EP0684385B1 - Compresseur avec dispositif de réduction de pression - Google Patents

Compresseur avec dispositif de réduction de pression Download PDF

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Publication number
EP0684385B1
EP0684385B1 EP95890053A EP95890053A EP0684385B1 EP 0684385 B1 EP0684385 B1 EP 0684385B1 EP 95890053 A EP95890053 A EP 95890053A EP 95890053 A EP95890053 A EP 95890053A EP 0684385 B1 EP0684385 B1 EP 0684385B1
Authority
EP
European Patent Office
Prior art keywords
pressure
compressor
valve
line
relief
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
Application number
EP95890053A
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German (de)
English (en)
Other versions
EP0684385A1 (fr
Inventor
Karl Rein
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.)
Hoerbiger Ventilwerke GmbH and Co KG
Original Assignee
Hoerbiger Ventilwerke GmbH and Co KG
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
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Publication of EP0684385A1 publication Critical patent/EP0684385A1/fr
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Publication of EP0684385B1 publication Critical patent/EP0684385B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/022—Stopping, starting, unloading or idling control by means of pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/01—Pressure before the pump inlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/06—Pressure in a (hydraulic) circuit
    • F04B2205/063—Pressure in a (hydraulic) circuit in a reservoir linked to the pump outlet

Definitions

  • the invention relates to a compressor with a device to lower the pressure when idling and when stopping, the Output of the compressor via a pressure accumulator and an adjoining one Supply line leads to a consumer and into the Intake line of the compressor a suction control valve controlling their passage is switched on by an actuator via a Control line is actuated depending on the pressure in the pressure accumulator, a pressure relief line leading away from the pressure accumulator for lowering the pressure is provided by a spring-loaded, on a desired pressure adjustable pressure control valve controlled and in Flow direction upstream of the pressure control valve depending on the pressure can be shut off in the supply line leading to the consumer.
  • Compressors with devices for reducing the pressure are also known (EP 0 130 662 A2), in which in the pressure relief line for pressure reduction a nozzle or throttle with a fixed passage cross-section is provided.
  • the passage cross section is dimensioned so that that in normal idle operation in the pressure accumulator to Ensuring the necessary pressure just stays upright. This lowering nozzle is therefore often of relatively small dimensions.
  • the Pressure reduction until the idle pressure starts from the full operating pressure is reached is therefore very slow.
  • Venting time when switching off the compressor is correspondingly long.
  • the Nozzle can be caused by contaminants carried in the pumped medium can be easily partially laid, reducing their passage cross-section and increases the time required to lower the pressure becomes. This has the consequence that the medium pressure in the container despite the Idle mode increases. This results in loss of drive energy, because the compressor is superfluous during this time Pressure level works, which must then be reduced uselessly.
  • the invention is based, the pressure reduction to improve in compressors in a simple way so that they both in Idling as well as when switching off the compressor as quickly and in in a manner adapted to the operating conditions to the desired one Printing takes place.
  • this object is achieved in that in the Pressure relief line in front of the pressure control valve a relief valve is installed and for further pressure reduction when the Compressor an additional, parallel to the first relief valve arranged second relief valve is provided, which from the immediate pressure in the intake line upstream of the compressor is acted upon and opens an additional relief path as soon as this pressure exceeds a certain level when the compressor is switched off.
  • each can Desired idle pressure regardless of the cross-section of the outflow opening be reached and held.
  • the outflow opening can be larger be dimensioned, which reduces the risk of laying. Any cross-sectional constrictions that may nevertheless occur can also occur can be compensated for by a slightly larger pressure control valve. This will ensure that the pressure relief valve is evenly rapid pressure relief ensures.
  • the additional second relief valve provided according to the invention also opens one when the compressor is turned off second relief route, so that in this case there is a rapid complete Pressure reduction is coming.
  • This second relief valve is from the in the suction line immediately before the compressor actuated, which is known to rise rapidly as soon as the compressor is turned off and a check valve in the suction line is closed.
  • the pressure control valve and the two relief valves to a pressure reduction unit be summarized in a common housing. Above all, this has the advantage that a compact unit is achieved and the necessary Connection lines can be significantly reduced.
  • the housing of the intake control valve to a common structural unit be assembled.
  • all are used to regulate the Compressor serving devices in a single device in the field the suction line combined so that connecting lines are largely eliminated can and especially for the entire arrangement only a little Space is required.
