside. The hollow section 21, In this example, To open from both ends of the first case H1, However, it is also possible to make a bag hole by opening from one side.  Alas, The hollow part 21 provided in the first case H1, In Figure 4, from the right end side, there are: A spring bearing installation portion 21a on which a spring bearing 27 is installed, And a bush accommodating portion 21b containing the first bush 22 and the second bush 23, And a second bushing mounting portion 21c on which the second bushing 23 is mounted.  Spring support installation portion 21a, In Figure 4, Formed at the right end of the first case H1, A threaded portion 21d is provided on the left in FIG. 4, And the inner diameter on the right in FIG. 4 is made larger than the threaded portion 21d. A part of the hollow portion 21 is formed.  Bushing receiving portion 21b, Caused by: To the left of the threaded portion 21d in FIG. 4, The front end portion 21e, whose inner diameter is larger than that of the threaded portion 21d, is formed. And to the left of the front end 21e in FIG. 4, The intermediate portion 21f, whose inner diameter is larger than the front end portion 21e, And the left neighbor of the middle part 21f in FIG. 4, The inner diameter is formed by a rear end portion 21g having a larger diameter than the middle portion 21f. It becomes a part of the hollow part 21. Between the front end of the bush accommodating portion 21b and the rear end of the spring bearing installation portion 21a, A stage portion 21h is formed. Second lining set part 21c, In Figure 4, Is formed at the left end of the first case H1, It becomes a part of the hollow part 21.  Alas, First case H1, In this example, Have: The first through port 21i, which is opened in the radial direction from the outer peripheral side and communicates with the front end portion 21e, And a second opening 21j, which opens from the outer peripheral side toward the radial direction and communicates with the intermediate portion 21f, And a third port 21k which opens from the outer peripheral side toward the radial direction and communicates with the rear end portion 21g, And a fourth port 21m that opens from the outer periphery toward the inner periphery. also, No display on the drawing, First port 21i, Is connected to the storage tank 6 located in the cylinder device C; The second port 21j and the fourth port 21m, It is connected to the rod-side chamber 4 located in the cylinder device C. also, A plug 50 having an orifice O is mounted on the inner periphery of the first through hole 21i of the first case H1.  And again, The second casing H2 mounted on the side of the first casing H1, The case H is formed in cooperation with the first case H1. Second housing H2, Have: From the outside of the left end in Figure 4, A valve hole 28 as a hole opened in parallel with the hollow portion 21, And a passage 29 that opens from the inner periphery and leads to the valve hole 28. also, In this example, Since a part of the passage 29 is formed by a hole opened from the right end of the second case H2 in FIG. 4, Therefore, the open end of the right end of the hole in FIG. 4 is closed by the bolt 33. also, In the second case H2, A fifth port 31 is provided which opens from the inner periphery and leads to the valve hole 28.  时 When the second case H2 is mounted on the first case H1, It is the passage 29 that faces the second port 21j to make these communicate, The fifth port 31 and the third port 21k face each other to communicate with each other. also, The first casing H1 and the second casing H2 may also be provided as the same part instead of separate entities.  的 The inner diameter of the valve hole 28, Is set larger than the inner diameter of the open end connected to the valve hole 28 in the passage 29, In valve hole 28, The open end of the valve hole 28 facing the passage 29 is used as the valve seat 34, A valve body 35 which can be left and seated on the valve seat 34 is accommodated. Furthermore, In valve hole 28, Contains a spring 16 that biases the valve body 35 toward the valve seat 34 side, A cover 37 that functions as a spring support is screwed to the left end side of the valve hole 28, 来 封 门 孔 28。 To block the valve hole 28. Spring 16, Is sandwiched between the cover body 37 and the valve body 35 in a compressed state, If the installation position of the cover 37 relative to the valve hole 28 is adjusted, The biasing force of the spring 16 applied to the valve body 35 can be adjusted. and, Fail-safe valve FV Valve body 35, Spring 16, And a cover 37.  Alas, In the valve body 35, Provided with orifice A for failure, Orifice A for this fault, Is connected in parallel to the fail-safe valve FV, Even if the fail-safe valve FV is closed, it communicates with the passage 29.  Therefore, The working oil is introduced from the outside through the fourth port 21m. When the pressure in the passage 29 exceeds the opening pressure of the fail-safe valve FV, The valve body 35 will retract from the valve seat 34 and open the valve. The path 29 is connected to the fifth port 31.  第 一套 22 ， The first bushing 22, It is provided with a cylindrical shape having a step so that the outer diameter of the front end side on the right end side in FIG. 4 is smaller than the outer diameter of the rear end side on the left end side in FIG. 4, Two annular grooves 22a, 22b.  