EP0801227A2 - Procédé et dispositif pour influencer une soupape d'entrée pour un compresseur - Google Patents

Procédé et dispositif pour influencer une soupape d'entrée pour un compresseur Download PDF

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Publication number
EP0801227A2
EP0801227A2 EP97890047A EP97890047A EP0801227A2 EP 0801227 A2 EP0801227 A2 EP 0801227A2 EP 97890047 A EP97890047 A EP 97890047A EP 97890047 A EP97890047 A EP 97890047A EP 0801227 A2 EP0801227 A2 EP 0801227A2
Authority
EP
European Patent Office
Prior art keywords
pressure
opening
control device
closing member
control
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
EP97890047A
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German (de)
English (en)
Other versions
EP0801227B1 (fr
EP0801227A3 (fr
Inventor
Peter Dr. Steinrück
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 Kompressortechnik Services GmbH
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
Application filed by Hoerbiger Ventilwerke GmbH and Co KG filed Critical Hoerbiger Ventilwerke GmbH and Co KG
Publication of EP0801227A2 publication Critical patent/EP0801227A2/fr
Publication of EP0801227A3 publication Critical patent/EP0801227A3/fr
Application granted granted Critical
Publication of EP0801227B1 publication Critical patent/EP0801227B1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/08—Actuation of distribution members
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/06—Valve parameters
    • F04B2201/0601—Opening times
    • F04B2201/06011—Opening times of the inlet valve only