  • a preferred embodiment of the invention provides that the common housing of the pressure reduction unit has a cylinder bore has a piston sealed in each of its two end sections is performed and through the cylinder bore between the two pistons is divided into two transverse walls, each with a central bore, each of an extension of one of the two pistons are penetrated, the one Bore is provided as a guide for the one piston in the direction is loaded on the bore by a spring and on which the bore having transverse wall seals and the other hole is penetrated by an extension of the second piston in the area has a seal at its end and the bore in the transverse wall seals when enforcing, and that the housing has five connections has, one of which is in the cylinder space on the spring-loaded Side of one piston leads and with the control line for that Intake control valve is connected, the second port in the cylinder chamber of the opposite piston opens and with the suction line is connected immediately before the compressor, the third connection in leads the space between the two transverse walls of the cylinder bore, is connected to the pressure accumulator and in through the
  • the actuating device for the relief valve upstream of the pressure control valve which preferably consists of a solenoid valve, an adjustable one Delay relay to turn on when the compressor starts the closing of the relief valve is delayed.
  • This configuration causes that when starting the compressor after a standstill Relief valve initially open for a while and thus the pressure control valve remains effective, thereby preventing the pressure in the Pressure accumulator exceeds idle pressure during this time. It will So with this measure, the compressor system is initially warmed up enabled in idle mode and a too rapid increase in Delivery pressure of the compressor prevented during start-up.
  • the delay relay in the power supply line of the relief valve of the pressure control valve actuating the solenoid valve switched on. This arrangement results from reasons of expediency, because then a simple electrical delay relay is used can be.
  • FIGS. 1 to 4 Circuit diagrams of a schematically illustrated embodiment of the invention in the operating modes start, full load, idling and stop, Fig. 5 that Circuit diagram of a modified embodiment in the operating mode start, Fig. 6 shows a longitudinal section through the summarized inventive Pressure reduction unit and Fig. 7 is a longitudinal section through the intake control valve with pressure reduction unit attached to this.
  • FIGS. 1 to 4 exists from a compressor 1 designed as a screw compressor, which by an electric motor 2 is driven.
  • the power supply to the electric motor 2 and the associated switching device are not shown; it deals devices that are common in such drives, for example a three-phase motor with a star-delta switch for starting.
  • the compressor 1 is provided with an intake line shown enlarged 3 provided, in which a suction control valve 4 is installed, the one by an adjusting piston 5 adjustable closure piece 6, the can shut off the suction pipe 3 in the suction direction, but at the same time also acts as a check valve in the opposite direction.
  • That condensed Medium is from the compressor 1 via a pressure line 7 to a pressure accumulator 8 out, which is designed as an oil separator and in the a fine separator 9 is provided in the upper part.
  • a pressure accumulator 8 out which is designed as an oil separator and in the a fine separator 9 is provided in the upper part.
  • the pressure relief of the pressure accumulator 8th closes and prevents simultaneous pressure relief of the consumer.
  • the minimum pressure valve 11 also closes when the Pressure in the consumer drops below a minimum value to one prevent strong pressure drop in the pressure accumulator 8, which the Lubrication and the cooling of the compressor 1 would be at risk. It will This ensures that there is always sufficient pressure in the accumulator 8 Medium pressure is present to provide fluid from the accumulator 8 to the compressor 1 designed as a screw compressor guarantee.
  • the supplied via these lines 12, 13 Liquid is used to seal, cool and lubricate the screw compressor.
  • a solenoid valve 14 with a return spring 14 'and some others Valves provided, which will be described later.
  • the solenoid valve 14 is operated via two power lines 15, one in the drawing only indicated delay relay 16 is installed. Besides, that is Power line 15 with a switch 17 for optional switching on and off the control device and a pressure switch 18 provided, via a pressure monitoring line 19 with the supply line 10 is connected.
  • a control line is from the fine separator 9 of the pressure accumulator 8 20 led to the solenoid valve 14, which branches and via a branch line 21, in which another branch 22 is installed, each a relief valve 23 and 24 is guided, each by a return spring 25 and 26 are loaded.
  • To the relief valve 23 is a Line 27 a pressure holding valve 29 loaded by a spring 28 connected, from which a relief line 30 into the intake line 3 of the compressor 1 returns.
  • the second relief valve 24 is via a line 31 with the control valve 4 in connection.
  • the administration 31 starts from a point of the control valve 4 at which the pressure in the suction line 3 prevails immediately before the compressor 1.
  • a further line 32, which starts from the relief valve 24, opens into the Relief line 30 and thus also leads into the intake line 3 back.
  • a control line 33 is provided, which from Solenoid valve 14 in the cylinder chamber of the actuating piston 5 of the intake control valve 4 leads and from which a line branch 34 into the pressure maintaining valve 29 upstream first relief valve 23 for actuating the same flows.
  • the regulation of the delivery rate of the compressor 1 thus takes place through the intake control valve 4, the closure piece 6 of the cross section the intake line 3 more or less releases or closes as required.
  • Fig. 1 the position is shown, the start of the compressor system corresponds.
  • the switch 17 and the pressure switch 18 are closed, but the delay relay 16 delays for a while switching the magnetic switch 14. During this delay time the closure piece 6 closes the suction control valve 4.
  • a bypass channel 35 is provided, through which despite the closed Suction control valve a small amount of air can be sucked in which prevents the formation of an adverse negative pressure in the compressor 1 and at the same time building up a small pressure in the pressure accumulator 8 allows to lubricate and cool the as a screw compressor executed compressor 1 via the two liquid lines To ensure 12 and 13.
