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EP0089881A2 - Druckluftspareinrichtung - Google Patents

Druckluftspareinrichtung Download PDF

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Publication number
EP0089881A2
EP0089881A2 EP83400524A EP83400524A EP0089881A2 EP 0089881 A2 EP0089881 A2 EP 0089881A2 EP 83400524 A EP83400524 A EP 83400524A EP 83400524 A EP83400524 A EP 83400524A EP 0089881 A2 EP0089881 A2 EP 0089881A2
Authority
EP
European Patent Office
Prior art keywords
valve
fluid
piston
pressure
action
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.)
Granted
Application number
EP83400524A
Other languages
English (en)
French (fr)
Other versions
EP0089881A3 (en
EP0089881B1 (de
Inventor
Yves Levenez
André Legris
Daniel Bouteille
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.)
Legris SA
Original Assignee
Legris SA
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
Priority claimed from FR8205042A external-priority patent/FR2523659A1/fr
Priority claimed from FR8303513A external-priority patent/FR2542043B2/fr
Application filed by Legris SA filed Critical Legris SA
Publication of EP0089881A2 publication Critical patent/EP0089881A2/de
Publication of EP0089881A3 publication Critical patent/EP0089881A3/fr
Application granted granted Critical
Publication of EP0089881B1 publication Critical patent/EP0089881B1/de
Expired legal-status Critical Current

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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
    • 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
    • F15B11/064—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam with devices for saving the compressible medium
    • 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
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F15B2211/50527—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves using cross-pressure relief valves
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • 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
    • F15B2211/75—Control of speed of the output member

