JPH0148401B2 - - Google Patents

Info

Publication number
JPH0148401B2
JPH0148401B2 JP59190443A JP19044384A JPH0148401B2 JP H0148401 B2 JPH0148401 B2 JP H0148401B2 JP 59190443 A JP59190443 A JP 59190443A JP 19044384 A JP19044384 A JP 19044384A JP H0148401 B2 JPH0148401 B2 JP H0148401B2
Authority
JP
Japan
Prior art keywords
oil
hydraulic
chamber
air
displacement member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
JP59190443A
Other languages
Japanese (ja)
Other versions
JPS60168902A (en
Inventor
Katsuhisa Yamaguchi
Kunio Yamaguchi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyooki Kogyo Co Ltd
Original Assignee
Toyooki Kogyo Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toyooki Kogyo Co Ltd filed Critical Toyooki Kogyo Co Ltd
Priority to JP59190443A priority Critical patent/JPS60168902A/en
Publication of JPS60168902A publication Critical patent/JPS60168902A/en
Publication of JPH0148401B2 publication Critical patent/JPH0148401B2/ja
Granted legal-status Critical Current

Links

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
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/072—Combined pneumatic-hydraulic systems
    • F15B11/0725—Combined pneumatic-hydraulic systems with the driving energy being derived from a pneumatic system, a subsequent hydraulic system displacing or controlling the output element
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/216—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being pneumatic-to-hydraulic converters
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3138—Directional control characterised by the positions of the valve element the positions being discrete
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/421—Flow control characterised by the type of actuation mechanically
    • F15B2211/423—Flow control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/47—Flow control in one direction only
    • F15B2211/473—Flow control in one direction only without restriction in the reverse direction
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Description

【発明の詳細な説明】 本発明は圧縮空気の圧力を油圧に変換する空油
変換器を用いて油圧アクチユエータの作動を行な
う空油制御装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a pneumatic-hydraulic control device that operates a hydraulic actuator using a pneumatic-hydraulic converter that converts compressed air pressure into hydraulic pressure.

従来、この種の空油制御装置は、実開昭53−
71199号公報に示される如く、油圧アクチユエー
タの往動室および復動室へ油室を連通する空油変
換器をそれぞれ備え、２個の空油変換器へ交互に
圧縮空気を供給することで変換油圧により油圧ア
クチユエータを作動している。そして、この繰り
返し作動において、油圧アクチユエータの往動室
と復動室間には油圧アクチユエータのピストンに
働く負荷に基因して圧力差が生じピストン摺動部
分を高圧側から低圧側へ作動油が漏出する。この
ため、長期間の作動で空油変換器の油室の油量が
許容値以上に増減して油圧アクチユエータの作動
不良をおこさないように、２個の空油変換器間に
開閉弁を設け、開閉弁の操作により空油変換器の
油室へ作動油を供給したり油室の作動油を排出し
たりして油量の修整が図れるようにしている。と
ころが、油量状態を目視し開閉弁を操作してお
り、修整作業が煩雑で、油量の最適な保守管理が
できない問題点があつた。 Conventionally, this type of air-hydraulic control device was developed in 1983.
As shown in Publication No. 71199, each of the hydraulic actuator is equipped with an air-oil converter that communicates the oil chamber with the forward movement chamber and the backward movement chamber, and the conversion is performed by alternately supplying compressed air to the two air-oil converters. The hydraulic actuator is operated by hydraulic pressure. During this repeated operation, a pressure difference is generated between the forward movement chamber and the backward movement chamber of the hydraulic actuator due to the load acting on the piston of the hydraulic actuator, and hydraulic oil leaks from the high pressure side to the low pressure side of the piston sliding area. do. For this reason, an on-off valve is installed between the two air-oil converters to prevent the oil level in the oil chamber of the air-oil converter from increasing or decreasing beyond the allowable value during long-term operation, causing malfunction of the hydraulic actuator. The oil amount can be adjusted by supplying hydraulic oil to the oil chamber of the air-oil converter or discharging the hydraulic oil from the oil chamber by operating the on-off valve. However, since the oil level condition was visually checked and the on-off valve was operated, the repair work was complicated and there were problems in that the oil level could not be maintained and managed optimally.

本発明は、かかる問題点を解決するもので、油
圧アクチユエータの作動毎に空油変換器の油室の
油量を最適に自動修整し得るようにした空油制御
装置を提供するものである。 The present invention solves this problem by providing an air-oil control device that can automatically adjust the amount of oil in the oil chamber of an air-oil converter to an optimum level each time a hydraulic actuator operates.