Alas, First bushing 22, Have: The inner peripheral large diameter portion 22c provided on the inner periphery of the front end side, And an inner peripheral small diameter portion 22d having a smaller diameter than the inner peripheral large diameter portion 22c provided on the inner periphery of the rear end side. Furthermore, First bushing 22, Have: A through hole 22e, which opens from the annular groove 22a and communicates with the inner peripheral large diameter portion 22c, And a through hole 22f that opens from the annular groove 22b and communicates with the inner peripheral small diameter portion 22d, And a through hole 22h that opens from the rear end and opens to the step portion 22g formed between the inner peripheral large diameter portion 22c and the inner peripheral small diameter portion 22d.  Alas, On the outer periphery of the first bushing 22, That is, between the annular groove 22a and the annular groove 22b along the circumferential direction, Equipped with a sealing ring 38, On the rear end side than the annular groove 22b, A seal ring 39 is attached along the circumferential direction.  The first bush 22 thus constituted, Is inserted into the hollow portion 21 of the first case H1 from the small diameter side, The small-diameter portion is fitted into the tip portion 21e, The large-diameter portion is fitted in the middle portion 21f of the first housing H1, And accommodated in the bush accommodating portion 21 b located in the hollow portion 21. As a result, Sealing ring 38, 39 is in close contact with the inner periphery of the bush accommodating portion 21b of the first housing H1, and seals between the annular groove 22a and the annular groove 22b. also, Annular groove 22a, Is opposite to and communicates with the first port 21i provided in the first housing H1, Annular groove 22b, It is opposed to and communicates with the second port 21j provided in the first case H1. therefore, Path 29, Is through the second port 21j, Annular groove 22b, And the through hole 22 f communicates with the first bushing 22. also, First port 21i, Communicates with the inside of the first bush 22 through the annular groove 22a and the through hole 22e, It is further connected to the fourth port 21m.  Second bush 23, It is provided with a cylindrical shape having a step so that the outer diameter of the front end side on the right end side in FIG. 4 is smaller than the outer diameter of the rear end side on the left end side in FIG. 4, It has: A cylindrical sleeve 23a provided on the rear end side and standing up to the left in FIG. 4 And a flange 23b provided on the outer periphery of the rear end of the sleeve 23a, And an annular groove 23c provided between the small-diameter portion and the large-diameter portion, And a screw portion 23d provided on the outer periphery of the sleeve 23a as a fixing portion.  Alas, The second bushing 23 is made into a tube shape, A slide valve hole Sh is formed in the inner side, In the slide valve hole Sh, An inner-peripheral large-diameter portion 23e is provided in which the inner periphery has a large diameter halfway. Furthermore, Second bushing 23, A through hole 23f is provided which opens from the annular groove 23c and communicates with the inner peripheral large diameter portion 23e. also, On the periphery of the second bushing 23, That is, with respect to the annular groove 23c in the axial direction, respectively along the circumferential direction, Equipped with sealing ring 40, 41.  The second bushing 23 thus constituted, The flange 23b is in contact with the rear end face of the first housing H1 which is the left end face in FIG. 4 and determines the axial position. And installed on the open end of the hollow portion 21 of the first case H1. Specifically, Second bushing 23, The threaded portion 23d as a fixed portion is screwed to the second bushing portion 21c formed in the hollow portion 21, Instead, it is fixed to the first case H1. As a result, Second bushing 23, The small diameter portion is fitted into the middle portion 21f in the first case H1, The large diameter portion is fitted into the rear end portion 21g in the first case H1, It is accommodated in the hollow portion 21. At the right end of the second bushing 23 in FIG. 4, Provided with a recessed portion 23g, Recess 23g, It faces the through hole 22h which is opened toward the rear end of the first bushing 22 which is the left end in FIG. 4, The inner peripheral large-diameter portion 22c in the first bush 22 is communicated through the through hole 22h. also, The inner diameter of the recess 23g, Is made smaller than the outer diameter of the first bushing 22 and larger than the inner diameter of the second bushing 23, The right end surface of the second bushing 23 in FIG. 4 faces the rear end surface of the first bushing 22. therefore, Second bushing 23, When installed in the first case H1, It can exert the anti-off function as the first bushing 22 accommodated in the hollow portion 21.  时 When the second bushing 23 is accommodated in the hollow portion 21 as described above, Seal ring 40, 41 is in close contact with the inner periphery of the bush accommodating portion 21b of the first housing H1, The annular groove 23 c is not communicated to other places by the outer periphery of the second bushing 23. also, Annular groove 23c, It is opposite to and communicates with the third port 21k provided in the first casing H1. therefore, The fifth port 31 of the second casing H2, To pass the third port 21k, Annular groove 23c, And the through hole 23f communicates with the inside of the second bushing 23.  Alas, Flange 23b, A part of the open end of the valve hole 28 which is the left end in FIG. 1 is plugged, This can prevent the lid body 37 attached to the valve hole 28 from falling off from the second case H2. therefore, The fail-safe valve FV provided in the second case H2 is not likely to be detached from the second case H2.  