Definitions

  • the present invention relates to a compressed air saver device.
  • the cylinders are oversized in relation to the load they have to move, in order to meet the criteria of speed of movement and mechanical resistance and, as a result, this results in a higher consumption of compressed air than 'it would only be necessary to move said load.
  • FIG. 1 there is shown the pressure curve A of pressure P as a function of the time T of displacement of the piston of the jack, the pressure level of the network being indicated in B and the end of stroke of the piston being indicated in C.
  • FIG. 16 shows a curve D of pressure as a function of time for the same cylinder equipped with an exhaust flow limiter and a curve E for the same cylinder equipped with a supply flow limiter .
  • the air consumption will be the same whether or not the cylinder is equipped with a flow limiter reducing the speed of the piston.
  • a device according to the invention is used.
  • the device comprises a means ensuring the passage of the working fluid under pressure during most of the stroke of the movable member of the jack and closing said passage of fluid under pressure before or at the end of the stroke of said movable member.
  • FIG. 1c shows the curve F of pressure with respect to the displacement time of the piston of the same cylinder as in FIGS. 1a and 1b, this curve F corresponding to a jack fitted with an air saving device according to the invention in which the flow of compressed air is cut towards the driving chamber of the jack, either before or at the end of travel C of the piston of the jack.
  • This arrangement allows, as can be seen in the figure, to save the volume of compressed air unnecessarily used resulting from the difference between the pressure B of the compressed air distribution network and the driving pressure sufficient to bring the piston at the end of race under the necessary speed and downforce conditions.
  • FIG. Id there is shown a pressure / time curve G of the same cylinder equipped with an economizer device according to the invention and comprising a means of speed limitation of the piston. This arrangement allows savings to be made the greater the lower the speed.
  • the economizer device according to the invention is preferably arranged between the orifice of the jack and the outlet of the dispenser, as close as possible to the latter.
  • the invention comprises a non-return device capable of allowing the exhaust air of the jack to pass at full flow when the movable member returns.
  • the valve is closed under the pressure of the working fluid.
  • FIGS 2 and 3 there is shown a cylinder 1 which is connected to a pneumatic distributor 2 by means of a compressed air saver device 3 according to the invention, said double-acting cylinder 1 comprising a cylinder in which moves a piston 4 connected by a rod 5 to a load to be moved. Furthermore, the distributor 2 is capable of putting said cylinder in communication with a network 6 for distributing compressed air and with a purge orifice 7 opening to the atmosphere.
  • the air saver device 3 comprises a body 8 in which are mounted two economizer assemblies which are connected respectively by conduits 9, 9a to the chambers 10, 10a of the jack 1, each assembly comprising a valve 11, 11a mounted slidingly with interposition of 'A seal 12, 12a in a bore 13, 13a formed in the body 8, said valve having at one of its ends forming a shutter member a seal 14, 14a which is capable of closing an orifice 15, 15a of a seat 16, 16a mounted to slide in a housing 17, 17a in communication via a conduit 18, 18a with the distributor 2.
  • the valves 11, 11a comprise a piston 19, 19a provided with a seal 20, 20a and moving in a cylinder 21, 21a formed in the body 8, said piston being subjected on its upper face to the action of a spring 22, 22a, one end of which bears against the end of a screw 23, 23a engaged in a tapped hole 24, 24a provided in the body 8 to the upper part of the cylinders 21, 21a.
  • the spring 22, 22a tends to push the valve 11, lla against the seat 16, 16a.
  • the driving chamber 10 is supplied with working fluid P1 under pressure by the conduits 9 and 27, the orifice 15 of the seat 16 (the valve 11 being in the open position), the conduit 18 and the distributor 2 which is connected to the distributor network 6 of compressed air at pressure P.
  • the chamber 10a of the jack 1 being in the air purge position, there occurs in said chamber a back pressure P2, so that the air flows through the conduits 9a, 27a, the orifice 15a (the valve 11a being in the open position), the conduit 18a and the distributor 2 which is connected to the atmosphere at 7.
  • the conduit 27 being connected by the conduit 26a to the chamber 29a located under the piston 19a, the driving pressure P1 exerts on said piston a force against the spring 22a, which is compressed, thus ensuring the opening of the valve 11a allowing the passage of the exhaust fluid at the back pressure P2 towards the distributor 2 and towards the atmosphere at 7.
  • the hardness of the springs 22, 22a is adjusted by compressing them by means of the screws 23, 23 ! , from a certain compression of the springs 22, 22a the device operates as a pressure reducer.
  • FIGS. 4 and 5 show an alternative embodiment of the economizer device in which the force required for closing the valve when the exhaust backpressure disappears is no longer supplied by the spring 22, 22a but by the engine fluid pressure P1.
  • the piston 19, 19a is extended by a part 30, 30a of smaller section than the piston 19, 19a and moving in a cylindrical housing 31, 31a.
  • valve 11, 11a has an axial channel 32, 32a opening at its upper part into the space 31, 31a and at its lower part in the conduit 27.