このため、本発明は、圧縮空気の供給排出によ
り軸方向へ変位自在にして変位部材を設け、変位
部材の一端部を内部に有して形成の作動油が充満
される油室を逆止弁を介し作動油を貯蔵する貯油
槽へ連通して貯油槽からの作動油の流入を許容し
て設け、変位部材の摺動する摺動部に油室を貯油
槽へ連通する流路を配設し、油室の作動油を吐出
するよう変位部材が軸方向の一方側へ変位すると
きには摺動部に配設の流路を変位部材により遮断
すると共に油室へ作動油が帰還するよう変位部材
が軸方向の他方側へ変位するときには変位端近傍
まで変位することで変位部材により遮断した摺動
部に配設の流路を連通するよう設けた空油変換器
を有し、油室より吐出される作動油によつて油圧
アクチユエータを往復動するよう油圧アクチユエ
ータの往動室に油室を連通する空油変換器と油圧
アクチユエータの復動室に油室を連通する空油変
換器とを設け、各空油変換器は油圧アクチユエー
タの作動油が油室に帰還する毎に貯油槽への流路
が連通する位置より他方側へ変位するよう変位部
材を設けて成る。 For this reason, the present invention provides a displacement member that is freely displaceable in the axial direction by supplying and discharging compressed air, and has one end portion of the displacement member inside and forms an oil chamber filled with hydraulic oil with a check valve. The oil chamber is connected to the oil storage tank that stores hydraulic oil through the oil storage tank, and is provided to allow the flow of hydraulic oil from the oil storage tank, and the sliding part on which the displacement member slides is provided with a flow path that communicates the oil chamber to the oil storage tank. However, when the displacement member is displaced to one side in the axial direction to discharge hydraulic oil from the oil chamber, the displacement member blocks the flow path provided in the sliding part and the displacement member is moved so that the hydraulic oil returns to the oil chamber. When the valve is displaced to the other side in the axial direction, the air-oil converter is disposed near the displacement end so that the flow path is communicated with the sliding part blocked by the displacement member, and discharge is discharged from the oil chamber. An air-oil converter that communicates an oil chamber with a forward movement chamber of the hydraulic actuator and an air-oil converter that communicates an oil chamber with a return movement chamber of the hydraulic actuator are provided so that the hydraulic actuator is reciprocated using hydraulic oil. , each air-oil converter is provided with a displacement member so as to be displaced from the position where the flow path to the oil storage tank communicates to the other side each time the hydraulic oil of the hydraulic actuator returns to the oil chamber.

かかる本発明の構成において、油圧アクチユエ
ータの往動室と復動室間の作動油漏出によつて増
加する空油変換器の油室の作動油は、油圧アクチ
ユエータの作動油が油室に帰還する毎に変位部材
が軸方向の他方側の変位端近傍へ変位することに
より流路を介して貯油槽へ排出する。また、油圧
アクチユエータの往動室と復動室間の作動油漏出
によつて作動油が減少する空油変換器の油室は、
変位部材の軸方向の他方側に向けての変位によつ
て内部が負圧状態となり逆止弁を介し貯油槽の作
動油が供給される。このため、油圧アクチユエー
タの作動毎に空油変換器の油室の油量を最適に自
動修整することができる。 In this configuration of the present invention, the hydraulic oil in the oil chamber of the air-oil converter that increases due to leakage of hydraulic oil between the forward movement chamber and the backward movement chamber of the hydraulic actuator is replaced by the hydraulic oil of the hydraulic actuator returning to the oil chamber. Each time, the displacement member is displaced to the vicinity of the displacement end on the other side in the axial direction, thereby discharging the oil into the oil storage tank via the flow path. In addition, the oil chamber of the air-oil converter, where the hydraulic oil decreases due to hydraulic oil leakage between the forward and reverse chambers of the hydraulic actuator,
Displacement of the displacement member toward the other side in the axial direction creates a negative pressure inside, and hydraulic oil from the oil storage tank is supplied through the check valve. Therefore, the amount of oil in the oil chamber of the air-oil converter can be automatically and optimally adjusted each time the hydraulic actuator operates.

以下、本発明の一実施例を図面に基づいて説明
する。 Hereinafter, one embodiment of the present invention will be described based on the drawings.