  • the pressure control valve 29 prevents open relief valve 23 an increase in pressure in the pressure accumulator 8 above a predetermined value, so that the compressor system during the delay time can warm up at idle.
  • the solenoid valve switches in the position shown in Fig. 2.
  • the medium pressure off the pressure accumulator 8 then passes through the control line 20 and Line branch 34 to the first relief valve 23, so that this too the force of the spring 25 switches.
  • the relief valve 23 is thereby closed, as shown in Fig. 2, in the control device is shown in the full load operating mode.
  • the Valves is also the control line 33 of the intake control valve 4 via the Control line 20 connected to the pressure accumulator 8, so that the actuating piston 5 of the intake control valve 4 from the one prevailing in the pressure accumulator 8 Pressure is applied, thereby extending and the closure piece 6 in the position of the largest flow cross-section, as in Fig. 2 illustrated by two fully marked arrows 37 and 38 is.
  • the compressor 1 thus works in this position of the control device at full load and supplied via the pressure accumulator 8 and Supply line 10 the connected consumer, not shown.
  • FIG. 3 This position of the control device is shown in Fig. 3 and corresponds to the idle operating mode. Since the control line 20 completed is, the control line 33 is depressurized, causing the control piston 5 under the action of its return spring 5 'and the closure piece 6 by the flow forces exerted on it by the sucked-in medium return to the closed position shown in FIG. 3.
  • the bypass channel 35 remains open, however, so that even in idle mode only medium is still sucked through the bypass channel 35, like the Arrow 36 indicates.
  • Fig. 4 is the position of the circuit arrangement when parking the compressor system shown.
  • the switch 17 is opened and at the same time the electric motor 2 switched off.
  • the pressure switch 18 is already open.
  • the control line 20 is closed by the solenoid valve 14, whereas the first relief valve 23 is open, so that in the pressure accumulator 8 still prevailing pressure via the control line 20, the Branch line 21, the relief valve 23 and the pressure holding valve 29 and then via the relief line 30 into the intake line 3 can be broken down.
  • FIG. 5 shows a modified embodiment, in which the intake control valve 4 has a different design than in the exemplary embodiment 1 to 4, but basically in the same Way works.
  • the essential valves of the Device for reducing the pressure in a common housing 39 summarized a pressure reduction unit. It is from Fig. 5 too recognize that the common housing 39 the two relief valves 23 and 24 and the pressure control valve 29 includes, the line connections largely between the individual valves in common Housing 39 itself are provided, so that a number of lines falls away.
  • Fig. 5 represents the operating state at the start of the system and is with the arrangement according to FIG. 1 comparable.
  • the common housing 39 has one that runs almost the entire length, but is offset several times Cylinder bore 40, which is provided with five connections.
  • the individual connections are to provide an easier overview with the same reference numbers as those following it Lines designated, but with the addition of a superscript Dashes.
  • a piston 41 is located in each of the two end sections of the bore 40 and 42 sealed out.
  • the cylinder bore is between the two pistons 40 divides the two by inserting them into them Form transverse walls 43 and 44, each with a central bore 45 and 46.
  • the two bores 45 and 46 are each from an extension 47 and 48 of the two pistons 41, 42 passes through, the bore 45 in the transverse wall 43 is provided as a guide for the piston 41.
  • the extension 47 has ribs for this purpose.
  • the piston 41 is in the direction loaded on the bore 45 by a spring 49 and strikes the Transverse wall 43 sealing.
  • the bore 46 in the transverse wall 44 is from an extension 48 of the second piston 42 passes through.
  • This extension 48 points in the area of its End a seal on, which seals the bore 46 when passing through.
  • connection 34 ′ leads from the five connections of the housing 39 in the cylinder space on the spring-loaded side of the piston 41 and 5 via the line branch 34 with the Control line 33 for the intake control valve 4 connected.
  • the second Port 31 ' opens into the cylinder space of the opposite piston 42 and is directly via line 31 to suction line 3 connected in front of the compressor 1.
  • the third connection 21 ' leads into the Space between the two transverse walls 43, 44 and is via the control line 20 connected to the pressure accumulator 8. He is through the two Piston 41.42 depending on the amount of pressure supplied either alternately or together with the fourth connection 32 ', the leads to the relief line 30, and the fifth terminal 30 ', the is directly connected to the pressure relief line 30.
  • the common housing 39 thus contains the first pressure relief valve 23, which is essentially formed by the spring-loaded piston 41 is, which also forms the pressure control valve 29, and also the second pressure relief valve 24, the function of the piston 42 is executed. So it results from using one summarized pressure reduction unit a significant simplification the entire arrangement, a saving of lines and thus also an increase in the operational reliability of the entire device for Pressure reduction.
  • connection 31 ' is in a recess in the cover plate 50 of the housing 39 directly with the interior of the Intake control valve 4 connected.
  • connection 34 ' is recessed in the housing 4, vertically extending channel 51 with the cylinder space below the Adjusting piston 5 of the intake control valve 4 in connection, so that here too a connecting line is omitted. So it's a summarized, easy-to-assemble and space-saving unit, all functions for rapid pressure reduction when idling and when stopping the compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Claims (6)