Definitions

  • the invention relates to a method for influencing the pressure-dependent, automatic, periodic opening movement of a closing element of a suction valve of a reciprocating compressor by means of a control device acting on the closing element, if necessary, at least over part of the crank circuit. Furthermore, the invention also relates to a corresponding device for influencing the pressure-dependent, automatic, periodic opening movement of a closing element of a suction valve of a reciprocating piston compressor, with a control device acting on the closing element at least over part of the crank circuit, if necessary, which has a hydraulic control cylinder, which has a control element can be periodically loaded and relieved with pressure medium.
  • compressor arrangements have become known in which, with the help of so-called lifting grippers, on the one hand a capacity control which is infinitely variable within certain limits is achieved by partially keeping the suction valves open during the compression cycle and on the other hand by means of corresponding ones Dimensioning of the mass of the lifting gripper and the arrangement of movement dampers a reduction in the impact speed of the closing member is achieved when closing.
  • the object of the invention is to improve a method and a device of the type mentioned in such a way that the abovementioned impact stress on the closing element or catcher is reduced in a simple manner at the end of the opening stroke and thus its effect on the life of the valve is reduced.
  • the invention is based on the finding that, in conventional valve designs of the type described in the introduction, when the pressure equilibrium between the cylinder space and the suction space is reached, the closing element of the valve is closed under the effect of its springing. As a result, the gas trapped in the cylinder continues to expand at an undiminished speed, which quickly results in a high negative pressure in the cylinder chamber, which, from a certain value and overcoming the springing of the closing element, results in a strong instantaneous acceleration of the closing element towards the catcher .
  • this existing control device is used to reduce the opening stroke, for which purpose, according to the invention, the closing member is forcibly opened under the action of the control device shortly before the pressure equilibrium between the cylinder space and the suction space of the compressor is reached becomes.
  • the control device or the lifting gripper is therefore brought up to the closing element a few degrees crank angle before the pressure equilibrium is reached, and this is raised shortly before the pressure equilibrium is reached, thus avoiding the suction in the indicator diagram, which is otherwise characteristic of automatic valves of the type described.
  • the closing element of the suction valve for example a one-part or multi-part If the valve plate is open when the pressure equilibrium is reached, pressure equalization can take place between the cylinder volume and the suction space, which ends the decompression phase in the cylinder.
  • the resulting maximum negative pressure in the cylinder chamber is now only determined by the throttle loss of the valve that is already open and is significantly lower than in the conventional case mentioned previously.
  • the differential pressure which causes the closing element of the suction valve to open further is significantly reduced, which also results in a significantly lower acceleration or impact speed of the closing element on the catcher.
  • the closing device is opened by the control device just before pressure equilibrium is reached.
  • this is pressed against the closing element or the valve plate by means of a spring and is in any case already there some time before the pressure equilibrium is reached.
  • the additional opening force caused by this pressure spring can, under certain circumstances, also open the closing member before pressure equilibrium is reached.
  • the mass of the lifting gripper must be accelerated by the spring force against the excess pressure in the cylinder space. Since the mass of such lifting grippers is inevitably relatively large compared to the mass of the closing members used, there is in any case only a slight acceleration and the premature opening of the closing member which is thereby brought about under certain circumstances is of subordinate magnitude.
  • the effect aimed at and achieved with the present invention of reducing the impact speed of the closing element on the catcher does not occur.
  • control device is delivered just before the pressure equilibrium is reached, so that the impulse, for example, of the lifting gripper is sufficient to open the closing element or the valve plate before the pressure equilibrium is reached, so this results in a premature, permanent opening of the closing element which is sufficient to achieve the desired effect.
  • the forced opening of the closing element which preferably takes place in the range from 20 ° to 0 ° crank angle before the pressure equilibrium between the cylinder and suction chamber is reached, is initiated in a further preferred embodiment of the invention by an impact of the control device on the closing element, the crank angle or
  • the time of the impact, as well as the mass ratio and the relative speed of the impact partners are chosen so that after the impact, the opening speed of the closing member does not drop to zero and preferably not below 10% of the speed that occurs immediately after the impact until it hits the catcher.