第１図において、１は油圧アクチユエータで、
ピストン２を摺動自在に収装して往動室３Ａと復
動室３Ｂを割成している。４Ａ，４Ｂは空油変換
器で、内部に異径の変位部材７Ａ，７Ｂを摺動自
在に収装して小径側に油室８Ａ，８Ｂを大径側に
空気室９Ａ，１０Ａ・９Ｂ，１０Ｂをそれぞれ割
成し、圧縮空気の作用力により変位部材７Ａ，７
Ｂを変位することで油室８Ａ，８Ｂの作動油を吐
出できるよう設けている。そして空油変換器４
Ａ，４Ｂは油室８Ａ，８Ｂに有する油流出入口６
Ａ，６Ｂを流路５Ａ，５Ｂを介し油圧アクチユエ
ータ１の往動室３Ａおよび復動室３Ｂへ連通して
おり、油室８Ａ，８Ｂからの吐出油量が油圧アク
チユエータ１のピストン２を往動側変位端から復
動側変位端までの間またはその逆の間、作動可能
に設けている。１１Ａ，１１Ｂは油室８Ａ，８Ｂ
と空気室１０Ａ，１０Ｂ間の変位部材７Ａ，７Ｂ
の小径部が摺動する孔に内周の一部を拡径して形
成した環状溝で、変位部材７Ａ，７Ｂが軸方向の
他方側としての反吐出側の変位端近傍へ変位した
際油室８Ａ，８Ｂと連通するように設けている。
１２Ａ，１２Ｂは作動油を貯蔵する貯油槽で、流
路１３Ａ，１３Ｂを介して環状溝１１Ａ，１１Ｂ
に連通している。１４Ａ，１４Ｂは空気抜きをす
るための開閉弁で、油室８Ａ，８Ｂと貯油槽１２
Ａ，１２Ｂ間を連通する流路に設けている。１５
Ａ，１５Ｂは逆止弁で、油室８Ａ，８Ｂと貯油槽
１２Ａ，１２Ｂ間を連通する流路に設け貯油槽１
２Ａ，１２Ｂから油室８Ａ，８Ｂへの油の流れを
許容するようにしている。１６Ａ，１６Ｂはエア
ブリーザ兼用の注油口である。１７は切換位置
Ａ，Ｎ，Ｂを有する電磁弁で、２個の空油変換器
４Ａ，４Ｂの空気室９Ａ，９Ｂへ流路１８Ａ，１
８Ｂを介して接続しており、流路１８Ａ，１８Ｂ
は分岐流路１９Ｂ，１９Ａを有して対設する空油
変換器４Ｂ，４Ａの空気室１０Ｂ，１０Ａにそれ
ぞれ連通している。２０は圧縮空気源、２１Ａ，
２１Ｂは消音器、２２Ａ，２２Ｂ，２３Ａ，２３
Ｂは逆止弁付の流量制御弁である。 In Fig. 1, 1 is a hydraulic actuator;
The piston 2 is slidably housed and divided into a forward movement chamber 3A and a backward movement chamber 3B. 4A and 4B are air-oil converters, in which displacement members 7A and 7B of different diameters are slidably housed, with oil chambers 8A and 8B on the small diameter side and air chambers 9A, 10A and 9B on the large diameter side. 10B, respectively, and the displacement members 7A, 7 are moved by the acting force of compressed air.
By displacing B, the hydraulic oil in the oil chambers 8A and 8B can be discharged. and air-oil converter 4
A, 4B are oil outflow inlets 6 in oil chambers 8A, 8B.
A, 6B are communicated with the forward motion chamber 3A and backward motion chamber 3B of the hydraulic actuator 1 via flow paths 5A, 5B, and the amount of oil discharged from the oil chambers 8A, 8B causes the piston 2 of the hydraulic actuator 1 to move forward. It is provided to be operable between the side displacement end and the return side displacement end or vice versa. 11A, 11B are oil chambers 8A, 8B
and the displacement members 7A, 7B between the air chambers 10A, 10B.
An annular groove is formed by enlarging a part of the inner circumference in the hole in which the small diameter part slides, and when the displacement members 7A and 7B are displaced to the vicinity of the displacement end on the opposite discharge side as the other side in the axial direction, the oil is removed. It is provided so as to communicate with chambers 8A and 8B.
12A and 12B are oil storage tanks for storing hydraulic oil, which are connected to annular grooves 11A and 11B via flow paths 13A and 13B.
is connected to. 14A and 14B are on-off valves for air venting, and oil chambers 8A and 8B and oil storage tank 12.
It is provided in the flow path that communicates between A and 12B. 15
Reference numerals A and 15B are check valves, which are installed in flow paths that communicate between the oil chambers 8A and 8B and the oil storage tanks 12A and 12B.
The oil is allowed to flow from the oil chambers 2A, 12B to the oil chambers 8A, 8B. Reference numerals 16A and 16B are oil fill ports that also serve as air breathers. Reference numeral 17 denotes a solenoid valve having switching positions A, N, and B, which connects flow paths 18A and 1 to the air chambers 9A and 9B of the two air-oil converters 4A and 4B.
8B, and the flow paths 18A, 18B
have branch passages 19B and 19A, and communicate with air chambers 10B and 10A of opposing air-oil converters 4B and 4A, respectively. 20 is a compressed air source, 21A,
21B is a silencer, 22A, 22B, 23A, 23
B is a flow control valve with a check valve.