  • This arrangement makes it possible to bring the working fluid P1 into the space 31 (FIG. 4) where its pressure on the part 30 of the piston 19 is exerted against the pressurized fluid located in the chamber 29 under the piston 19 ; however, the section of the part 30 being smaller than that of the piston 19 subjected to the pressure of the exhaust fluid P2, the valve 11 is maintained in the open position against the screw 23 which makes it possible to reduce the flow rate at will and, consequently , the speed of the jack; the air consumption being lower the lower the speed.
  • a chamber 33, 33a situated above the piston 19, 19a is connected by a conduit 34, 34a to a cell 35, 35a or limit switch supplied from a conduit 36, 36a and d a distributor 37, 37a selectively connecting the cell to a source of pressurized fluid and to the atmosphere.
  • the cells 35, 35a have a feeler 38, 38a capable of coming into contact with a part 39 of the rod 5 of the piston 4, so that when the cell 35, 35a is actuated it sends a pneumatic signal to the chamber 33, 33a which pushes the piston 19, 19a downwards and ensures the closing of the valve 11, lla.
  • the chamber 33a also being unpressurized and the valve being in the open position, the fluid at pressure P2 escapes from the chamber 10a of the jack via the duct 27a and the distributor 2.
  • the screws 23, 23a make it possible to adjust the flow rate of fluid and, consequently, the speed of the piston 4 of the jack.
  • the cell 35, 35a or end of stroke sensor can be replaced by a sensor for the passage of the movable member or piston 4 of the jack.
  • a pneumatic signal is used coming from a circuit associated with the movement of another jack triggering immediately after the end of the stroke of the piston of the control jack.
  • a compressed air saving device which comprises a body 41 mounted between a distributor 42 and a base 43 with which it is in contact by two of its faces 44 and 45, said base 43 having integrated channels including a channel 46 connected to the compressed air distributor, channels 47, 47a connected to the atmosphere and channels 48, 48a connected to the chambers 10, 10a of the jack 1.
  • Channels 46, 47, 47a , 48, 48a of fluid open onto one of the faces 45 of the body 41 which has on its other face 44 orifices opening into the conduits of the distributor 42.
  • a sleeve 49, 49a having a cylinder closed by a screw cap 50, 50a and in which is slidably mounted a piston 51, 51a of a valve 11, lla having a shutter member or joint 52, 52a capable of closing a hole 53, 53a.
  • the piston 51 is subjected on one of its faces to the action of a spring 54, 54a which maintains the valves 11, lla in the open position, in the absence of pressurized fluid.
  • the body 41 comprises a duct 55, 55a in which is mounted a non-return valve 56, 56a subjected to the action of a spring 57, 57a which only ensures the passage of the chambers 10, 10a towards the exhaust 47, 47a.
  • Said conduit 55, 55a is in communication on one side of the valve 56, 56a through the orifice 53, 53a with a chamber 58, 58a and on the other side of the valve by an orifice 59, 59a.
  • the valve 11, lla has an axial duct 61, 61a putting the chamber 58, 58a in communication with the chamber 62, 62a and a duct 63, 63a connects the duct 55, 55a to a chamber 64, 64a placed under the piston 51, 51a.
  • FIG. 9 an alternative embodiment of the economizer device is shown, the body 41 of which is mounted in the same manner as in FIG. 8 between the distributor 42 and the base 43.
  • the piston 51, 51a is not connected to the chamber 58, 58a and the plug 50, 50a has a conduit 66, 66a which is connected in particular to a position sensor of the piston 4 before or at the end of the stroke which delivers in the chamber 62, 62a a pneumatic signal or a certain quantity of fluid which pushes the piston 51 and the valve 11, 11a into the closed position.
  • FIG. 10 shows an alternative embodiment of the double compressed air economizer device, the body 41 of which is mounted in the same manner as in FIG. 8 between the distributor 42 and the base 43.
  • a valve 67, 67a subjected to the action of a spring 79, 79a is held in the open position relative to the orifice 68, 68a which connects the conduits 69, 69a leading to the chambers 10 and 10a of the jack and the conduits 70, 70a selectively connected by the distributor 42 to the compressed air network and to the atmosphere.
  • the valve 67, 67a comprises a rod 71, 71a which is mounted to slide freely in a blind hole in the piston 72, 72a which moves in a cylinder provided in a jacket 73, 73a mounted in leaktight manner in the body 41, said piston 72 , 72a being subjected on its face of larger section to the action of a spring 74, 74a pressing against a sleeve 75, 75a screwed into the jacket 73, 73a, said sleeve being capable of being actuated by a plug 76 , 76a in order to adjust the pressure of the spring 74, 74a.
  • chambers 77, 77a are connected to the conduits 70. 70a by conduits 78, 78a.
  • valve 67a When the chamber 10a is supplied with working fluid through the conduits 70a and 69a, the valve 67a is in the open position pushed back by the piston 72a on which the spring 74a and the exhaust pressure act in the chamber 77a against the action of the working fluid acting on the smallest section of the piston on the opposite face.
  • the spring 74a is compressed under the action of the pressure of the working fluid and the piston 72a moves against the sleeve 75a thus allowing the valve 67a under the action of the pressure of the working fluid to close off the orifice 6 8a and to interrupt the passage of the working fluid between the conduits 70a and 69a towards the motor chamber 10a.
  • the exhaust fluid coming from the chamber 10 passes through the conduits 69 and 70, the valve 67 being in the open position, and goes via the distributor 42 towards the exhaust channel 47.
  • FIG. 11 there is shown an economizer device the body 41 of which is mounted between a distributor 42 and a base 43 as shown in FIG. 8.
