EP0579037B2 - Hydropneumaischer Druckübersetzer - Google Patents
Hydropneumaischer Druckübersetzer Download PDFInfo
- Publication number
- EP0579037B2 EP0579037B2 EP93110428A EP93110428A EP0579037B2 EP 0579037 B2 EP0579037 B2 EP 0579037B2 EP 93110428 A EP93110428 A EP 93110428A EP 93110428 A EP93110428 A EP 93110428A EP 0579037 B2 EP0579037 B2 EP 0579037B2
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- operating
- pressure
- chamber
- storage
- 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 - Lifetime
Links
Images
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
- F15B11/0325—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 the fluid-pressure converter increasing the working force after an approach stroke
-
- 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
Definitions
- the invention is based on a hydropneumatic Pressure translator according to the type of the main claim.
- On Main problem with such hydropneumatic pressure intensifiers consists in the sealing between the storage room and the control room, because the hydraulic pressures in the storage space and the pneumatic ones Press continuously in the control room during a work cycle change, and not necessarily change synchronously, whereby on the one hand there is a risk that oil from the storage space in the Control room arrives and this causes leakage losses that the Working capacity of the hydropneumatic pressure intensifier can affect, or there is a risk that air from the Control room enters the storage room where it is absorbed by the oil with the disadvantage that it gets into the work area and there the high pressure phase of the pressure stroke to an intensified Compressibility tends with all of the resulting disadvantages for the working ability of the unit.
- pressure translators (DE-OS 2810 894) are both to the wall of the working cylinder, as well as to the outer surface of the Plunger two radial seals provided with the purpose one to achieve optimal air-oil separation. Is problematic here in particular, that the inclination of the air from the control room in the Storage space does not come about in the low pressure phase is present, but rather in the high pressure phase, whereby also small amounts of air as wall laminates during the axial movement of the Storage piston are "pumped past" the radial seals.
- the hydropneumatic pressure intensifier according to the invention with the characteristic features of the main claim points to compared to the advantage that in the ventilation ring grooves
- the lowest pressure prevails, for example atmospheric pressure, so that the radial seal towards the control room passing air volumes can be derived.
- A is used for ventilation Bore in the working cylinder, which is independent of the working stroke of the Accumulator piston with the lateral surface ring groove always in overlap stands. Both in the starting position and in the end position - possibly with only small remaining amounts in the storage space - is for a complete relief is provided, the vent hole can lead directly to the atmosphere.
- a radial bore can in be carried out simply as a cross hole, beginning and end of this radial bore in each case in the annular groove lateral surfaces ends and therefore no frictional contact with the working cylinder or the plunger.
- a Auxiliary piston connected to the working piston for rapid traverse alternately can be acted upon pneumatically on both sides.
- Pressure intensifier is a working piston 2 axially in a housing 1 slidably and radially sealed and limited with it a hydraulic oil-filled working space 3.
- a piston rod 4 projecting outside the housing arranged.
- the working piston 2 has a collar Auxiliary piston 5, which is radially sealed to a casing tube 6 and thereby separates two pneumatic spaces 7 and 8 from each other for the rapid traverse of working piston 2 alternating with pneumatic Pressure are supplied.
- a storage space 9 for hydraulic oil Above the work area 3 and hydraulically connected to it is a storage space 9 for hydraulic oil, the storage pressure by a storage piston and pneumatic pressure in one Control room 12 is generated.
- the storage piston 11 is in one Storage space 9 and the control room 12, delimiting Jacket tube 13 guided radially sealing and axially displaceable, in Art a free piston.
- the casing tube 13 is on the one hand by a Housing part 14 of the housing 1 and on the other hand by a Partition 15 closed, being on housing part 14 and partition 15 corresponding twists for pushing on the casing tube 13 are present, with additional static seals 16.
- the partition 15 is used for the side facing away from the control chamber 12 Limitation of a pneumatic space 17, which is by a casing tube 18th is surrounded and in which the drive piston 19 of a plunger 21st is stored, which counter to the hydraulic pressure in the Work space 3 is movable.
- the plunger 21 penetrates the partition 15 in a radially sealed manner and the storage piston 11 and dips with its free end in the Storage space 9.
- the drive piston 19 with plunger 21 is driven by compressed air, which in a drive room 22 above of the drive piston 21 is passed, whereby the High pressure operation is initiated.