次に、かかる構成の作動を説明する。図示状態
は電磁弁１７が中立の切換位置Ｎで、各流路１８
Ａ，１８Ｂを遮断しており、空油変換器４Ａの変
位部材７Ａは反吐出側の変位端に、空油変換器４
Ｂの変位部材７Ｂは吐出側の変位端に、油圧アク
チユエータ１のピストン２は往動室３Ａ側に位置
している。 Next, the operation of this configuration will be explained. In the illustrated state, the solenoid valve 17 is in the neutral switching position N, and each flow path 18
A, 18B are cut off, and the displacement member 7A of the air-oil converter 4A is connected to the displacement end of the air-oil converter 4A on the non-discharge side.
The displacement member 7B of B is located at the displacement end on the discharge side, and the piston 2 of the hydraulic actuator 1 is located on the forward movement chamber 3A side.

電磁弁１７を切換位置Ｂに操作すると、圧縮空
気源２０から圧縮空気は流路１８Ａを介して空油
変換器４Ａの空気室９Ａへ、さらに分岐流路１９
Ｂを介して流量制御弁２３Ｂで絞り制御され空油
変換器４Ｂの空気室１０Ｂへ供給される。また空
油変換器４Ａの空気室１０Ａの圧縮空気は流量制
御弁２３Ａの逆止弁と分岐流路１９Ａ流路１８Ｂ
を介して外部へ、空油変換器４Ｂの空気室９Ｂの
圧縮空気は流路１８Ｂを介して外部へ排出され
る。そして空油変換器４Ａの変位部材７Ａが空気
室９Ａの圧縮空気による作用力により環状溝１１
Ａと油室８Ａ間を遮断して吐出側へ変位し、油室
８Ａの作動油は変位部材７Ａの受圧面積差に応じ
て増圧され油流出入孔６Ａ流路５Ａ流量制御弁２
２Ａの逆止弁を介して油圧アクチユエータ１の往
動室３Ａへ供給されてピストン２を図示左方向へ
往動する。油圧アクチユエータ１の復動室３Ｂの
作動油は流量制御弁２２Ｂで絞り制御され流路５
Ｂ油流出入孔６Ｂを介して空油変換器４Ｂの油室
８Ｂへ帰環する。変位部材７Ｂは油室８Ｂへ帰還
する。作動油と空気室１０Ｂへ供給される圧縮空
気との作用力により反吐出側へ変位し、変位端近
傍で油室８Ｂを環状溝１１Ｂ流路１３Ｂを介して
貯油槽１２Ｂへ連通る。 When the solenoid valve 17 is operated to the switching position B, the compressed air from the compressed air source 20 passes through the flow path 18A to the air chamber 9A of the air-oil converter 4A, and then to the branch flow path 19.
The air is throttle-controlled by the flow rate control valve 23B and supplied to the air chamber 10B of the air-oil converter 4B. In addition, the compressed air in the air chamber 10A of the air-oil converter 4A is connected to the check valve of the flow control valve 23A and the branch flow path 19A flow path 18B.
The compressed air in the air chamber 9B of the air-oil converter 4B is discharged to the outside via the flow path 18B. Then, the displacement member 7A of the air-oil converter 4A is moved to the annular groove 11 by the acting force of the compressed air in the air chamber 9A.
The hydraulic oil in the oil chamber 8A is increased in pressure according to the pressure receiving area difference of the displacement member 7A, and the oil inlet/outlet hole 6A flow path 5A is displaced to the discharge side.
The piston 2 is supplied to the forward movement chamber 3A of the hydraulic actuator 1 through the check valve 2A, and moves the piston 2 forward in the left direction in the figure. The hydraulic fluid in the reciprocating chamber 3B of the hydraulic actuator 1 is throttle-controlled by the flow control valve 22B and flows through the flow path 5.
The B oil returns to the oil chamber 8B of the air-oil converter 4B via the oil inflow/outflow hole 6B. The displacement member 7B returns to the oil chamber 8B. It is displaced toward the opposite discharge side by the acting force of the hydraulic oil and the compressed air supplied to the air chamber 10B, and near the displacement end, the oil chamber 8B is communicated with the oil storage tank 12B via the annular groove 11B flow path 13B.