Alas, In this example, In a state where the second bushing 23 is mounted on the first housing H1 and positioned in the axial position, The axial length of the first bushing 22, It is set to be shorter than the axial length from the end surface of the second bushing 23 which is the right end in FIG. 4 to the step portion 21h in the hollow portion 21. therefore, Even if the second bushing 23 is attached to the first housing H1, The first bushing 22 will not be held in a compressed state by the second bushing 23 and the stage portion 21h. The first bushing 22 and the second bushing 23 are provided so as not to receive an axial force. also, The axial length of the first bushing 22 can also be adjusted. It is set to be equal to the axial length from the end face of the second bushing 23 which is the right end in FIG. 4 to the step portion 21h in the hollow portion 21. Even so, It is also possible to prevent the first bushing 22 and the second bushing 23 from loading an axial force.  Alas, Second bushing 23, In this example, The flange 23b is in contact with the first housing H1 and positioned in the axial position. The positioning portion is implemented by the flange 23b. and, The fixed part of the second bushing 23, In this example, It is provided as the threaded portion 23d. Spool valve hole Sh, Relative to the second bushing 23, Is set at: It is outside the range from the flange 23b provided as a positioning part to the screw part 23d as a fixed part. In this case, The flange 23b (positioning portion), the screw portion 23d (fixing portion), and the spool hole Sh are arranged in series (in-line) in the axial direction, Therefore, the spool valve hole Sh, Relative to the second bushing 23, Just set in: The flange 23b (positioning portion) and the screw portion 23d (fixing portion) may be offset from the axial position.  This way, It is possible to prevent the compressive load and the tensile load from being applied to the portion of the slide valve hole Sh of the second bushing 23. That is, Since the positioning portion positions the second bushing 23 in the axial direction, The fixing portion is a portion that fixes the second bushing 23 to the first casing H1, Therefore, there may be a case where a compressive load or a tensile load acts between the second bushing 23 and the second bushing 23. however, When the spool valve hole Sh is configured as described above, There will not be any load on the portion of the second bushing 23 provided with the slide valve hole Sh, The deformation of the spool hole Sh can be prevented.  In Figure 4, Although the second bushing 23 is fastened to the first housing H1 with a screw lock, However, it is also possible to abolish the screw groove and the screw portion 23d of the second bushing setting portion 21c, The flange 23b and the housing H are fastened by bolts to fix the second bushing 23 to the first housing H1. In this case, The positioning portion and the fixing portion are flanges 23b, Spool valve hole Sh, The second bushing 23 is still provided outside the range from the positioning portion to the fixing portion. Even so, It is also possible to prevent an axial load from acting on a portion of the second bushing 23 where the spool hole Sh is provided.  Alas, As shown in Figure 5, It is also possible to abolish the thread groove of the second bushing installation portion 21c and the screw portion 23d on the outer periphery of the sleeve 23a of the second bush 23, A cylindrical inner peripheral screw portion 60 is provided on the outer periphery of the flange 23b. The inner peripheral screw portion 60 is screwed to the outer periphery of the first housing H1 to fix the second bushing 23 to the first housing H1. In this case, Since the flange 23b abuts on the end of the first housing H1, the second bushing 23 is positioned at the axial position, Therefore, the positioning portion on the second bushing 23 is a flange 23b, The fixed portion is an inner peripheral screw portion 60. Spool valve hole Sh, On the second bushing 23, It is outside the range provided between the flange 23b of the positioning portion and the inner peripheral screw portion 60 of the fixing portion. Even so, It is also possible to prevent an axial load from acting on a portion of the second bushing 23 where the spool hole Sh is provided. also, When the inner peripheral screw portion 60 is provided on the outer periphery of the flange 23b, Even when the spool valve hole Sh is provided in a position overlapping the inner thread portion when viewed from the radial direction, Since on the second bushing 23, Still outside the range provided between the flange 23b of the positioning portion and the inner peripheral screw portion 60, Therefore, an axial load can be prevented from acting on a portion of the second bushing 23 where the spool hole Sh is provided.  第一 滑 阀 24, It is accommodated in the first bushing 22 and can be guided to move in the axial direction. Specifically, First spool valve 24, The department has: The slide shaft portion 24a, which is slidably inserted into the inner peripheral small diameter portion 22d of the first bushing 22, And a small-diameter shaft portion 24b extending from the right end of the slide shaft portion 24a to the right in FIG. And a tapered trapezoidal valve body 24c provided on the small-diameter shaft portion 24b and having a right end in FIG. 4.  