EP0355780B1 - Verfahren zur Ölauffüllung eines hydro-pneumatischen Druckübersetzers und Einrichtung zur Durchführung des Verfahrens - Google Patents

Verfahren zur Ölauffüllung eines hydro-pneumatischen Druckübersetzers und Einrichtung zur Durchführung des Verfahrens Download PDF

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Publication number
EP0355780B1
EP0355780B1 EP89115428A EP89115428A EP0355780B1 EP 0355780 B1 EP0355780 B1 EP 0355780B1 EP 89115428 A EP89115428 A EP 89115428A EP 89115428 A EP89115428 A EP 89115428A EP 0355780 B1 EP0355780 B1 EP 0355780B1
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EP
European Patent Office
Prior art keywords
pressure
piston
reservoir
air
working
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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
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EP89115428A
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German (de)
English (en)
French (fr)
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EP0355780A1 (de
Inventor
Eugen Rapp
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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
    • F15B11/02—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 method for filling up the oil in a storage space of a hydro-pneumatic pressure intensifier, and on a known type of hydro-pneumatic pressure intensifier for carrying out the method, in each case according to the preamble of claim 1 and claim 5.
  • a problem with the oil filling of the storage space is the venting of the storage space, which is of course required when the storage space is first filled with hydraulic oil, but may also be required when refilling hydraulic oil, namely whenever air flows from the spring space through the radial seals of the storage piston Storage space has reached.
  • Such harmful air can also have reached the working space from the working space if, for example, the radial seals on the working piston do not seal sufficiently against the pneumatic pressures acting on the working piston.
  • the storage space is usually vented through a vent hole which is closed by a vent screw, which must be removed during hydraulic oil refilling and intended venting. Often, however, is one when refilling oil Venting not required so that the vent hole is not opened.
  • the storage piston can be pushed so far into the spring chamber that the radial outer seals run over connection bores in the spring chamber and can be injured over time.
  • these connection bores of the spring chamber are relatively large. These connection bores are used, for example, for an air spring or, if a coil spring is arranged in the spring chamber, for the main ventilation of the spring chamber.
  • the method according to the invention for filling a storage space of a hydro-pneumatic pressure booster and the hydro-pneumatic pressure booster for carrying out this method with the characterizing features of claim 1 and claim 4 has the advantage that any air quantities present in the storage space, or when filling up the storage space air volumes entering with hydraulic oil are automatically vented. Since the oil is always refilled with a certain overpressure that overcomes the force of the accumulator spring, when using the individual pressures or the forces that cause the pressures, the accumulator piston is displaced during refilling until after sufficient oil refill, but before the working piston is displaced Oil refilling is ended.
  • this termination can take place by opening the pressure valve, for example a pressure-maintaining valve, so that a certain pressure in the storage space is not exceeded.
  • this interruption can also take place in that when a filling pressure is reached which is somewhat higher than the storage pressure but lower than the pressure required on the working piston for its displacement, the oil filling is ended.
  • the maximum pressure in the storage space is limited according to the invention when filling up with oil, and this is preferably in conjunction with an automatic control (ventilation).
  • the pressure is limited by a pressure-maintaining valve which, as is known, either opens when a certain pressure is exceeded in order to reduce the excess pressure or closes in order to prevent excess pressure, so that such a pressure-maintaining valve is arranged either on the oil overflow or on the oil inlet can be.
  • a non-return valve can also serve as a pressure valve with a simultaneous venting effect, which opens when the storage pressure is exceeded accordingly.
  • the vent opening is only exposed by the storage piston in its initial position.
  • this only makes sense for ventilation if the cylinder receiving the accumulator piston is installed vertically, so that the air volumes can collect above the oil column and below the accumulator piston, which then, after a corresponding displacement of the accumulator piston, automatically first , escape before oil can then flow in.
  • the installation position does not play a decisive role as a pure safeguard against excess oil pressure in the storage space.
  • the pressure valve to be used in this case must in any case prevent backflow of air from outside via the ventilation hole into the storage space.
  • two vent holes are provided, one of which is opened in the starting position and the other is only opened in the extreme position of the storage piston when the storage piston is moved further in the direction of the storage spring.
  • the accumulator piston always returns to its starting position during normal operation and thereby opens the first vent hole, which can then be used for continuous venting
  • the second vent hole is only opened if an error occurs during oil refilling, e.g. if there is too much oil in the system is pumped in and cannot be adequately discharged from the relatively small first vent hole.
  • the storage spring pushes the storage piston back a little, whereby this second ventilation hole is closed by the storage piston.
  • this second vent hole can also be controlled by a pressure valve, but also the accumulator piston itself with its radial seals in connection with the mouth of this second vent hole works as a pressure valve and thus an extra pressure valve serves as an additional safeguard against leakage air.