  1. Compresseur comportant un dispositif pour réduire la pression pendant le fonctionnement à vide ou lors d'un arrêt, dans lequel la sortie (7) du compresseur (1) mène à un dispositif consommateur via un accumulateur de pression (8) et via une conduite d'alimentation (10) qui se raccorde à celui-ci, et dans lequel une vanne de régulation d'aspiration (4) est branchée dans la conduite d'alimentation (3) du compresseur (1), qui commande son débit et qui est actionnée par un dispositif de réglage (5) via une conduite de commande (33) en dépendance de la pression dans l'accumulateur de pression (8), et dans lequel est prévue une conduite de décharge de pression (20, 21) s'éloignant de l'accumulateur de pression (8) pour réduire la pression, ladite conduite étant commandée par une vanne de maintien de pression (29) réglable à une pression désirée et chargée par un ressort, et susceptible d'être obturée en direction d'écoulement en avant de la vanne de maintien de pression (29) en fonction de la pression dans la conduite d'alimentation (10) menant vers le dispositif consommateur, caractérisé en ce qu'il est prévu une vanne de décharge (23) montée dans la conduite de décharge de pression (20, 21) en avant de la vanne de maintien de pression (29), et en ce qu'il est prévu en supplément une seconde vanne de décharge (24) agencée parallèlement à la première vanne de décharge (23) pour réduire davantage la pression lors d'un arrêt du compresseur, laquelle est sollicitée par la pression régnant directement en avant du compresseur (1) dans la conduite d'aspiration (3) et ouvre un chemin de décharge supplémentaire (22, 32) dès que cette pression dépasse une certaine valeur lors de l'arrêt du compresseur (1).
  2. Compresseur selon la revendication 1, caractérisé en ce que la vanne de maintien de pression (29) et les deux vannes de décharge (23, 24) sont regroupées dans un boítier commun (39) pour former une unité de réduction de pression.
  3. Compresseur selon la revendication 2, caractérisé en ce que le boítier commun (39) de l'unité de réduction de pression est assemblé avec le boítier de la vanne de régulation d'aspiration (4) pour former une unité structurelle commune (fig. 7).
  4. Compresseur selon l'une ou l'autre des revendications 2 et 3, caractérisé en ce que le boítier commun (39) de l'unité de réduction de pression présente un perçage cylindrique (40), dans les deux tronçons d'extrémité duquel est guidé avec étanchement un piston respectif (41, 42), et le perçage cylindrique (40) entre les deux pistons (41, 42) est subdivisé par deux parois transversales (43, 44) présentant chacune un perçage central (45, 46) traversé par un prolongement respectif (47, 48) de l'un des deux pistons (41, 42), l'un des perçages (45) étant prévu en tant que guidage pour l'un des pistons (41) qui est chargé par un ressort (49) vers le perçage (45) et qui bute avec étanchement contre la paroi transversale (43) présentant le perçage (45), et l'autre perçage (46) est traversé par un prolongement (48) du second piston (42) qui présente dans la région de son extrémité un joint d'étanchement et qui étanche le perçage (45) dans la paroi transversale (44) lors du passage, et en ce que le boítier (39) présente cinq raccords dont un premier (34') mène dans la chambre cylindrique sur le côté chargé par le ressort de l'un des pistons (41) et est relié à la conduite de commande (33) pour la vanne de régulation d'aspiration (4), dont un second raccord (31') débouche dans la chambre cylindrique du piston situé en vis-à-vis (42) et est relié à la conduite d'aspiration (3) directement en avant du compresseur (1), dont un troisième raccord (21') mène dans la chambre entre les deux parois transversales (43, 44) du perçage cylindrique (40), est raccordé à l'accumulateur de pression (8) et peut être relié par les deux pistons (41, 42), en dépendance de la hauteur de la pression appliquée, soit en alternance, soit conjointement avec le quatrième raccord (32') et le cinquième raccord (30'), qui débouchent tous les deux via des conduites de décharge de pression (32, 30) dans l'atmosphère ou dans la conduite d'aspiration (3).
  5. Compresseur selon l'une quelconque des revendications 1 à 4, caractérisé en ce qu'il est prévu un relais retardateur réglable (16) dans le dispositif d'actionnement pour la vanne d'obturation (23) agencée en amont de la vanne de maintien de pression (29) et constituée de préférence par une vanne magnétique (14), ledit relais retardant la fermeture de la vanne de décharge (23) lors du démarrage du compresseur (1).
  6. Compresseur selon la revendication 5, caractérisé en ce que le relais retardateur (16) est branché dans la ligne d'amenée de courant (15) de la vanne magnétique (14) qui actionne la vanne de décharge (23) de la vanne de maintien de pression (29).
EP95890053A 1994-03-30 1995-03-15 Compresseur avec dispositif de réduction de pression Expired - Lifetime EP0684385B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0067694A AT401551B (de) 1994-03-30 1994-03-30 Vorrichtung zur druckabsenkung eines verdichters
AT676/94 1994-03-30