  • control device has a hydraulic control cylinder which is periodically acted upon and relieved of pressure medium by a control member, it is provided that the pressure at the control cylinder or control member causing the periodic opening of the closing member - or else the volume flow of the pressure medium, preferably via a measurement of the pressure drop at a throttle used in the inlet to the control member, and is used for indirect determination or monitoring of the opening speed of the closing member.
  • the control element of the device designed according to the invention can preferably have an electrically switching 3/2-way valve, the Control electronics is connected to an evaluation unit, which is further connected to at least one measuring sensor for monitoring the opening movement of the closing member.
  • the control device or the mentioned lifting gripper is thus actuated hydraulically, the feed movement preferably being initiated via an electrically switching, fast directional valve.
  • the time at which the corresponding infeed movement begins is determined by the changeover of this directional control valve and can be specified by a suitable device with a specification, for example the changeover crank angle, or by a control system which determines the optimal time.
  • the hydraulic pressure in the inlet of the 3/2-way valve mentioned can be measured.
  • the system pressure in the supply line is essentially measured at the measuring point.
  • the subsequent opening of the valve causes a dilution wave that spreads in the feed line at the speed of sound. A steep drop in ambient pressure will occur at the measuring location.
  • the pressure fluctuates between the system pressure and ambient pressure.
  • the pressure pulsations subside during the movement of the control device or the lifting gripper.
  • the frequency of these pulsations is determined by the distance of the 3/2-way valve from the next hydro-pneumatic pulsation damper or other expansion tank arranged in the inlet line.
  • the deceleration of the still flowing hydraulic column causes an upstream compression wave, which can be observed as a steep increase in pressure at the measuring point. From this point on, the pressure recorded at the measuring point fluctuates by a significantly higher value than before.
  • the control device reaches the closing element and comes to a standstill there because of the If the delivery time was chosen too early and the cylinder device pressure is still too high when the closing device reaches the closing element, the pressure increase described occurs or can be observed.
  • the control device or the lifting gripper can open the closing member or the valve plate directly. Only after the end position determined by the valve catcher does the closing member and the control device remain at rest, so that the pressure rise described above occurs only once during a working cycle of the compressor.
  • control device is likewise only stopped when the end position determined by the catcher is reached.
  • the optimum changeover time of the control member or of the 3/2-way valve thus results in the earliest point in time at which the steep pressure increase described above can be determined only once per working cycle of the compressor. This also applies if the closing element rebounds after reaching the end position and collides with the control device still in motion. In this case, the ratio of the mass of the control device to the mass of the closing element requires only a slight braking of the control device and no significantly detectable compression shaft.
  • the actually interesting course of motion of the closing element opened prematurely according to the invention via the course of the pressure on the control cylinder causing the periodic opening of the closing element or to determine the control device consists in monitoring the instantaneous pressure drop at a throttle used in the inlet to the control member.
  • This throttle is to be dimensioned accordingly, so that there is a measurable drop in the medium pressure behind the throttle at the speeds to be expected. If the movement of the control device or a lifting gripper begins, the differential pressure measured at the throttle also increases. If the control device reaches the closing element and comes to a standstill there because the delivery time was selected too early and when the control element still reaches an excessively high cylinder chamber pressure, the differential pressure to be determined at the throttle reaches a minimum.
  • the course of the indicator pressure in the cylinder space can also be monitored and the time of opening of the closing member can be selected so that the suction tip is minimized in the indicator diagram or made to disappear.
  • the indicator diagram of course, a representation of the pressure over the crank angle or over time can also be used.
  • the crank angle or time of opening of the closing member can also be selected so that the intensity of the opening stroke determined by vibration monitoring in the valve area is minimized.
  • the opening stroke of valves causes a pulse-like excitation of the natural vibrations of the valve holding devices. These structure-borne noise vibrations quickly subside within a characteristic time.
  • the intensity of the opening stroke can now be quantified in the manner described by measuring the accelerations occurring, for example, on the valve cover in the direction of the valve axis in the time window after the valve has opened until after the time characteristic of the decay behavior has expired. These detectable accelerations are usually in very high frequency ranges.
  • the intensity of the vibrations derived from the recording of the envelope of the vibrations or, in a particularly simple manner, the shape of the amplitude by low-pass filtering of the rectified oscillating signal can therefore be used for the assessment of the opening stroke.