  • the extreme position of the accumulator piston is determined by a stop, so that the accumulator piston is only pushed against this stop when hydraulic oil is being filled, before the ventilation or the overfill protection device opens in order to allow the air or too much pumped hydraulic quantities to escape allow.
  • This in particular also prevents the accumulator piston from being displaced to such an extent that the radial seal could be damaged by any connections which it would run over.
  • ring grooves (labyrinth grooves) to the cylinder wall and to the plunger are provided with leakage lines in the storage piston for the discharge of leakage air and leakage oil.
  • a locking ring which engages in a corresponding groove in the inner wall of the cylinder bore receiving the storage piston serves as a stop.
  • a locking ring can be inserted into the correspondingly provided groove of the cylinder bore without any problems when the pressure intensifier is assembled.
  • a loose stop ring is arranged between the storage piston and the locking ring, the outside diameter of which is the inside diameter of the Corresponds to the cylinder bore.
  • the latter embodiment can be used particularly advantageously when using a helical spring as a storage spring, in which this helical spring is supported on the stop ring.
  • this configuration can also be used advantageously in an air spring as a storage spring.
  • a coil spring can be used in a double function as a storage spring and as a return spring between the storage piston and the drive piston of the plunger
  • compressed air acting on the storage piston and on the other hand on the drive piston can serve as the storage spring in the same function.
  • the air pressure acting on this drive piston for driving the plunger must be correspondingly higher than the accumulator spring pressure.
  • a device can be used as a flow valve or pressure-maintaining valve with an elastic valve member, which is pressed from the outside onto the mouth of the vent hole via a rocker, the rocker being mounted on a collar screw with radial play, and the closing force by a resilient element acting on the other lever end of the rocker is determined becomes.
  • Rubber-like elements can serve as a resilient element or as a movable valve member, the opening force of this valve being determined by the cross section of the mouth of the vent hole and the elastic forces of the rubber elements.
  • the pressure intensifier shown in Fig. 1 has cylindrical outer dimensions, but can also have other outer shapes, such as two cylinders lying side by side or a cuboid configuration.
  • a working piston 2 is arranged axially displaceably in a working space 1 filled with hydraulic oil, said working piston being guided radially sealingly in a bore of a housing 3 of the pressure booster.
  • a piston rod 4 is arranged on the working piston 2 for power transmission.
  • the working piston 2 has an auxiliary piston 5 arranged as a collar on it, which is radially sealed off from a casing tube 6 and thereby delimits two spaces 7 and 8 which are supplied pneumatically for the rapid traverse of the working piston. As soon as sufficient compressed air flows into the space 7, the working piston 2 is pushed downwards, but if compressed air is conveyed into the space 8, the working piston 2 returns to the starting position shown.
  • a storage space 9 for hydraulic oil for hydraulic oil, the storage pressure of which is generated by a storage piston 11 and a storage spring 12.
  • the storage piston 11 is guided in a radially sealing, axially displaceable manner in a casing tube 13.
  • a drive piston 14 of a plunger 15 is mounted in this casing tube 13 and can be displaced in the direction of the working space 1 against the force of the storage spring 12.
  • the plunger 15 penetrates the storage piston 11 in a radially sealed manner and dips into the storage space 9.
  • the drive piston 14 with plunger 15 is driven by compressed air which is conducted into a drive space 16 above the drive piston 14.
  • the pneumatic pressure in the drive chamber 16 is reduced, so that the storage spring 12 pushes the drive piston 14 back into the starting position shown, after which from the Working space 1 displaced by the working piston 2, hydraulic fluid flows into the storage space 9, and the working piston 2 is displaced into the starting position shown by compressed air in the space 8, which acts on the auxiliary piston 5.
  • a venting device with overfill protection 19 and 42 is provided according to the invention, as described in detail with reference to FIG. 2.
  • hydraulic oil is refilled via a filling screw 22, which is provided on the piston rod 4 and from which a channel 23 running in the piston rod 4 leads to the working space 1.
  • the starting position of the accumulator piston 11, which is shown in FIG. 1, is determined by the balance of forces between the force of the accumulator spring 12 and the force resulting from the hydraulic pressure times the accumulator piston surface. Only when the pressure in the storage space 9 continues to rise inadmissibly is the storage piston 11 pushed into an extreme position against a locking ring 24 which engages in a corresponding groove in the inner wall of the casing tube 13. As soon as the above-mentioned leakage losses occur in the storage space 9, the storage piston 11 is held down accordingly by the storage spring 12, so that the storage piston 11 no longer reaches its starting position shown below the stop formed by the locking ring 24. Only when hydraulic oil is refilled into the working space 1 or the storage space 9, the storage piston 11 is pushed upwards in the direction of the stop 24.
  • a steel ring 30 is provided between the storage piston 11 and the locking ring 24, on which the storage spring 12 is also supported, and on the other hand the storage piston 11 in the desired starting position shown is the input of a opened first vent hole 25.