Sliding shaft portion 24a, The outer diameter is set larger than the small-diameter shaft portion 24b. And slidingly connected to the inner peripheral small diameter portion 22d of the first bushing 22, With the first bushing 22, The axial movement of the first spool valve 24 is guided without shakiness of the shaft. Small-diameter shaft portion 24b, Its outer diameter is smaller than the inner diameter of the inner peripheral small diameter portion 22d. It faces the through hole 22f provided in the first bushing 22. also, First spool valve 24, Although it moves axially relative to the first bushing 22, However, the sliding shaft portion 24a does not completely close the opening of the through hole 22f.  Valve body 24c, The outer diameter is set to be larger than the inner diameter of the inner peripheral small diameter portion 22d. Let the opening edge of the inner peripheral small-diameter portion 22d which is the right end in FIG. 4 be the valve seat 42, By the axial movement of the first spool valve 24, Can be seated and seated on the valve seat 42.  Alas, The spring-supported installation portion 21a in the hollow portion 21 of the first housing H1, A spring bearing 27 is installed. Spring bearing 27, It has a bottomed cylindrical shape and is provided with a threaded portion 27a on the outer periphery. This screw portion 27a can be screwed to a screw portion 21d provided in the hollow portion 21 of the first case H1, and can be attached to the first case H1. also, Spring bearing 27, The department has: The seal ring 43 is installed in a circumferential direction while avoiding the outer peripheral position of the screw portion 27a. When the spring support 27 is attached to the first case H1 as described above, Then, the seal ring 43 is in close contact with the inner periphery of the spring support installation portion 21a in the hollow portion 21, With spring support 27, The right end of the hollow portion 21 of the first case H1 in the fourth figure is locked in a liquid-tight state.  Between the spring support 27 and the right end of the valve body 24c of the first slide valve 24 in the fourth figure, The spring S is interposedly installed, By the urging force of the spring S, First spool valve 24, The valve body 24c is biased in a direction in which it is seated on the valve seat 42. So With the first slide valve 24 provided with the valve body 24c, And a first bushing 22 provided with a valve seat 42, And spring S, This constitutes a release valve RV. and, In a state where no external force is applied to the first spool valve 24 except the spring S, The valve body 24c is pressed against the valve seat 42 to close the valve, The opening pressure of the release valve RV is maximized. and, If a thrust force pressing the first spool valve 24 is applied in a direction to open the valve body 24c against the biasing force of the spring S, By adjusting the thrust, the urging force of the valve body 24c toward the valve seat 42 can be adjusted. The opening pressure of the release valve RV can be adjusted.  When the release valve RV is opened, Will be opened by: The fourth port 21m, Annular groove 22b, Through hole 22f, And the damping force adjustment path TP formed in the inner peripheral small diameter portion 22d. on the other hand, When the valve body 24c is seated on the valve seat 42 to close the release valve RV, The connection between the inner small diameter portion 22d and the inner large diameter portion 22c will be interrupted, The damping force adjustment path TP is blocked. also, In this example, Downstream pathway DP, By: Inner large diameter portion 22c, Through hole 22e, Annular groove 22a, And the first port 21i, As before, In the downstream channel DP, An orifice O is provided through the plug 50 installed due to the first through port 21i. also, As before, First port 21i, Is connected to the storage tank 6 located in the cylinder device C, The fourth port is 21m, It is connected to the rod-side chamber 4 located in the cylinder device C. therefore, Upstream of the damping force adjustment passage TP provided with a release valve RV, It is connected to the rod-side chamber 4 in the same manner as the cylinder device C shown in FIG. The downstream of the downstream channel DP is connected to the storage tank 6, By adjusting the opening pressure of the release valve RV, The damping force of the cylinder device C can be adjusted.  Alas, Between the spring S and the first slide valve 24, The intermediary is provided with a valve body-side spring support 44. In this example, The spring S is a coil spring, The right end of the valve body side spring support 44 in FIG. 4 is loosely fitted to the inner periphery of the spring S, The deflection of the shaft core of the spring S and the first spool valve 24 can be absorbed by the valve body side spring support 44. With this, Since the biasing force of the spring S acts on the first slide valve 24 without deviation in the radial direction, Therefore, the opening pressure of the first spool valve 24 is stabilized without unevenness.  Second spool valve 25, It is accommodated in the second bushing 23 and is guided to move in the axial direction. also, In Figure 4, The right end is abutted toward the left end of the first slide valve 24 in FIG. 4. Specifically, Second slide valve 25, The department has: The slide shaft portion 25a, which can be slidably inserted into the slide valve hole Sh of the second bushing 23, And a cylindrical valve portion 25b extending from the right end of the slide shaft portion 25a to the right in FIG. 4, And a convex portion 25c provided on the right end of the valve portion 25b in FIG. 4 and protruding in the axial direction.  