  • the optimal delivery time of the control device or a lifting gripper or the like can thus advantageously be determined directly by minimizing the intensity of the vibrations caused by the opening stroke of the valve.
  • a further embodiment of the invention is advantageous, according to which the selection or setting of the start of the delivery of the control device is made only when the compressor is started up or inspected. In this case, it is sufficient to optimize the delivery time using special commissioning or inspection measuring devices, which allow the use of the methods described above.
  • a preferred further embodiment of the invention can also provide for ongoing monitoring and adaptation of the start of the delivery of the control device. For this, continuous monitoring of one of the above is then carried out Measured variables and the periodic execution of the described optimization processes are necessary.
  • FIG. 1 shows a basic circuit diagram for the method and device according to the present invention
  • FIG. 2 shows a schematic diagram of another device according to the invention or for carrying out the method according to the invention
  • FIG. 3 shows the time course of the stroke of the closing element for different delivery times of the control device 4 shows the corresponding course of the opening speed of a closing element actuated according to FIG. 3
  • FIG. 5 shows the time course of the pressure in the cylinder chamber just before and after the pressure equilibrium between the cylinder chamber and the suction chamber has been reached
  • FIG. 1 shows a basic circuit diagram for the method and device according to the present invention
  • FIG. 2 shows a schematic diagram of another device according to the invention or for carrying out the method according to the invention
  • FIG. 3 shows the time course of the stroke of the closing element for different delivery times of the control device 4 shows the corresponding course of the opening speed of a closing element actuated according to FIG. 3
  • FIG. 5 shows the time course of the pressure in the cylinder chamber just before and after the pressure equilibrium between the cylinder chamber
  • FIGS. 7 to 10 each show variants of schematic devices for carrying out process configurations according to the present invention.
  • the reciprocating compressor shown schematically in FIG. 1 has a crankshaft 1 to which a flywheel 2 is flanged and which actuates pistons 4 of double-acting cylinders 5 via connecting rods or push rods 3. Via the oscillating movement of the pistons 4, gas is drawn in via suction valves 6, the closing element 7 of which can move between a catcher 8 and the valve seat 9. After the respective suction valve 6 has automatically closed, the sucked-in gas is compressed in the cylinder 5 or ejected via the pressure valves 10, which are likewise automatic here.
  • the pressure-dependent, automatic periodic opening movement of the closing members 7, for example a valve plate or the like, of the suction valves 6 is carried out by means of a, if necessary, at least part of the Crank circuit on the closing member 7 acting control device 12 influenced.
  • This control device 12 can, for example, have a lifting gripper 13, which is only indicated here and which forcibly opens the closing member 7 via a hydraulic control cylinder 14 shortly before the pressure equilibrium between the cylinder space 15 and the suction space of the compressor outside the suction valve 6 is reached.
  • the control device 12 includes an electronic control, not shown here, which is coordinated by means of a bus connection 16, which effects the exchange of information between the control device 12 and an evaluation unit 17.
  • the evaluation unit 17 is supplied via a line 18 with the signal of an encoder 19 arranged on the flywheel 2 for dead center or crank angle, with which the influencing of the closing elements 7 via the lifting gripper 13 can be synchronized with the oscillating movement of the pistons 4.
  • FIG. 2 shows the control device 12 from FIG. 1 on one of the two suction valves 6 in more detail.
  • the lifting gripper 13 acting on the closing element 7 of the suction valve 6, again only shown symbolically, is actuated by a hydraulic control cylinder 14.
  • the hydraulic fluid fed via an inlet line 21 can act on the control cylinder 14 in the position shown of a control member 22 designed here as a 3/2-way valve 20 and thus press the lifting gripper 13 against the closing member 7.
  • gas forces act on the closing member 7 and seek to close the valve 6.
  • a check valve 23 the hydraulic fluid locked in the control cylinder 14 is prevented from flowing back and thereby the closing element 7 of the suction valve 6 is blocked in the open position.
  • a coil 24 Only when the valve 20 is switched by energizing a coil 24 is the control cylinder 14 connected to an outflow line 25 and thereby the closing movement of the suction valve 6 initiated or enabled.
  • the coil 24 is supplied by an electronic circuit arranged in a housing 26, which thus determines the actuation of the valve 20 over time.
  • the corresponding actuation times are determined on the one hand by synchronizing pulses which are sent to the electronics via the bus connection 16, and on the other hand by parameters also communicated via the bus connection 16, such as the time interval, expressed in degrees crank angle (° KW), of the switching times for the synchronizing pulse of the encoder 19, set.
  • those angles of the crank circuit (flywheel 2) are determined for each control device 12, at which the valve 20 is opened (angle: KWon) or deactivated (KWoff) by feeding the coil 24.