  • the vent hole 25 is separated from the accumulator chamber 9 by an annular seal 26 which is arranged in an annular groove 27 of the accumulator piston.
  • the storage piston 11 will again be slightly below a certain pressure increase pushed back against the storage spring 12 without the vent hole 25 being opened again, ie without this slight pressure increase allowing oil to get into the vent hole from the reservoir. If, after the end of the working cycle, the accumulator piston 11 again assumes the starting position shown, possible amounts of air that have undesirably entered the working space 1 or the storage space are automatically vented via the vent hole 25.
  • the mouth of the vent hole 25 is controlled by a mushroom-shaped movable valve part 28 which is mounted on a vent plate 29 designed as a rocker.
  • the ventilation plate 29 is anchored to the casing tube 13 with a collar screw 31, wherein a certain play is provided between the shaft of the collar screw 31 and the bore 32 of the ventilation plate receiving the collar of the collar screw in order to allow the ventilation plate 29 to rock when the collar screw 31 is fixed .
  • the closing force of the valve part 28 and thus the pressure control of the storage space pressure is determined by a second rubber mushroom 33 which acts on the other end of the ventilation plate 29.
  • the filling screw 22 is opened to fill the hydraulic oil and hydraulic oil is filled in under a certain pressure, this flows through the channel 23 into the working space 1 and from there into the storage space 9, the storage piston 11 being pushed upward against the force of the storage spring.
  • the breather plate is removed during filling and during the first filling, in order to allow an unimpeded escape of air and to be able to easily recognize when the breather has ended and only hydraulic oil flows out through the breather bore 25. If, however, it is forgotten to remove the ventilation plate 29 and thus the movable valve part 28, the accumulator piston 11 is pushed further up to the locking ring 24 due to the resulting greater throttling effect when air and hydraulic oil flow out.
  • Fig. 3 is a cross section through the first embodiment according to line III is shown, namely with the locking ring 24, but with the omission of the inner parts such as plunger, storage piston and storage spring. From this figure it can also be seen that the locking ring 24 is interrupted at the point at which the collar screw 31 is screwed into the casing tube 13.
  • the pressure intensifier is constructed in principle in exactly the same way as in the first.
  • an air spring which acts in the form of air pressure in the spring chamber 121, serves as the storage spring. Since the demands on the radial seals are particularly high here, the drive piston 114 and the storage piston 111 are also designed accordingly. While there is almost no air overpressure in the spring chamber 21 in the spring chamber 121, there is a correspondingly high air pressure in the spring chamber 121 of this second embodiment in order to generate the required spring force. This also increases the risk of air leaking into the storage space 9. In order to enable the drive piston 114 to be driven against the air spring, the drive air pressure required in the drive chamber 16 must be correspondingly greater than the air spring pressure.
  • a simple pneumatic control can, however, at the same time complete pressure relief of the spring chamber 121 when the compressed air is connected to the drive chamber 16, since from the moment at which the plunger 15 plunges into the connecting bore 17, the pressure in the storage chamber 9 and thus no longer the force spring required are.
  • the accumulator piston 211 has additional leak ring grooves 34 and 35 as a seal, which have a connecting bore 36 and from which the leak ring groove 34 is vented via a leak bore 37 arranged in the casing tube 113. This prevents leakage of compressed air from the air spring from the spring chamber 121 into the storage chamber 9.
  • FIG. 6 which also works with an air spring like the second exemplary embodiment, it acts on the one hand on the storage piston 311, but on the other hand on an intermediate wall 38 arranged in the casing tube 213, that is to say not on the drive piston 214 as in the second exemplary embodiment.
  • the space 39 above the intermediate wall 38 thus has no control function and can only be filled with air of low pressure in order to reset the drive piston 214.
  • a helical spring can also be used, which is then between the drive pistons 214 and partition 38 is arranged.
  • the casing tube 213 is interrupted for receiving the intermediate wall 38 and there is a corresponding collar 40 radially on the intermediate wall 38.
  • the air is supplied in the air spring chamber 221, which has shrunk to almost zero in the position shown, via a bore, not shown.
  • the collar screw 31 is fastened to the intermediate wall 38 or the collar 40 in the variant in FIG. 7 of the third exemplary embodiment.
  • the intermediate wall 38 serves as an extreme stop for the accumulator piston 311, the vent hole 25 of course being opened in the extreme position shown.
  • this third exemplary embodiment also works like the two previously described exemplary embodiments.
  • FIGS. 2 and 3 Such an additional device is shown in FIGS. 2 and 3.
  • the accumulator piston 11 assumes the starting position in which a second ventilation hole 41 is still closed by the ring seal 26 designed as a quad ring. Only when the storage piston 11 is pushed further up into its extreme position, in which the steel ring 30 abuts the securing ring 24 serving as a stop, is this second ventilation bore 41 opened by the storage piston 11.
  • the vent hole 41 is followed by a check valve 42 with a movable valve member 43 which is loaded by a closing spring 44.
  • first vent hole 25 can also be controlled via such a check valve, or both vent holes 25 and 41 can be controlled by a vent plate, as is shown by way of example in FIG. 2.
  • nipple 45 of the spring chamber 21 is shown in FIG. 3 under the number 45, this nipple being able to serve for ventilation but also ventilation, for example when using an air spring.