  • the device is identical to that of FIG. 10, however , the plugs 76, 76a have conduits 80; 80a which are connected to position sensors of the piston 4 before or at the end of the stroke which deliver a pneumatic signal.
  • the piston 72, 72a is extended by a rod 81, 81a extending through the sleeve 75, 75a and in the plug 76, 76a, said rod 81, 81a having a conduit 82, 82a in communication on one side with the conduit 80, 80a and on the other with the chamber 83, 83a disposed under the piston 72.
  • a pneumatic signal is emitted at one of the ends and transmitted by the conduits 80, 80a and 82, 82a the piston 72, 72a is raised against the spring 74, 74a, so that the valve 67, 67a closes under the action of the pressure of the working fluid coming from the conduit 70, 70a.
  • FIG. 12 there is shown an economizer device which comprises a double connector body consisting of two elements 84, 84a in the shape of a T. connected together by a rib 85 and arranged with their parallel axes.
  • Each element 84, 84a of the body (FIG.
  • conduits 86, 86a for circulation of the fluid which are provided with connection means 87, 87a with external pipes, said element of the body having in its central part a bore 88 perpendicular to conduits 86, 86a and in which is mounted a valve 89 which comprises a shutter member 90 integral with a piston 91 slidably mounted in a cylinder provided on one side of bore 88 and closed by a plug 92 against which bears one end of a spring 93, the other end of which acts in combination with the exhaust pressure against the piston 91.
  • Figure 14 it is possible to replace the plug 92 by a sealing sleeve 97 mounted in the bore 88 and having a threaded hole in which is screwed the threaded part of a rod 98 ensuring the adjusting the tension of the spring 93 which acts on the piston 91 in order to vary the outlet pressure.
  • the rod 98 is extended by an operating head 99 comprising colored rings 100 enabling the economy to be viewed.
  • FIGS. 15 and 16 show an alternative embodiment of an economizer device which comprises a double connector body 101 in the form of a compact block and which contains two economizer assemblies identical to that represented in FIG. 12 and which has been described below. -above.
  • FIG. 17 represents a setting sleeve 97 which can be mounted to replace the plug 92 for adjusting the spring 93 and the fluid outlet pressure.
  • an economizer device which comprises a double connector body consisting of two elements 84, 84a in the form of T, connected together by a rib 85 and arranged with their parallel axes.
  • Each element 84, 84a of the body has at its two ends conduits 86, 86a for circulation of the fluid which are provided with connection means 87, 87a with external pipes, said element having in its central part a bore 102 perpendicular to the conduits 86, 86a.
  • a plug 103 against which a spring 104 pushes against a valve 105 controlling the passage of the working and exhaust fluid, said valve 105 being extended by a rod 106 slidably mounted in a blind hole of a piston 107 sliding in the bore 102, said piston being subjected on one of its faces to the action of a spring 108 bearing against an adjustment plug 109 screwed into the central bore and the action of the exhaust fluid.
  • FIG. 20 an energy-saving device which comprises a simple connector 110 enclosing a valve 111 for controlling the passage of the fluid and having an orifice 112 connected by a conduit 113 to a chamber 10 of a jack 1 and a conduit 114 connected to a distributor 115 capable of bringing said chamber 10 into communication with a source of pressurized fluid and the atmosphere.
  • the other chamber 10a of the jack is connected by a conduit 116 directly to the distributor 115, but it would obviously be possible to mount on the conduit 116 a simple connector identical to the connector 110 which includes an economizer device.
  • the connector 110 comprises a main body 117 having at its base a threaded portion 130 for mounting in a tapped hole of a support or connection member, or of the distributor 115, said body 117 containing a valve 111 for controlling the passage of fluid controlled by a piston 118 subjected to the action of a pneumatic signal or of a certain quantity of fluid directed into a chamber 119 formed between the upper part of the piston and a plug 120 screwed into a tapped part of the body 117, said plug being pierced with a conduit 121 connected by a conduit 122 to a sensor 123 of the position of the piston 4 of the jack.
  • a movable seat 124 which is pushed against a shoulder of the body and against the valve shutter member by a spring 125.
  • the main body 117 receives a socket 126 comprising a tube 127 putting the conduit 113 in communication with the conduit 114 through the space between the valve 111 and the main body through the orifice 128 and through the conduit 112 of the tube 127.
  • a socket 126 comprising a tube 127 putting the conduit 113 in communication with the conduit 114 through the space between the valve 111 and the main body through the orifice 128 and through the conduit 112 of the tube 127.
  • the piston 4 As soon as the piston 4 reaches the end of the stroke or before the end of the stroke, it acts on the sensor 123 which sends a pneumatic signal in the chamber 119 pushing the piston 118 downwards and the valve 111 against the seat 124 thus closing the passage to the chamber 10 whose supply of working fluid is interrupted.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
EP83400524A 1982-03-19 1983-03-15 Druckluftspareinrichtung Expired EP0089881B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR8205042 1982-03-19
FR8205042A FR2523659A1 (en) 1982-03-19 1982-03-19 Control economiser for compressed air - has adjustable, double reduction valve controlling actuator operating cycle of actuator moving part
FR8303513A FR2542043B2 (fr) 1983-03-03 1983-03-03 Dispositif economiseur d'air comprime
FR8303513 1983-03-03