  • FIG. 3 shows typical courses of the opening movement of a closing element (7 in FIGS. 1 and 2) of a suction valve (6 in FIGS. 1 and 2), which is controlled by the method according to the invention.
  • the stroke plotted on the vertical is plotted as a relative stroke based on the total stroke of the closing element over a dimensionless ratio time.
  • the time scale is selected so that when the upper end of movement in the illustration is reached, the dimensionless time is set to -1 and when the lower end of movement is reached to 0.
  • FIG. 4 shows the course of the speed of the closing element belonging to FIG. 3 over the dimensionless ratio time, a suitable speed scale that is not of interest being selected. 5 accordingly shows the pressure curves in the compressor cylinder.
  • the curves labeled A represent the case in which the lifting gripper (13 in FIGS. 1 and 2) is delivered too late.
  • the closing element 7 opens only under the effect of the differential pressure between the cylinder space and the suction space of the compressor.
  • the rapid drop in cylinder pressure after passing through the pressure equilibrium causes a strong one Acceleration of the closing member, a high impact speed on the catcher (8 in Fig. 1 and 2) and thus a strong and undesirable opening blow.
  • the closing element can also bounce back under the action of the usual valve springing and come to rest only after one or more bumps in the open position.
  • the curves denoted by B represent the course of the opening for a delivery point in time of the lifting gripper which is optimized in accordance with the present invention (13 in FIGS. 1 and 2).
  • the closing element of the suction valve is pressed open just before the pressure equilibrium is reached due to the effect of the gripper shock, so that when the pressure equilibrium between the cylinder space and the suction space is reached, the suction valve is already largely open.
  • the filling of the cylinder space (15 in FIGS. 1 and 2) with gas can begin immediately after passing through the pressure equilibrium.
  • the suction tip which occurs in the case of conventionally designed suction valves and is described at the outset is largely avoided. Consequently, significantly lower opening forces act on the closing element of the suction valve compared to a conventionally designed suction valve and - as can be seen in FIG. 4 - the closing element hits the catcher of the valve with a significantly reduced impact speed.
  • the curves labeled A correspond to a KWoff of 38 °
  • the curves labeled B correspond to a KWoff of 34 °
  • the curves labeled C correspond to a KWoff of 32 °.
  • FIG. 6 shows the influence of the time of delivery of the lifting gripper (13 in FIGS. 1 and 2) on the opening stroke on the basis of measurement results with another embodiment.
  • the vibrations or accelerations measured at the valve nest are plotted against the time in ms for different times or crank angles of the delivery of the lifting gripper.
  • the time course of the indicator pressure (cylinder interior) is also shown in FIG. 6 - the corresponding curve is designated by H.
  • FIG. 7 shows, in a representation similar to FIG. 2, an example of the application of the method according to the invention for the indirect determination of the opening speed of the closing element 7 by means of monitoring the hydraulic medium pressure which causes the closing element 7 to open periodically.
  • a via a line 27 with the inlet line 21 in Connected measuring sensor 28 used for the inlet pressure the measuring signals are evaluated by the electronic circuit arranged in the housing 26.
  • Figure 8 relates to a variant of the method in which, for the indirect monitoring of the opening speed of the sealing element 7, a measurement or monitoring of the pressure drop at a throttle 29 used in the feed line 21 to the control member 22 by means of a measuring sensor 28 which measures the differential pressure upstream and downstream of the throttle 29 is carried out.
  • the time of the forced opening of the closing member 7 is selected such that the intensity of the opening stroke determined by means of the measuring sensor 28 via vibration monitoring in the valve area is minimized.
  • the measurement sensor 28 acting as an acceleration sensor could also be attached directly to the cylinder 5 at a suitable location, for example in the immediate vicinity of the suction valve 6. Signals of the measuring sensor 28 are in turn evaluated in the circuit electronics arranged in the housing 26 in a manner not shown and used to determine the initiation of the opening process of the closing element 7.
  • the time of initiation of the opening of the closing member 7 is selected so that the under-suction tip is minimized in the indicator diagram.
  • the indicator pressure is measured here by means of the measuring sensor 28 in the form of a pressure sensor, the signal of which is amplified by a measuring amplifier 30 and displayed as an indicator diagram over the piston stroke with the aid of a suitable display device 31 or alternatively is also displayed as a time signal.
  • the time of opening of the closing member can again be selected here in such a way that the under-suction tip is minimized in the indicator diagram in the manner mentioned.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP97890047A 1996-04-12 1997-03-14 Procédé et dispositif pour influencer une soupape d'entrée pour un compresseur Expired - Lifetime EP0801227B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT662/96 1996-04-12
AT66296 1996-04-12
AT0066296A AT409655B (de) 1996-04-12 1996-04-12 Verfahren und einrichtung zur beeinflussung eines kompressor-saugventils