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  • 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)
  • Production Of Liquid Hydrocarbon Mixture For Refining Petroleum (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
EP89115428A 1988-08-24 1989-08-22 Verfahren zur Ölauffüllung eines hydro-pneumatischen Druckübersetzers und Einrichtung zur Durchführung des Verfahrens Expired - Lifetime EP0355780B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89115428T ATE89894T1 (de) 1988-08-24 1989-08-22 Verfahren zur oelauffuellung eines hydropneumatischen druckuebersetzers und einrichtung zur durchfuehrung des verfahrens.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3828699A DE3828699A1 (de) 1988-08-24 1988-08-24 Verfahren zur oelauffuellung eines hydro-pneumatischen druckuebersetzers und einrichtung zur durchfuehrung des verfahrens
DE3828699 1988-08-24

Publications (2)

Publication Number Publication Date
EP0355780A1 EP0355780A1 (de) 1990-02-28
EP0355780B1 true EP0355780B1 (de) 1993-05-26

Family

ID=6361491

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Application Number Title Priority Date Filing Date
EP89115428A Expired - Lifetime EP0355780B1 (de) 1988-08-24 1989-08-22 Verfahren zur Ölauffüllung eines hydro-pneumatischen Druckübersetzers und Einrichtung zur Durchführung des Verfahrens

Country Status (6)

Country Link
US (1) US5040369A (ja)
EP (1) EP0355780B1 (ja)
JP (1) JP3048581B2 (ja)
AT (1) ATE89894T1 (ja)
DE (2) DE3828699A1 (ja)
ES (1) ES2040951T3 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104329303A (zh) * 2014-09-15 2015-02-04 北京沃客石油工程技术研究院 一种基于活塞机构的自动换向水力机械