Sliding shaft portion 25a, Is the slide valve hole Sh slidingly connected to the second bushing 23, The second bushing 23 is used to guide the axial movement of the second slide valve 25 without shaking the shaft.  Valve part 25b, Its outer diameter is set to a size that makes sliding contact with a slide valve hole Sh provided in the second bushing 23, When the right end is disposed more to the right than the inner peripheral large diameter portion 23e located in the spool hole Sh, The communication of the flow path formed by the through hole 23f and the spool valve hole Sh provided in the second bushing 23 is blocked.  Alas, At the rear end which is the left end in FIG. 4 as the sliding shaft portion 25a, Provided with flange 25d, Between the right end of the flange 25d in the fourth figure and the second bushing 23, The intermediary is provided with a coil spring 45. The second spool valve 25 is biased toward the left in FIG. 4 by the coil spring 45. In a state where no external force acts except the biasing force of the coil spring 45, Second slide valve 25, As shown in Figure 4, The valve portion 25b thereof is positioned in the inner peripheral large diameter portion 23e with respect to the second bushing 23, A flow path formed by the through hole 23f and the spool hole Sh is communicated.  And again, To the left of the second bushing 23 in FIG. 4, Equipped with Solenoid Sol, By energizing the solenoid Sol, The plunger 51 of the solenoid Sol applies a thrust force to the second spool valve 25 in the right direction in FIG. 4. also, By adjusting the amount of electricity to the solenoid Sol, The thrust applied to the second spool valve 25 can be adjusted. The thrust, Since the force against the coil spring 45 is applied to the second slide valve 25, Therefore, it is possible to make the second slide valve 25 resist the urging force of the coil spring 45 to move the front end of the valve portion 25 b toward the right side of the inner peripheral large diameter portion 23 e in the second bushing 23. therefore, By energizing the solenoid Sol, Moving the second spool valve 25 in the axial direction, Instead, the above-mentioned flow path can be connected or blocked. So Second bushing 23, Second slide valve 25, And coil spring 45, It is an on-off valve OV that opens and closes the flow path and is set to a normally open type. The on-off valve OV, This is a solenoid valve provided to open and close the flow path by energizing the solenoid Sol.  When the on-off valve OV is open, Will be caused by: Path 29, Valve hole 28, Fifth port 31, Third port 21k, Annular groove 23c, Through hole 23f, Spool valve hole Sh, Recessed 23g, And the fail-safe path FP constituted by the through hole 22h is in a connected state. Fail-safe path FP, Since it communicates with the inner peripheral large diameter portion 22c of the first bush 22, So the fail-safe path FP, Will merge with the damping force adjustment passage TP in the inner peripheral large diameter portion 22c, And connected to the downstream channel DP. When the fail-safe path FP is connected, The fail-safe valve FV provided in the valve hole 28 is also in a valve-openable state, When the pressure introduced from the fourth port 21m reaches the opening pressure of the fail-safe valve FV, the fail-safe valve FV will open, The pressure of the rod side chamber 4 can be discharged to the storage tank 6 through the fail-safe path FP and the downstream path DP. also, When the on-off valve OV is closed, The connection of the flow path formed by the through hole 23f and the spool hole Sh will be interrupted, The fail-safe path FP is brought into a blocking state.  Alas, By the amount of electricity from the solenoid Sol, The thrust applied to the second spool valve 25 can be adjusted, When the flow path closing valve is further brought into contact with the first slide valve 24 by the second slide valve 25, Then, the thrust of the electromagnetic coil Sol can also be transmitted to the first spool valve 24 through the second spool valve 25.  So, Since the thrust of the electromagnetic coil Sol in a direction opposing the spring S acts on the first spool valve 24, Therefore, by adjusting the energizing amount of the electromagnetic coil Sol, Can adjust the thrust of the first spool valve 24, The opening pressure of the release valve RV can be adjusted.  So, Attenuation valve DV, By applying to the cylinder device C, It functions as a source of attenuation force. and, In the damping valve DV in the present invention, An orifice O is provided downstream of the release valve RV. Orifice O, When the flow rate of the working oil passing through the orifice O fluctuates at a high frequency, It has the characteristics of hindering the change of the flow rate of the hydraulic oil. here, When the valve body of the release valve RV is suddenly opened and closed, Since the flow rate of the working oil passing through the downstream orifice O changes with high frequency vibration, Therefore, the orifice O has a function of suppressing the fluctuation of the flow rate. and, When the release valve RV is open, The back pressure acting on the valve body of the release valve RV will increase, Instead, When the release valve RV is closed, The back pressure acting on the valve body of the release valve RV will be reduced, This prevents the rapid opening and closing of the release valve RV. So Orifice O, It is a sudden opening and closing action that hinders the valve body of the release valve RV, A damping effect that makes the action proceed slowly. therefore, For a specific damping valve DV, When the damping force of the cylinder device C is controlled by the release valve RV, Even if pressure fluctuations occur in the rod-side chamber 4, The damping effect exerted by the orifice O can suppress the high-frequency vibration of the release valve RV. therefore, According to this specific damping valve DV, Can suppress the vibration of the release valve RV, For the damping force generated by the cylinder device C, the waveform will not be disturbed. Can improve the controllability of the shock absorption control of the vehicle body improved by the damping force adjustment, And can avoid the sudden change of the attenuation force and prevent the generation of strange sounds.  