- the plunger dives 21, after a certain stroke in one of Storage space 9 connecting bore 23 leading to work space 3, this connection with the participation of a radial seal 24 is interrupted.
- This pressure corresponds to that Transmission ratio of the working surfaces of drive pistons 19 to Plunger piston 21, starting from the drive piston 19 pressurized pneumatic pressure.
- the resulting high hydraulic pressure acts directly on the working piston 2 and causes the desired high force on the piston rod 4.
- the various pneumatic rooms are through to the outside of the Hydropneumatic pressure intensifier leading connection channels equipped, namely the pneumatic room 7 through the channel 25, the Pneumatic room 8 through the channel 26, the control room 12 through the Channel 27, the pneumatic room 17 through the channel 28 and the Drive space 22 through the channel 29.
- the working stroke is in the pneumatic control line 31 Pressure reduced and passed into a pneumatic control line 32, which connects the connecting channels 25, 27 and 29 to each other, wherein the connection channel 29 is a pressure-controlled valve 33 is connected upstream.
- the supplied pneumatic pressure is the first the connecting channels 25 and 27 and thus the pneumatic space 7 and supplied to the control chamber 12, after which the auxiliary piston 5 with Piston 2 is pushed down in rapid and the Accumulator piston 11 corresponding to that from the storage space 9 in the Working space 3 overflowing hydraulic quantity is replenished.
- the hydraulic volume in work space 3 and storage space 9 is overall constant, except for leakage amounts that occur every now and then need to be refilled.
- Control line 32 and the pressure-controlled valve 33 gives the Inflow to the connecting duct 29 and thus to the drive chamber 22 free, so that the drive piston 19 with plunger 21 down is moved with the effect described above.
- the accumulator piston 11 is between the one filled with oil Storage space 9 and, according to the control mentioned above, with air different pressure-filled control chamber 12, wherein especially to prevent oil from the storage space 9 in the control room 12 and vice versa air into the storage room 9 arrives.
- an absolute air-oil separation is used for this on the storage piston 11, in which it is on the one hand both to the casing tube 13 as well as plunger 21 with annular grooves 34 and 35 Has radial seals 36 and 37.
- the radial seals 37 for Plunger 21 is once as a round cord seal and once as Cuff seal shown shown shown.
- annular groove 38 which is arranged in a Casing tube 13 arranged vent hole 39 to the outside the unit is vented.
- the vent hole 39 is related on the annular groove 38, or the maximum possible stroke of the Storage piston 11 arranged so that they are always in overlap with the annular groove 38 remains.
- annular groove 42 is provided by a continuous Radial bore 43 with the always vented annular groove 38 on the Shell surface of the storage piston 11 is connected.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
- Fluid-Pressure Circuits (AREA)
- Fluid-Damping Devices (AREA)
- Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
Description
- Fig. 1
- einen hydropneumatischen Druckübersetzer im Längsschnitt und
- Fig. 2
- einen Ausschnitt aus Fig. 1 im vergrößerten Maßstab.
- 1
- Gehäuse
- 2
- Arbeitskolben
- 3
- Arbeitsraum
- 4
- Kolbenstange
- 5
- Hilfskolben
- 6
- Mantelrohr
- 7
- Pneumatikraum
- 8
- Pneumatikraum
- 9
- Speicherraum
- 10
- -
- 11
- Speicherkolben
- 12
- Steuerraum
- 13
- Mantelrohr
- 14
- Gehäuseteil
- 15
- Trennwand
- 16
- Statische Dichtung
- 17
- Pneumatikraum
- 18
- Mantelrohr
- 19
- Antriebskolben
- 20
- -
- 21
- Tauchkolben
- 22