次に電磁弁１７を切換位置Ａに操作すると、流
路１８Ｂが圧縮空気源２０に流路１８Ａが外部に
切換え連通され、変位部材７Ａ，７Ｂおよびピス
トン２は前記と逆方向の作動を行なつて図示状態
になる。 Next, when the solenoid valve 17 is operated to the switching position A, the flow path 18B is switched to communicate with the compressed air source 20 and the flow path 18A is switched to the outside, and the displacement members 7A, 7B and the piston 2 operate in the opposite direction. The state shown is shown.

この作動において、いま、油圧アクチユエータ
１の復動時にピストン２へ負荷を働かせると、負
荷の大きさやピストン２両側の受圧面積差に基因
して復動室３Ｂの圧力が往動室３Ａの圧力よりも
高く成り、復動室３Ｂの作動油はピストン２両側
室間の圧力差によつてピストン２摺動部分を往動
室３Ａへ漏出する。この作動油漏出によつて増加
する空油変換器４Ａの油室８Ａの油量は、変位部
材７Ａを反吐出側へ変位するときその変位端近傍
で油室８Ａを環状溝１１Ａを連通しているため、
増加分の作動油が流路１３Ａを流れて貯油槽１２
Ａへ流出し修整される。また、前述油漏出により
作動油が減少する空油変換器４Ｂの油室８Ｂの油
量は、変位部材７Ｂを反吐出側へ変位するときそ
の変位部材７Ｂを空気室１０Ｂへ供給の圧縮空気
による作用力により強制変位しているため、減少
油量分に基因して油室８Ｂが負圧状態となり逆止
弁１５Ｂを介し貯油槽１２Ｂの作動油が供給する
と共に、変位部材７Ｂの反吐出側の変位端近傍で
油室８Ｂを環状溝１１Ｂへ連通して貯油槽１２Ｂ
の作動油が供給し修整される。 In this operation, when a load is applied to the piston 2 during the backward movement of the hydraulic actuator 1, the pressure in the backward movement chamber 3B becomes higher than the pressure in the forward movement chamber 3A due to the magnitude of the load and the difference in pressure receiving areas on both sides of the piston 2. The hydraulic fluid in the reciprocating chamber 3B leaks from the sliding portion of the piston 2 into the reciprocating chamber 3A due to the pressure difference between the chambers on both sides of the piston 2. The amount of oil in the oil chamber 8A of the air-oil converter 4A, which increases due to this hydraulic oil leakage, can be reduced by communicating the oil chamber 8A with the annular groove 11A near the displacement end when the displacement member 7A is displaced toward the opposite discharge side. Because there are
The increased amount of hydraulic oil flows through the flow path 13A to the oil storage tank 12.
It is leaked to A and corrected. In addition, the amount of oil in the oil chamber 8B of the air-oil converter 4B, where the hydraulic oil decreases due to the aforementioned oil leakage, is due to the compressed air supplied to the air chamber 10B when the displacement member 7B is displaced toward the opposite discharge side. Due to the forced displacement due to the acting force, the oil chamber 8B becomes a negative pressure state due to the reduced oil amount, and the hydraulic oil in the oil storage tank 12B is supplied via the check valve 15B, and the non-discharge side of the displacement member 7B The oil chamber 8B is communicated with the annular groove 11B near the displacement end of the oil storage tank 12B.
Hydraulic oil is supplied and repaired.

さらに、油圧アクチユエータ１の往動時にピス
トン２へ負荷を働かせ往動室３Ａと復動室３Ｂに
前述と逆の作動油増減が生じたときには、２個の
空油変換器４Ａ，４Ｂの同様な作用によつてその
増減が修整される。 Furthermore, when a load is applied to the piston 2 during the forward movement of the hydraulic actuator 1, and the hydraulic fluid increases or decreases in the forward movement chamber 3A and the backward movement chamber 3B in the opposite manner to that described above, the two air-oil converters 4A and 4B do the same. Its increase or decrease is corrected by action.

この結果、油圧アクチユエータ１の作動毎にピ
ストン２を往復動する２個の空油変換器４Ａ，４
Ｂの油室８Ａ，８Ｂの油量を最適に自動修整する
ことができて保守管理の簡素化が図れる。 As a result, the two air-oil converters 4A, 4 reciprocate the piston 2 every time the hydraulic actuator 1 operates.
The amount of oil in the oil chambers 8A and 8B of B can be automatically and optimally adjusted, and maintenance management can be simplified.