Publications (3)

Publication Number Publication Date
EP0089881A2 true EP0089881A2 (de) 1983-09-28
EP0089881A3 EP0089881A3 (en) 1984-01-18
EP0089881B1 EP0089881B1 (de) 1985-09-25

Family

ID=26222830

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83400524A Expired EP0089881B1 (de) 1982-03-19 1983-03-15 Druckluftspareinrichtung

Country Status (8)

Country Link
US (1) US4608910A (de)
EP (1) EP0089881B1 (de)
JP (1) JPS591801A (de)
CH (1) CH652454A5 (de)
DE (1) DE3360864D1 (de)
ES (1) ES520793A0 (de)
GB (1) GB2117055B (de)
IT (2) IT8353079V0 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0144337B1 (de) * 1983-04-12 1988-08-03 Legris-Société Anonyme dite Druckluftspareinrichtung
CH684651A5 (de) * 1991-04-03 1994-11-15 Schlatter Ag Pneumatische Antriebsvorrichtung.
WO1995027854A1 (de) * 1994-04-06 1995-10-19 Barth, Veronika Maschine zur erzeugung von arbeit mit einem ständig verwendbaren arbeitsdruckmedium
WO1995030095A2 (de) * 1994-05-03 1995-11-09 Wolfgang Barth Pneumatisches antriebssystem zum erhalt einer steten arbeit zur fortbewegung einer masse mittels innerer druckkraftwirkung
WO2016202356A1 (de) * 2015-06-15 2016-12-22 Festo Ag & Co. Kg Antriebssystem und verfahren zum betreiben eines fluidbetätigen drehantriebs

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DE69527093D1 (de) * 1995-10-02 2002-07-18 Pos Line Ab Verfahren und ventilvorrichtung zum steuern eines hin-und herbewegenden hydraulischen antriebs
US6354797B1 (en) * 2000-07-27 2002-03-12 General Electric Company Brazeless fillet turbine nozzle
GB2388633B (en) 2002-05-15 2006-03-08 Dana Automotive Ltd Engine lubrication system
RU2457368C1 (ru) * 2010-12-16 2012-07-27 Государственное образовательное учреждение высшего профессионального образования "Тульский государственный университет" (ТулГУ) Газовый привод с экономичным клапанным распределителем

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0144337B1 (de) * 1983-04-12 1988-08-03 Legris-Société Anonyme dite Druckluftspareinrichtung
CH684651A5 (de) * 1991-04-03 1994-11-15 Schlatter Ag Pneumatische Antriebsvorrichtung.
WO1995027854A1 (de) * 1994-04-06 1995-10-19 Barth, Veronika Maschine zur erzeugung von arbeit mit einem ständig verwendbaren arbeitsdruckmedium
WO1995030095A2 (de) * 1994-05-03 1995-11-09 Wolfgang Barth Pneumatisches antriebssystem zum erhalt einer steten arbeit zur fortbewegung einer masse mittels innerer druckkraftwirkung
WO1995030095A3 (de) * 1994-05-03 1995-11-30 Wolfgang Barth Pneumatisches antriebssystem zum erhalt einer steten arbeit zur fortbewegung einer masse mittels innerer druckkraftwirkung
WO2016202356A1 (de) * 2015-06-15 2016-12-22 Festo Ag & Co. Kg Antriebssystem und verfahren zum betreiben eines fluidbetätigen drehantriebs

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ES8402053A1 (es) 1984-01-01
CH652454A5 (fr) 1985-11-15
ES520793A0 (es) 1984-01-01
US4608910A (en) 1986-09-02
JPS591801A (ja) 1984-01-07
IT8367309A0 (it) 1983-03-18
GB2117055B (en) 1985-12-18
GB2117055A (en) 1983-10-05
EP0089881A3 (en) 1984-01-18
IT1158908B (it) 1987-02-25
IT8353079V0 (it) 1983-03-18
GB8307508D0 (en) 1983-04-27
DE3360864D1 (en) 1985-10-31
EP0089881B1 (de) 1985-09-25

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