- Antriebsraum
- 23
- Verbindungsbohrung
- 24
- Radialdichtung
- 25
- Anschlußkanal
- 26
- Anschlußkanal
- 27
- Anschlußkanal
- 28
- Anschlußkanal
- 29
- Anschlußkanal
- 30
- -
- 31
- Pneumatische
Steuerleitung - 32
- Pneumatische
Steuerleitung - 33
- Druckabhängig
gesteuertes
Ventil - 34
- Ringnut
- 35
- Ringnut
- 36
- Radialdichtung
- 37
- Radialdichtung
- 38
- Ringnut
- 39
- Entlüftungsbohrung
- 40
- -
- 41
- Zentrale Bohrung
- 42
- Ringnut
- 43
- Radialbohrung
Claims (6)
- Hydropneumatischer Drucküberseztermit einem in einem Aggregatsgehäuse angeordneten Arbeitsraum (3) für wechselnde Drücke, nämlich einem niederen Speicherdruck und einem hohen Arbeitsdruck,mit einem den Arbeitsraum (3) stirnseitig begrenzenden und durch den Arbeitsdruck im Aggregatsgehäuse (1) für seinen Arbeitshub betätigbaren Arbeitskolben (2), der durch eine Kolbenstange (4) nach außen geführt ist,mit einem mit dem Arbeitsraum (3) hydraulisch verbindbaren in einem Mantelrohr (13) angeordneten Speicherraum (9), aus dem während eines Eilgangs des Arbeitshubs Hydrauliköl unter Speicherdruck in den Arbeitstraum (3) strömt und beim Rückhub wieder zurückströmt,mit einem als Hochdruckerzeuger pneumatisch oder hydraulisch betätigbaren und nach dem Eingang des Arbeitskolbens (2) in den Arbeitsraum (3) tauchenden Tauchkolben (21),mit einem den Speicherraum (9) begrenzenden axial im Mantelrohr (13) verschiebbaren und vom Tauchkolben (21) durchdrungenen Speicherkolben (11),mit jeweils zwei in Hubrichtung mit Abstand am Speicherkolben vorhandenen, sowohl zum Tauchkolben (21) als auch zum Mantelrohr (13) wirkenden Dichtungen (36, 37), nämlich in zwei Ringnuten (34) auf der Mantelfläche des Speicherkolbens (11) angeordneten zum Mantelrohr (13) hin wirkenden Radialdichtungen (36) bzw. in zwei Ringnuten (35) in der Wand der vom Tauchkolben (21) durchdrungenen Innenbohrung (41) angeordneten zum Tauchkolben (21) hin wirkenden Radialdichtungen (36),mit einem auf der dem Speicherraum (9) abgewandten Seite des Speicherkolbens (11) vorhandenen und mit Luft unterschiedlichen Drucks beaufschlagbaren Steuerraum (12) undmit einer den Steuerraum (12) begrenzenden und mit dem Mantelrohr (13) fest verbundenen, sowie vom Tauchkolben (21) durchdrungenen Trennwand (15),mit einer auf der Mantelfläche des Speicherkolbens (11) in Hubrichtung zwischen den Dichtungen (36) zum Mantelrohr (13) hin offenen Außenringnut (38) undmit einer in der Wand der Innenbohrung (41) des Speicherkolbens (11), ebenfalls zwischen den Dichtungen (37) angeordnetendass zur Druckentlastung der Außenringnut (38) eine mit der Außenringnut (38) stets in Überdeckung stehende Entlüftungsbohrung (39) im Mantelrohr (13) angeordnet ist unddass die Entlüftungsbohrung (39) zur Atmosphäre hin führt.
- Hydropneumatischer Druckübersetzer nach Anspruch 1, dadurch gekennzeichnet, dass die Außenringnut (38) mit der Innenringnut (42) durch eine Radialbohrung (43) im Speicherkolben (11) verbunden ist.
- Hydropneumatischer Druckübersetzer nach einem der vorgehenden Ansprüche 1 oder 2, dadurch gekennzeichnet, dass auf beiden Seiten der Außenringnut (38) bzw. Innenringnut (42) separate Dichtungsringnuten (34, 35) vorgesehen sind zur Aufnahme von Raidaldichtungen (36, 37).
- Hydropneumatischer Druckübersetzer nach einem der vorgehenden Ansprüche, dadurch gekennzeichnet, dass in der Trennwand (15) radial nach außen führende Anschlusskanäle (27, 28) für Druckluft vorhanden sind.
- Hydropneumatischer Druckübersetzer nach einem der vorgehenden Ansprüche, dadurch gekennzeichnet, dass der auf dem Steuerraum (12) abgewandten Seite der Trennwand (15) vorhandene Raum (17) luftdruckgesteuert ist, für die Rückstellung eines mit dem Tauchkolben (21) verbundenen Antriebskolbens (19).