また、油圧アクチユエータ１のピストン２の往
復動長さを短かく変更する場合も、油圧アクチユ
エータ１の往動室３Ａと復動室３Ｂ間の作動油漏
出によつて増加する油室８Ａまたは８Ｂの作動油
は変位部材７Ａまたは７Ｂが反吐出側の変位端近
傍へ変位することにより貯油槽１２Ａまたは１２
Ｂへ排出できると共に、この作動油漏出によつて
作動油が減少する油室８Ｂまたは８Ａは内部の負
圧状態により逆止弁１５Ｂまたは１５Ａを介し貯
油槽１２Ｂまたは１２Ａの作動油が供給できるた
め、空油変換器４Ａ，４Ｂを変更することなく油
室８Ａ，８Ｂの油量を自動修正でき、油圧アクチ
ユエータ１を良好に作動することができる。開閉
弁１４Ａ，１４Ｂは装置の作動中閉じておき、油
室８Ａ，８Ｂ内に蓄積した空気を抜く際に開く。 Also, when changing the reciprocating length of the piston 2 of the hydraulic actuator 1 to a shorter length, the oil chamber 8A or 8B increases due to hydraulic oil leakage between the forward movement chamber 3A and backward movement chamber 3B of the hydraulic actuator 1. The hydraulic oil is transferred to the oil storage tank 12A or 12 by displacing the displacement member 7A or 7B to the vicinity of the displacement end on the anti-discharge side.
The oil chamber 8B or 8A, where the hydraulic oil decreases due to this hydraulic oil leakage, can be supplied with hydraulic oil from the oil storage tank 12B or 12A via the check valve 15B or 15A due to the internal negative pressure state. The amount of oil in the oil chambers 8A, 8B can be automatically corrected without changing the air-oil converters 4A, 4B, and the hydraulic actuator 1 can be operated satisfactorily. The on-off valves 14A, 14B are kept closed during operation of the device, and are opened when air accumulated in the oil chambers 8A, 8B is vented.

第２図は他の実施例で、第１図との相違点を主
に説明する。３１Ａ，３１Ｂは同径の変位部材
で、油室３２Ａ，３２Ｂと空気室３３Ａ，３３Ｂ
を割成しており、変位部材３１Ａ，３１Ｂは油室
３２Ａ，３２Ｂに収装したばね３４Ａ，３４Ｂ力
によつて空気室３３Ａ，３３Ｂ側へ強制変位する
と共に空気室３３Ａ，３３Ｂへ供給する圧縮空気
の作用力により、油室３２Ａ，３２Ｂ側へ変位自
在に収装している。３５Ａ，３５Ｂは油室３２
Ａ，３２Ｂと空気室３３Ａ，３３Ｂ間の変位部材
３１Ａ，３１Ｂが摺動する孔に内周の一部拡径し
て形成した環状溝で、変位部材３１Ａ，３１Ｂが
反吐出側の変位端へ変位した際、油室３２Ａ，３
２Ｂと連通するよう設けている。３６は貯油槽１
２Ａ，１２Ｂ間を連通する流路３７Ａ，３７Ｂは
流路１８Ａ，１８Ｂに設置した逆止弁付の流量制
御弁で、空気室３３Ａ，３３Ｂから外部へ排出す
る空気を制御する。 FIG. 2 shows another embodiment, and the differences from FIG. 1 will be mainly explained. 31A, 31B are displacement members of the same diameter, and oil chambers 32A, 32B and air chambers 33A, 33B.
The displacement members 31A, 31B are forcibly displaced toward the air chambers 33A, 33B by the force of springs 34A, 34B housed in the oil chambers 32A, 32B, and compressed air is supplied to the air chambers 33A, 33B. It is housed so that it can be freely displaced toward the oil chambers 32A and 32B by the action of air. 35A and 35B are oil chambers 32
A, 32B and the air chambers 33A, 33B between the displacement members 31A, 33B is an annular groove formed in the hole in which the displacement members 31A, 31B slide, by enlarging a part of the inner circumference, and the displacement members 31A, 31B move to the displacement end on the anti-discharge side. When displaced, the oil chambers 32A, 3
It is installed to communicate with 2B. 36 is oil storage tank 1
Flow paths 37A and 37B communicating between 2A and 12B are flow control valves with check valves installed in flow paths 18A and 18B to control the air discharged from the air chambers 33A and 33B to the outside.