Alas, In the specific damping valve DV, Since the fail-safe path FP is provided with a fail-safe valve FV which resists the flow of the hydraulic oil, Therefore, the attenuation force characteristics at the time of failure can be adjusted according to the desired characteristics. And in the event of a failure, it can exert the attenuation force characteristics of the desired target.  Alas, In the specific damping valve DV, Have: A first case H1 (case H) having a hollow portion 21, And the first bushing 22 and the second bushing 23 inserted in the hollow portion 21 in series (in-line), And the first spool valve 24 housed in the first bushing 22, And a second slide valve 25 housed in the second bushing 23. also, The second bushing 23 is provided with: The flange 23b (positioning portion) for positioning the axial position relative to the first housing H1 (housing H), And a screw portion 23d (fixed portion) for fixing to the first case H1 (case H), And a slide valve hole Sh provided outside the range from the flange 23b (positioning portion) to the screw portion 23d (fixed portion). When the damping valve DV is configured in this way, To prevent a load having an axial load from acting on a portion of the second bushing 23 where the spool hole Sh is provided, Nor is it necessary to load the first bushing 22 accommodated in the hollow portion 21 with a tensile load or a compressive load in the axial direction, This prevents them from falling off. therefore, The inner peripheral shapes of the first bushing 22 and the second bushing 23 to receive the first spool valve 24 and the second spool valve 25, No strain. With this, No need for the first bushing 22, Second bushing 23, And the size of the first housing H1 is managed with high precision, It is not necessary to subject the inner peripheries of the first bushing 22 and the second bushing 23 to reshaping. The axial movement of the first spool valve 24 and the second spool valve 25 can also be guaranteed. With the above description, According to the damping valve DV, The first slide valve 24 and the second slide valve 25 can be smoothly processed while being easily processed.  Alas, In the damping valve DV in this example, Its spool valve Sh is set at: Relative to the second bushing 23, It is closer to the inside of the first case H1 (case H) than the flange 23b (positioning portion) and the screw portion 23d (fixed portion). When the damping valve DV is thus configured, The portion where the slide valve hole Sh of the second bushing 23 is provided can be accommodated in the first case H1 (case H), It is also possible to shorten the entire length of the damping valve DV.  Alas, The damping valve DV in this example, The axial length of the first bushing 22, It is set so as to be shorter than the axial length from the end surface of the second bushing 23 to the step portion 21 h in the hollow portion 21. therefore, Even if the second bushing 23 is attached to the first housing H1, The first bushing 22 will not be clamped by the second bushing 23 and the stage portion 21h in a compressed state. A state in which the axial force does not act on the first bushing 22 and the second bushing 23 can be reliably achieved. also, For the first bushing 22, Second bushing 23, And the size management of the first case H1 becomes easier.  And, In the damping valve DV in this example, Positioning section, For the flange 23b provided on the outer periphery of the second bushing 23, That is, the flange 23b abuts the end surface of the first case H1 (case H), The second bushing 23 is positioned relative to the first casing H1 (the casing H). When the damping valve DV is thus configured, With a simple structure, The second bushing 23 is positioned on the case H. also, When the flange 23b is fixed to the first case H1 with bolts, The flange 23b is used as a positioning part, It also functions as a fixed part, And the entire length of the second bushing 23 and even the entire length of the damping valve DV can be shortened. No load is required to act on the second bushing 23 and the first bushing 22, It is possible to more effectively prevent strain in the inner peripheral shape of both.  Alas, Orifice O, As long as it is set at: The damping force adjustment path TP and the fail-safe path FP to the downstream path DP of the storage tank 6 are sufficient. Therefore, it may be provided separately and separately from the case H.   the above, Although the preferred embodiment of the present invention has been described in detail, But as long as the substance does not exceed the scope of patent application, Is able to transform, Deformation, And changes.  案 This case, Claiming priority based on Japanese Patent Office 2016-176299 filed on September 9, 2016, The entire contents of the patent application are referred to in this patent specification.