- Hydropenumatischer Druckübersetzer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass ein Hilfskolben (5) mit dem Arbeitskolben (2) verbunden ist, der für einen Eilgang beiderseits abwechselnd pneumatisch beaufschlagbar ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4223411A DE4223411A1 (de) | 1992-07-02 | 1992-07-02 | Hydropneumatischer Druckübersetzer |
DE4223411 | 1992-07-02 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0579037A1 EP0579037A1 (de) | 1994-01-19 |
EP0579037B1 EP0579037B1 (de) | 1997-09-24 |
EP0579037B2 true EP0579037B2 (de) | 2003-01-22 |
Family
ID=6463352
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP93110428A Expired - Lifetime EP0579037B2 (de) | 1992-07-02 | 1993-06-30 | Hydropneumaischer Druckübersetzer |
Country Status (5)
Country | Link |
---|---|
US (1) | US5377488A (de) |
EP (1) | EP0579037B2 (de) |
JP (1) | JPH06159303A (de) |
AT (1) | ATE158642T1 (de) |
DE (2) | DE4223411A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004010438B3 (de) * | 2004-03-01 | 2005-06-30 | Farger & Joosten Maschinenbau Gmbh | Hydropneumatischer Druckübersetzer mit Axial- und Radialdichtungen |
Families Citing this family (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA2102762A1 (en) * | 1993-11-09 | 1995-05-10 | Viljo K. Valavaara | Two-stage pressure cylinder |
DE4445011A1 (de) * | 1994-12-16 | 1996-06-20 | Tox Pressotechnik Gmbh | Hydraulischer Druckübersetzer |
US5526644A (en) * | 1995-06-07 | 1996-06-18 | Brieschke; Todd M. | Oil intensifier cylinder |
US5943862A (en) * | 1996-03-19 | 1999-08-31 | Tox Pressotechnik Gmbh | Hydropneumatic machine tool with cushioning |
DE19720252A1 (de) * | 1997-05-15 | 1998-11-19 | Kraemer & Grebe Kg | Hydropneumatischer Druckübersetzer als Stanzenantrieb in Verpackungsmaschinen |
US5865029A (en) * | 1997-07-11 | 1999-02-02 | Aries Engineering Company, Inc. | Air/oil intensifier having multiple sensors |
DE19859891A1 (de) | 1998-12-23 | 2000-06-29 | Tox Pressotechnik Gmbh | Hydropneumatischer Druckübersetzer |
KR100380121B1 (ko) * | 2000-03-15 | 2003-04-14 | 주재석 | 유압식 증압실린더 |
JP2004503702A (ja) | 2000-03-27 | 2004-02-05 | トックス・プレッソテヒニック・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング・ウント・コンパニー・コマンディトゲゼルシャフト | 液圧式増圧器 |
DE10255230A1 (de) * | 2002-11-26 | 2004-06-09 | Uhde High Pressure Technologies Gmbh | Hochdruckvorrichtung und -verfahren zum hydraulisch-pneumatischen Krafthub für Reinraumanwendungen |
MX2009000844A (es) * | 2006-07-31 | 2009-02-04 | Norgren Gmbh | Accionador neumatico. |
CN101688545A (zh) * | 2007-04-13 | 2010-03-31 | 诺格伦有限责任公司 | 气动致动器系统和方法 |
DE102007036844B4 (de) * | 2007-08-06 | 2021-05-06 | Tox Pressotechnik Gmbh & Co. Kg | Verfahren zum Betrieb einer hydropneumatischen Vorrichtung zur Druckübersetzung |
KR100917070B1 (ko) * | 2007-09-03 | 2009-09-15 | 윤택수 | 부스터가 구비된 증압장치 |
DE102007044907A1 (de) * | 2007-09-19 | 2009-04-02 | Tox Pressotechnik Gmbh & Co. Kg | Verfahren zum Betrieb einer hydropneumatischen Vorrichtung sowie Hydraulikflüssigkeitspumpe für die Wartung einer hydropneumatischen Vorrichtung |
DE102012008902A1 (de) * | 2012-05-08 | 2013-11-14 | Tox Pressotechnik Gmbh & Co. Kg | Hydropneumatische Vorrichtung zur Druckübersetzung und Nietvorrichtung |
US9394928B2 (en) | 2012-07-31 | 2016-07-19 | Caterpillar Inc. | Dynamic seal wear mitigation system |
US9651067B2 (en) * | 2012-07-31 | 2017-05-16 | Caterpillar Inc. | Hydraulic system with a dynamic seal |
CN102913509A (zh) * | 2012-11-23 | 2013-02-06 | 湖北汽车工业学院 | 电液增压缸及安装有电液增压缸的压机设备 |