Publications (2)

Publication Number Publication Date
EP0684385A1 EP0684385A1 (fr) 1995-11-29
EP0684385B1 true EP0684385B1 (fr) 1998-01-07

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP95890053A Expired - Lifetime EP0684385B1 (fr) 1994-03-30 1995-03-15 Compresseur avec dispositif de réduction de pression

Country Status (6)

Country Link
US (1) US5584673A (fr)
EP (1) EP0684385B1 (fr)
JP (1) JPH0849662A (fr)
AT (1) AT401551B (fr)
DE (1) DE59501201D1 (fr)
FI (1) FI108569B (fr)

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WO2012058069A2 (fr) 2010-10-27 2012-05-03 Dresser-Rand Company Système et procédé permettant la mise sous pression rapide d'un moteur/circuit de refroidissement pour un système de moteur/compresseur étanche
US9540998B2 (en) 2011-05-27 2017-01-10 Daniel K. Schlak Integral gas turbine, flywheel, generator, and method for hybrid operation thereof
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WO2016002635A1 (fr) * 2014-07-02 2016-01-07 株式会社日立産機システム Compresseur refroidi par un liquide et son procédé de fonctionnement
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US5584673A (en) 1996-12-17
AT401551B (de) 1996-10-25
JPH0849662A (ja) 1996-02-20
DE59501201D1 (de) 1998-02-12
ATA67694A (de) 1996-02-15
EP0684385A1 (fr) 1995-11-29
FI951489A0 (fi) 1995-03-29
FI951489A (fi) 1995-10-01
FI108569B (fi) 2002-02-15

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