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1247263B (it) * 1991-02-28 1994-12-12 Carlo Brasca Testa di pressa pneumo-idraulica ad elevata velocita' di azionamento.
IT1247264B (it) * 1991-02-28 1994-12-12 Carlo Brasca Pressa pneumo-idraulica a corsa controllata
DE4214409A1 (de) * 1992-05-07 1993-11-11 Pressotechnik Gmbh Hydraulik-Aggregat
DE4217121C2 (de) * 1992-05-22 1996-02-01 Langenstein & Schemann Gmbh Freikolben-Zylinder-Vorrichtung mit zwei verschiedenen Druckflüssigkeiten
DE4223411A1 (de) * 1992-07-02 1994-01-05 Pressotechnik Pressen Und Werk Hydropneumatischer Druckübersetzer
DE4221638B4 (de) * 1992-07-02 2005-11-03 Tox Pressotechnik Gmbh & Co. Kg Verfahren für einen hydraulischen Druckübersetzer
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
DE4445011A1 (de) * 1994-12-16 1996-06-20 Tox Pressotechnik Gmbh Hydraulischer Druckübersetzer
DE19780220D2 (de) * 1996-03-19 1998-03-19 Tox Pressotechnik Gmbh Hydropneumatische Werkzeugmaschine
DE19859891A1 (de) * 1998-12-23 2000-06-29 Tox Pressotechnik Gmbh Hydropneumatischer Druckübersetzer
DE19907883A1 (de) * 1999-02-24 2000-08-31 Tox Pressotechnik Gmbh Hydropneumatischer Druckübersetzer
KR100380121B1 (ko) * 2000-03-15 2003-04-14 주재석 유압식 증압실린더
US20050091972A1 (en) * 2003-10-31 2005-05-05 Redman Kenneth K. Electrohydraulic actuator
JP4753110B2 (ja) * 2004-01-14 2011-08-24 株式会社富士トレーラー製作所 圃場溝掘機
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
CN101852227A (zh) * 2010-06-22 2010-10-06 肖高富 一种强力气缸
US9151690B2 (en) * 2011-12-20 2015-10-06 Gates Corporation Hose tester intensifier
AU2015204332B2 (en) * 2011-12-20 2016-10-20 The Gates Corporation High pressure and temperature valve
WO2013096586A2 (en) * 2011-12-20 2013-06-27 The Gates Corporation High pressure and temperature valve
CN104141641A (zh) * 2013-05-09 2014-11-12 上海易昆机械工程有限公司 一种自动预压紧压力传输及减压装置
CN105003472B (zh) * 2015-06-05 2017-05-03 武汉工程大学 一种气‑液增压缸
CN106050760B (zh) * 2016-06-27 2018-12-18 武汉仁达秦雕数控设备有限公司 四活塞气水增压缸

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2810894A1 (de) * 1977-03-24 1978-10-05 Schenker Storen Maschf Pneumatisch hydraulischer zylinder

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH429462A (fr) * 1963-11-21 1967-01-31 Torossian Edouard Dispositif hydropneumatique pour outil de serrage
CH412745A (fr) * 1965-01-08 1966-04-30 Torossian Edouard Dispositif de commande hydropneumatique pour étau d'établi
FR1504765A (fr) * 1966-10-26 1967-12-08 Faiveley Sa Vérin oléopneumatique à structure étagée
IT1020968B (it) * 1974-10-10 1977-12-30 Peuti Anstalt Cilindro operatore ad azionamento fluidico con convertitore di sforzo incorporato
FR2394386A1 (fr) * 1977-01-27 1979-01-12 Somifra Procede et dispositif automatique d'alimentation en matiere telle qu'un elastomere pour machine a injecter
DE2818337C2 (de) * 1978-04-26 1980-07-17 Haug, Paul, 7307 Aichwald Druckübersetzter hydropneumatischer
FR2547871B1 (fr) * 1983-06-24 1987-10-16 Mecagrav Sa Verin multiplicateur de pression

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2810894A1 (de) * 1977-03-24 1978-10-05 Schenker Storen Maschf Pneumatisch hydraulischer zylinder

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104329303A (zh) * 2014-09-15 2015-02-04 北京沃客石油工程技术研究院 一种基于活塞机构的自动换向水力机械

Also Published As

Publication number Publication date
JPH02102901A (ja) 1990-04-16
EP0355780A1 (de) 1990-02-28
ES2040951T3 (es) 1993-11-01
DE3828699A1 (de) 1990-03-01
DE58904472D1 (de) 1993-07-01
JP3048581B2 (ja) 2000-06-05
ATE89894T1 (de) 1993-06-15
US5040369A (en) 1991-08-20

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