この構成において、２個の空油変換器４Ａ，４
Ｂの変位部材３１Ａ，３１Ｂは電磁弁１７によつ
て空気室３３Ａ，３３Ｂへ圧縮空気が供給された
り、空気室３３Ａ，３３Ｂの圧縮空気が外部に排
出されたりすることで、圧縮空気の作用力とばね
３４Ａ，３４Ｂ力との対向作用により変位され、
油圧アクチユエータ１へ吐出する油圧は空気室３
３Ａ，３３Ｂへ供給される圧縮空気の圧力と同圧
である。そして流路３６によつて貯油槽１２Ａ，
１２Ｂ間が連通しているため、貯油槽１２Ａと１
２Ｂ間の油量を修整ることができる。 In this configuration, two air-oil converters 4A, 4
The displacement members 31A and 31B of B are supplied with compressed air to the air chambers 33A and 33B by the solenoid valve 17, and the compressed air in the air chambers 33A and 33B is discharged to the outside, so that the acting force of the compressed air is reduced. is displaced by the opposing action of the springs 34A and 34B,
The hydraulic pressure discharged to the hydraulic actuator 1 is supplied to the air chamber 3.
This is the same pressure as the compressed air supplied to 3A and 33B. The oil storage tank 12A,
Since 12B are in communication, oil storage tanks 12A and 1
The amount of oil between 2B can be adjusted.

このように本発明は、圧縮空気の供給排出によ
り軸方向へ変位自在にして変位部材を設け、変位
部材の一端部を内部に有して形成の作動油が充満
される油室を逆止弁を介し作動油を貯蔵する貯油
槽へ連通して貯油槽からの作動油の流入を許容し
て設け、変位部材の摺動する摺動部に油室を貯油
槽へ連通する流路を配設し、油室の作動油を吐出
するよう変位部材が軸方向の一方側へ変位すると
きには摺動部に配設の流路を変位部材により遮断
すると共に油室へ作動油が帰還するよう変位部材
が軸方向の他方側へ変位するときには変位端近傍
まで変位することで変位部材により遮断した摺動
部に配設の流路を連通するよう設けた空油変換器
を有し、油室より吐出される作動油によつて油圧
アクチユエータを往復動するよう油圧アクチユエ
ータの往動室に油室を連通する空油変換器と油圧
アクチユエータの復動室に油室を連通する空油変
換器とを設け、各空油変換器は油圧アクチユエー
タの作動油が油室に帰還する毎に貯油槽への流路
が連通する位置より他方側へ変位するよう変位部
材を設けたことにより、油圧アクチユエータの作
動毎に空油変換器の油室の油量を最適に自動修整
することができて保守管理の簡素化が図れる。 In this way, the present invention provides a displacement member that is freely displaceable in the axial direction by supplying and discharging compressed air, and has one end of the displacement member inside and forms an oil chamber filled with hydraulic oil as a check valve. The oil chamber is connected to the oil storage tank that stores hydraulic oil through the oil storage tank, and is provided to allow the flow of hydraulic oil from the oil storage tank, and the sliding part on which the displacement member slides is provided with a flow path that communicates the oil chamber to the oil storage tank. However, when the displacement member is displaced to one side in the axial direction to discharge hydraulic oil from the oil chamber, the displacement member blocks the flow path provided in the sliding part and the displacement member is moved so that the hydraulic oil returns to the oil chamber. When the valve is displaced to the other side in the axial direction, the air-oil converter is disposed near the displacement end so that the flow path is communicated with the sliding part blocked by the displacement member, and discharge is discharged from the oil chamber. An air-oil converter that communicates an oil chamber with a forward movement chamber of the hydraulic actuator and an air-oil converter that communicates an oil chamber with a return movement chamber of the hydraulic actuator are provided so that the hydraulic actuator is reciprocated using hydraulic oil. , each air-oil converter is provided with a displacement member so that it is displaced from the position where the flow path to the oil storage tank communicates to the other side every time the hydraulic oil of the hydraulic actuator returns to the oil chamber. The amount of oil in the oil chamber of the air-oil converter can be automatically adjusted to the optimum level, simplifying maintenance management.

また、油圧アクチユエータの往復動長さを短か
く変更する場合も、油圧アクチユエータの往動室
と復動室間の作動油漏出によつて増加する油室の
作動油は変位部材が軸方向の他方側の変位端近傍
へ変位することにより貯油槽へ排出できると共
に、この作動油漏出によつて作動油が減少する油
室は内部の負圧状態により逆止弁を介し貯油槽の
作動油が供給できるため、空油変換器を変更する
ことなく各油室の油量を自動修整でき、油圧アク
チユエータを良好に作動することができる効果を
有する。 Also, when changing the reciprocating length of the hydraulic actuator to a shorter length, the hydraulic fluid in the oil chamber that increases due to leakage of hydraulic fluid between the forward and backward chambers of the hydraulic actuator is increased when the displacement member is axially The hydraulic oil can be discharged to the oil storage tank by being displaced near the side displacement end, and the oil chamber, where the hydraulic oil decreases due to this hydraulic oil leakage, is supplied with hydraulic oil from the oil storage tank via the check valve due to the internal negative pressure state. Therefore, the oil amount in each oil chamber can be automatically adjusted without changing the air-oil converter, and the hydraulic actuator can be operated satisfactorily.