CN104279194A (zh) * | 2013-07-09 | 2015-01-14 | 北京精密机电控制设备研究所 | 一种燃气挤压式油箱 |
CN107288942B (zh) * | 2016-03-31 | 2019-01-08 | 中核新能核工业工程有限责任公司 | 以压缩空气为动力的小流量uf6气体增压装置 |
US10941790B2 (en) * | 2017-03-15 | 2021-03-09 | Seiko Instruments Inc. | Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece |
US10982690B2 (en) * | 2017-03-15 | 2021-04-20 | Seiko Instruments Inc. | Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece |
JP6999439B2 (ja) * | 2017-03-15 | 2022-01-18 | セイコーインスツル株式会社 | シリンダ装置、プレス装置、ワーククランプ装置、シリンダ装置動作方法、ワークのクランプ方法、及びワークのプレス方法 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4029138A1 (de) † | 1989-09-18 | 1991-03-28 | Savair Inc | Oel-/luft-verstaerkerzylinder |
US5107681A (en) † | 1990-08-10 | 1992-04-28 | Savair Inc. | Oleopneumatic intensifier cylinder |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2765625A (en) * | 1952-06-12 | 1956-10-09 | Charles H Hart | Air-hydraulic booster |
FR1504765A (fr) * | 1966-10-26 | 1967-12-08 | Faiveley Sa | Vérin oléopneumatique à structure étagée |
DE1777423C2 (de) * | 1967-06-08 | 1975-12-04 | Josef 6200 Wiesbaden-Bierstadt Nemetz | Hydropneumatischer Spannzylinder |
DE2230492A1 (de) * | 1972-06-22 | 1974-01-10 | Stommel & Voos Stahlstempelfab | Pneumatisch-hydraulischer druckumsetzer |
DE2304752A1 (de) * | 1973-02-01 | 1974-08-15 | Schaal Kg Werkzeug U Vorrichtu | Vorrichtung zur pneumatisch - hydraulischen uebertragung von kraeften |
CH616992A5 (en) * | 1977-03-24 | 1980-04-30 | Schenker Emil Storen Und Masch | Pneumatic-hydraulic piston/cylinder unit, in particular for the actuation of tools |
DE2818337C2 (de) * | 1978-04-26 | 1980-07-17 | Haug, Paul, 7307 Aichwald | Druckübersetzter hydropneumatischer |
DE3125081A1 (de) * | 1981-06-26 | 1983-01-13 | Kolben-Seeger GmbH & Co KG, 6236 Eschborn | Hydropneumatischer druckzylinder |
DE3828699A1 (de) * | 1988-08-24 | 1990-03-01 | Eugen Rapp | Verfahren zur oelauffuellung eines hydro-pneumatischen druckuebersetzers und einrichtung zur durchfuehrung des verfahrens |
US5265423A (en) * | 1992-12-04 | 1993-11-30 | Power Products Ltd. | Air-oil pressure intensifier with isolation system for prohibiting leakage between and intermixing of the air and oil |
-
1992
- 1992-07-02 DE DE4223411A patent/DE4223411A1/de not_active Ceased
-
1993
- 1993-06-30 DE DE59307411T patent/DE59307411D1/de not_active Expired - Lifetime
- 1993-06-30 EP EP93110428A patent/EP0579037B2/de not_active Expired - Lifetime
- 1993-06-30 AT AT93110428T patent/ATE158642T1/de not_active IP Right Cessation
- 1993-07-02 JP JP5164517A patent/JPH06159303A/ja active Pending
- 1993-07-02 US US08/084,975 patent/US5377488A/en not_active Expired - Lifetime
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4029138A1 (de) † | 1989-09-18 | 1991-03-28 | Savair Inc | Oel-/luft-verstaerkerzylinder |
US5107681A (en) † | 1990-08-10 | 1992-04-28 | Savair Inc. | Oleopneumatic intensifier cylinder |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004010438B3 (de) * | 2004-03-01 | 2005-06-30 | Farger & Joosten Maschinenbau Gmbh | Hydropneumatischer Druckübersetzer mit Axial- und Radialdichtungen |
Also Published As
Publication number | Publication date |
---|---|
DE4223411A1 (de) | 1994-01-05 |
EP0579037B1 (de) | 1997-09-24 |
DE59307411D1 (de) | 1997-10-30 |
ATE158642T1 (de) | 1997-10-15 |
US5377488A (en) | 1995-01-03 |
JPH06159303A (ja) | 1994-06-07 |
EP0579037A1 (de) | 1994-01-19 |
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