Publications (3)

Publication Number Publication Date
EP0801227A2 true EP0801227A2 (fr) 1997-10-15
EP0801227A3 EP0801227A3 (fr) 1999-03-03
EP0801227B1 EP0801227B1 (fr) 2003-07-09

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP97890047A Expired - Lifetime EP0801227B1 (fr) 1996-04-12 1997-03-14 Procédé et dispositif pour influencer une soupape d'entrée pour un compresseur

Country Status (6)

Country Link
US (1) US5988985A (fr)
EP (1) EP0801227B1 (fr)
JP (1) JPH1030564A (fr)
AT (1) AT409655B (fr)
DE (1) DE59710392D1 (fr)
ES (1) ES2203781T3 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001059266A1 (fr) * 2000-02-07 2001-08-16 Compart Compressor Technology Gmbh & Co. Kg Dispositif et procede de commande d'une machine a piston
WO2008000698A2 (fr) 2006-06-28 2008-01-03 Dott. Ing. Mario Cozzani S.R.L. Équipement pour la régulation continue du débit de compresseurs alternatifs
WO2011009880A1 (fr) 2009-07-23 2011-01-27 Burckhardt Compression Ag Procédé de régulation de débit et compresseur à piston élévateur doté d'une régulation de débit
EP2511526B1 (fr) 2011-04-14 2019-08-21 Hoerbiger Wien GmbH Compresseur à piston élévateur avec réglage du débit de refoulement

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EP1338794A1 (fr) * 2002-02-26 2003-08-27 Whirlpool Corporation Pompe à piston pour refrigerateur avec des panneaux isolants sous vide
ITBO20030390A1 (it) * 2003-06-23 2004-12-24 Magneti Marelli Powertrain Spa Metodo e dispositivo di controllo della velocita' delle valvole
JP3904002B2 (ja) * 2004-06-18 2007-04-11 ダイキン工業株式会社 振動式圧縮機
ITGE20080036A1 (it) * 2008-04-30 2009-11-01 Dott Ing Mario Cozzani Srl Metodo per il controllo della posizione di un attuatore elettromeccanico per valvole di compressori alternativi.
EP2456978B1 (fr) 2009-07-23 2016-03-09 Burckhardt Compression AG Procédé de régulation de débit et compresseur à piston élévateur doté d'une régulation de débit
EP2456979B1 (fr) 2009-07-23 2016-12-28 Burckhardt Compression AG Procédé de régulation du débit de refoulement et compresseur à piston à régulation de débit de refoulement
DE202010002145U1 (de) * 2010-02-09 2011-09-07 Vacuubrand Gmbh + Co Kg Membranvakuumpumpe
CN102705199B (zh) * 2012-06-30 2014-09-17 柳州市金螺机械有限责任公司 压缩机
EP3994570A4 (fr) 2019-07-01 2023-06-14 FW Murphy Production Controls, LLC Système de surveillance de compresseur de gaz naturel intuitif

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001059266A1 (fr) * 2000-02-07 2001-08-16 Compart Compressor Technology Gmbh & Co. Kg Dispositif et procede de commande d'une machine a piston
WO2008000698A2 (fr) 2006-06-28 2008-01-03 Dott. Ing. Mario Cozzani S.R.L. Équipement pour la régulation continue du débit de compresseurs alternatifs
WO2008000698A3 (fr) * 2006-06-28 2008-02-14 Dott Ing Mario Cozzani Srl Équipement pour la régulation continue du débit de compresseurs alternatifs
CN101479479B (zh) * 2006-06-28 2011-11-02 工学博士马里奥·科扎尼有限责任公司 用于往复式压缩机的流量的连续调节的装备
WO2011009880A1 (fr) 2009-07-23 2011-01-27 Burckhardt Compression Ag Procédé de régulation de débit et compresseur à piston élévateur doté d'une régulation de débit
WO2011009879A1 (fr) 2009-07-23 2011-01-27 Burckhardt Compression Ag Procédé de régulation du débit de refoulement et compresseur à piston à régulation de débit de refoulement
EP2511526B1 (fr) 2011-04-14 2019-08-21 Hoerbiger Wien GmbH Compresseur à piston élévateur avec réglage du débit de refoulement

Also Published As

Publication number Publication date
JPH1030564A (ja) 1998-02-03
EP0801227B1 (fr) 2003-07-09
US5988985A (en) 1999-11-23
ES2203781T3 (es) 2004-04-16
DE59710392D1 (de) 2003-08-14
EP0801227A3 (fr) 1999-03-03
ATA66296A (de) 2002-02-15
AT409655B (de) 2002-10-25

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