【図面の簡単な説明】[Brief explanation of drawings]

図面は本発明の実施例を一部断面で示した回路
図で、第１図は一実施例、第２図は他の実施例で
ある。 １…油圧アクチユエータ、３Ａ…往動室、３Ｂ
…復動室、４Ａ，４Ｂ…空油変換器、７Ａ，７
Ｂ，３１Ａ，３１Ｂ…変位部材、８Ａ，８Ｂ，３
２Ａ，３２Ｂ…油室、１２Ａ，１２Ｂ…貯油槽。 The drawings are circuit diagrams partially showing an embodiment of the present invention in cross section, with FIG. 1 showing one embodiment and FIG. 2 showing another embodiment. 1... Hydraulic actuator, 3A... Forward movement chamber, 3B
... Double action chamber, 4A, 4B... Air-oil converter, 7A, 7
B, 31A, 31B...displacement member, 8A, 8B, 3
2A, 32B...Oil chamber, 12A, 12B...Oil storage tank.

Claims (1)

【特許請求の範囲】[Claims] １ 圧縮空気の供給排出により軸方向へ変位自在
にして変位部材を設け、変位部材の一端部を内部
に有して形成の作動油が充満される油室を逆止弁
を介し作動油を貯蔵する貯油槽へ連通して貯油槽
からの作動油の流入を許容して設け、変位部材の
摺動する摺動部に油室を貯油槽へ連通する流路を
配設し、油室の作動油を吐出するよう変位部材が
軸方向の一方側へ変位するときには摺動部に配設
の流路を変位部材により遮断すると共に油室へ作
動油が帰還するよう変位部材が軸方向の他方側へ
変位するときには変位端近傍まで変位することで
変位部材により遮断した摺動部に配設の流路を連
通するよう設けた空油変換器を有し、油室より吐
出される作動油によつて油圧アクチユエータを往
復動するよう油圧アクチユエータの往動室に油室
を連通する空油変換器と油圧アクチユエータの復
動室に油室を連通する空油変換器とを設け、各空
油変換器は油圧アクチユエータの作動油が油室に
帰還する毎に貯油槽への流路が連通する位置より
他方側へ変位するよう変位部材を設けて成る空油
制御装置。1. A displacement member is provided that is freely displaceable in the axial direction by the supply and discharge of compressed air, and an oil chamber filled with hydraulic oil is formed with one end of the displacement member inside, and the hydraulic oil is stored through a check valve. A flow path communicating the oil chamber to the oil storage tank is provided in the sliding part of the displacement member to allow hydraulic oil to flow in from the oil storage tank. When the displacement member is displaced to one side in the axial direction to discharge oil, the displacement member blocks the flow path provided in the sliding part, and the displacement member is moved to the other side in the axial direction so that the hydraulic oil returns to the oil chamber. It has an air-oil converter installed so that the flow path connected to the sliding part blocked by the displacement member is communicated with the sliding part when it is displaced to the vicinity of the displacement end, and the hydraulic fluid discharged from the oil chamber is used. A pneumatic-hydraulic converter that communicates an oil chamber with a forward movement chamber of the hydraulic actuator and a pneumatic-hydraulic converter that communicates an oil chamber with a backward movement chamber of the hydraulic actuator are provided so that the hydraulic actuator reciprocates. An air-oil control device comprising a displacement member so as to be displaced from a position where a flow path to an oil storage tank communicates to the other side each time hydraulic oil of a hydraulic actuator returns to an oil chamber.
JP59190443A 1984-09-10 1984-09-10 Air-oil control device Granted JPS60168902A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP59190443A JPS60168902A (en) 1984-09-10 1984-09-10 Air-oil control device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP59190443A JPS60168902A (en) 1984-09-10 1984-09-10 Air-oil control device

Publications (2)

Publication Number Publication Date
JPS60168902A JPS60168902A (en) 1985-09-02
JPH0148401B2 true JPH0148401B2 (en) 1989-10-19

Family

ID=16258216

Family Applications (1)

Application Number Title Priority Date Filing Date
JP59190443A Granted JPS60168902A (en) 1984-09-10 1984-09-10 Air-oil control device

Country Status (1)

Country Link
JP (1) JPS60168902A (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0527684Y2 (en) * 1987-01-22 1993-07-15

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5082482A (en) * 1973-11-26 1975-07-03
JPS5089906A (en) * 1973-11-16 1975-07-18

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5089906A (en) * 1973-11-16 1975-07-18
JPS5082482A (en) * 1973-11-26 1975-07-03

Also Published As

Publication number Publication date
JPS60168902A (en) 1985-09-02

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