1‧‧‧壓缸1‧‧‧Press Cylinder

2‧‧‧活塞2‧‧‧ Pistons

3‧‧‧桿3‧‧‧ par

4‧‧‧桿側室4‧‧‧ Rod side chamber

5‧‧‧活塞側室5‧‧‧Piston side chamber

6‧‧‧儲槽6‧‧‧ storage tank

7‧‧‧第一通路7‧‧‧ the first path

8‧‧‧第一卸載閥8‧‧‧ the first unloading valve

9‧‧‧第二通路9‧‧‧Second Access

10‧‧‧第二卸載閥10‧‧‧Second Unloading Valve

11‧‧‧整流通路11‧‧‧ Rectification Path

12‧‧‧吸入通路12‧‧‧ Inhalation pathway

13‧‧‧蓋體13‧‧‧ cover

14‧‧‧桿導14‧‧‧ Rod Guide

15‧‧‧孔口15‧‧‧ orifice

16‧‧‧彈簧16‧‧‧Spring

21‧‧‧中空部21‧‧‧Hollow

21a‧‧‧彈簧支承裝設部21a‧‧‧Spring support installation

21b‧‧‧襯套容納部21b‧‧‧ Bush housing

21c‧‧‧第二襯套裝設部21c‧‧‧Second lining set

21d‧‧‧螺紋部21d‧‧‧Thread

21e‧‧‧前端部21e‧‧‧Front end

21f‧‧‧中間部21f‧‧‧Middle

21g‧‧‧後端部21g‧‧‧Back end

21h‧‧‧階段部21h‧‧‧stage

21i‧‧‧第一通口21i‧‧‧First port

21j‧‧‧第二通口21j‧‧‧Second Port

21k‧‧‧第三通口21k‧‧‧The third port

21m‧‧‧第四通口21m‧‧‧Fourth port

22‧‧‧第一襯套22‧‧‧first bush

22a、22b‧‧‧環狀溝槽22a, 22b‧‧‧Annular groove

22c‧‧‧內周大徑部22c‧‧‧Inner circumference large diameter section

22d‧‧‧內周小徑部22d‧‧‧Inner circumference path

22e‧‧‧通孔22e‧‧‧through hole

22f‧‧‧通孔22f‧‧‧through hole

22g‧‧‧階段部22g‧‧‧stage

22h‧‧‧通孔22h‧‧‧through hole

23‧‧‧第二襯套23‧‧‧Second bush

23a‧‧‧套管23a‧‧‧ Casing

23b‧‧‧凸緣23b‧‧‧ flange

23c‧‧‧環狀溝槽23c‧‧‧Circular groove

23d‧‧‧螺紋部23d‧‧‧Thread

23e‧‧‧內周大徑部23e‧‧‧Inner circumference large diameter section

24‧‧‧第一滑閥24‧‧‧The first spool valve

24a‧‧‧滑動軸部24a‧‧‧ sliding shaft

24b‧‧‧小徑軸部24b‧‧‧Small diameter shaft

24c‧‧‧閥體24c‧‧‧Valve body

25‧‧‧第二滑閥25‧‧‧Second Spool Valve

25a‧‧‧滑動軸部25a‧‧‧ sliding shaft

25b‧‧‧閥部25b‧‧‧valve

25c‧‧‧凸部25c‧‧‧ convex

25d‧‧‧凸緣25d‧‧‧ flange

27‧‧‧彈簧支承27‧‧‧ spring bearing

28‧‧‧閥孔28‧‧‧Valve hole

29‧‧‧通路29‧‧‧ access

31‧‧‧第五通口31‧‧‧ fifth port

33‧‧‧栓33‧‧‧ suppository

34‧‧‧閥座34‧‧‧Valve seat

35‧‧‧閥體35‧‧‧Valve body

37‧‧‧蓋體37‧‧‧ Lid

38、39、40、41‧‧‧密封環38, 39, 40, 41‧‧‧ seal ring

42‧‧‧閥座42‧‧‧Valve seat

43‧‧‧密封環43‧‧‧sealing ring

44‧‧‧閥體側彈簧支承44‧‧‧ Valve body side spring bearing

45‧‧‧線圈彈簧45‧‧‧coil spring

50‧‧‧插栓50‧‧‧ plug

51‧‧‧柱塞51‧‧‧ plunger

60‧‧‧內周螺紋部60‧‧‧Inner peripheral thread

H‧‧‧殼體H‧‧‧shell

H1‧‧‧第一殼體H1‧‧‧First case

H2‧‧‧第二殼體H2‧‧‧Second shell

A、O‧‧‧孔口A, O‧‧‧ orifice

C‧‧‧壓缸裝置C‧‧‧cylinder device

DP‧‧‧下游通路DP‧‧‧ downstream channel

DV‧‧‧衰減閥DV‧‧‧ Attenuation Valve

FP‧‧‧故障安全通路FP‧‧‧Fail-safe path

FV‧‧‧故障安全閥FV‧‧‧Fail-safe valve

OV‧‧‧開閉閥OV‧‧‧Open and close valve

RV‧‧‧釋放閥RV‧‧‧ release valve

S‧‧‧彈簧S‧‧‧Spring

Sh‧‧‧滑閥孔Sh‧‧‧ sliding valve hole

Sol‧‧‧電磁線圈Sol‧‧‧ Solenoid Coil

TP‧‧‧衰減力調整通路TP‧‧‧ Attenuation Force Adjustment Path

第1圖，是具備有一實施形態中之衰減閥的壓缸裝置的液壓迴路圖。 　　第2圖，是顯示具備有一實施形態中之衰減閥的壓缸裝置其衰減力特性的圖面。 　　第3圖，是具備有一實施形態中之衰減閥的壓缸裝置其一變形例的液壓迴路圖。 　　第4圖，是具體之衰減閥的斷面圖。 　　第5圖，是具體之衰減閥其一變形例之一部分的斷面圖。Fig. 1 is a hydraulic circuit diagram of a cylinder device including a damping valve according to an embodiment. FIG. 2 is a view showing a damping force characteristic of a cylinder device including a damping valve according to an embodiment. Fig. 3 is a hydraulic circuit diagram of a modified example of the cylinder device including the damping valve according to the embodiment. Figure 4 is a sectional view of a specific damping valve. FIG. 5 is a cross-sectional view of a part of a specific modification of the damping valve.

Claims (4)

一種衰減閥，其特徵為，具備有： 　　衰減力調整通路、及 　　與上述衰減力調整通路並聯設置的故障安全通路、及 　　連接於上述衰減力調整通路與上述故障安全通路之下游的下游通路、及 　　設置於上述衰減力調整通路的釋放閥、及 　　設置於上述故障安全通路之常開型開閉閥、及 　　在通電時調節上述釋放閥的開閥壓並且關閉上述開閉閥的電磁線圈、以及 　　設置於上述下游通路的孔口。A damping valve, comprising: a damping force adjustment path, a fail-safe path provided in parallel with the damping force adjustment path, and a downstream path connected downstream of the damping force adjustment path and the fail-safe path, and A release valve provided on the damping force adjustment path, a normally open type on-off valve provided on the fail-safe path, and an electromagnetic coil that adjusts the opening pressure of the release valve and closes the on-off valve when power is applied, and is provided on the above The orifice of the downstream pathway. 如申請專利範圍第1項所述的衰減閥，其中， 　　具備有具有中空部的殼體， 　　上述釋放閥，具備有： 　　***於上述中空部並具備有上述衰減力調整通路之筒狀的第一襯套、及 　　可朝向軸向移動地容納於上述第一襯套內並具備有閥體能夠就座於設在上述第一襯套上的閥座之第一滑閥、 　　以及容納於上述中空部內並對上述第一滑閥，朝向使上述閥體就座於上述閥座的方向施力之彈簧； 　　上述開閉閥，具備有：與上述第一襯套串聯排列地***於上述中空部並具備有至少上述故障安全通路的一部分之筒狀的第二襯套、以及容納於上述第二襯套內並可於上述第二襯套中朝向軸向移動地被引導之第二滑閥； 　　上述第二襯套，具備有：將相對於上述殼體之軸向位置予以定位的定位部、及固定於上述殼體的固定部、以及供上述第二滑閥自由滑動地***於從上述第二襯套的上述定位部至上述固定部的範圍外的位置之滑閥孔， 　　上述電磁線圈，使第二滑閥朝向軸向移動並使上述開閉閥開閉，同時經由上述第二滑閥對上述第一滑閥施予推力來調節上述釋放閥的開閥壓。The damping valve according to item 1 of the patent application scope, wherein: is provided with a housing having a hollow portion, the release valve is provided with: a cylindrical first is inserted into the hollow portion and provided with the damping force adjustment passage A bush, and a first slide valve housed in the first bush so as to be axially movable and provided with a valve body capable of being seated on a valve seat provided on the first bush, and a housing, and housed in the hollow portion And a spring that biases the first slide valve in a direction in which the valve body is seated on the valve seat; the on-off valve includes: inserted in the hollow portion in series with the first bush and provided with: A cylindrical second bushing at least a part of the fail-safe path, and a second slide valve housed in the second bushing and guided in the second bushing so as to move axially; 第二 the second The bush includes a positioning portion for positioning an axial position with respect to the casing, a fixing portion fixed to the casing, and the second slide valve is freely slidable. The spool valve hole is inserted into a position outside the range from the positioning portion of the second bushing to the fixing portion, and the electromagnetic coil moves the second spool valve in the axial direction and opens and closes the on-off valve, while passing through the first Two slide valves apply thrust to the first slide valve to adjust the valve opening pressure of the release valve. 如申請專利範圍第1項所述的衰減閥，其中，於上述故障安全通路具備有對液體的流動給予抵抗的故障安全閥。The damping valve according to item 1 of the patent application scope, wherein the fail-safe passage is provided with a fail-safe valve that resists the flow of liquid. 一種壓缸裝置，其特徵為，具備有： 　　壓缸、及 　　可自由滑動地***於上述壓缸內的活塞、及 　　***於上述壓缸內並連結於上述活塞的桿、及 　　於上述壓缸內藉由上述活塞劃分的桿側室與活塞側室、及 　　儲槽、及 　　設置於將上述桿側室與上述活塞側室連通的第一通路並將上述第一通路予以開閉的第一卸載閥、及 　　設置於將上述活塞側室與上述儲槽連通的第二通路並將上述第二通路予以開閉的第二卸載閥、及 　　僅容許從上述活塞側室朝向上述桿側室流動的整流通路、及 　　僅容許從上述儲槽朝向上述活塞側室流動的吸入通路、及 　　衰減力調整通路、及 　　與上述衰減力調整通路並聯設置的故障安全通路、及 　　連接於上述衰減力調整通路與上述故障安全通路之下游的下游通路、及 　　設置於上述衰減力調整通路的釋放閥、及 　　設置於上述故障安全通路的常開型開閉閥、及 　　在通電時調節上述釋放閥的開閥壓同時關閉上述開閉閥的電磁線圈、以及 　　設置於上述下游通路的孔口； 　　且上述衰減力調整通路與上述故障安全通路的上游是往上述桿側室連接，上述下游通路是連接於上述儲槽。A cylinder device comprising: a cylinder and a piston slidably inserted into the cylinder; a rod inserted into the cylinder and connected to the piston; and a cylinder. A rod-side chamber, a piston-side chamber, and a storage tank divided by the piston, and a first unloading valve provided on a first passage that communicates the rod-side chamber with the piston-side chamber, and opening and closing the first passage, and a A second unloading valve that communicates with the piston-side chamber and the storage tank and opens and closes the second passage; a rectification path that allows flow only from the piston-side chamber to the rod-side chamber; The suction path through which the piston-side chamber flows, the damping force adjustment path, a fail-safe path provided in parallel with the damping force adjustment path, and a downstream path connected downstream of the damping force adjustment path and the fail-safe path, and provided at Release valve for the damping force adjustment path And a normally open on-off valve provided in the fail-safe path, an electromagnetic coil that adjusts the opening valve pressure of the release valve while closing the on-off valve while energizing, and an orifice provided in the downstream path; and the damping force An upstream of the adjustment path and the fail-safe path is connected to the rod-side chamber, and the downstream path is connected to the storage tank.
TW106130568A 2016-09-09 2017-09-07 Damping valve and cylinder device TW201812198A (en)

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