EP1650434B2 - Multi-stage piston type compressor with reduced power input during idle running - Google Patents

Multi-stage piston type compressor with reduced power input during idle running Download PDF

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Publication number
EP1650434B2
EP1650434B2 EP05022666.1A EP05022666A EP1650434B2 EP 1650434 B2 EP1650434 B2 EP 1650434B2 EP 05022666 A EP05022666 A EP 05022666A EP 1650434 B2 EP1650434 B2 EP 1650434B2
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EP
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Prior art keywords
compressor
stage
valve
valve chamber
chamber
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German (de)
French (fr)
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EP1650434A2 (en
EP1650434A3 (en
EP1650434B1 (en
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Jörg Nickl
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Voith Patent GmbH
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Voith Patent GmbH
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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
    • 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
    • F04B49/08—Regulating by delivery 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
    • F04B25/00—Multi-stage pumps
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/005—Multi-stage pumps with two cylinders
    • 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
    • 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
    • F04B49/03—Stopping, starting, unloading or idling control by means of 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
    • F04B49/22—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
    • F04B2205/00—Fluid parameters
    • F04B2205/07—Pressure difference over the pump

Definitions

  • the invention relates to a multi-stage piston compressor with reduced power consumption in the absence of back pressure (idle).
  • Piston compressors are used for the compression of gases, usually air, which is to be used as a working medium for the operation of various aggregates.
  • gases usually air
  • Such compressors operate e.g. to a compressed air tank, i.
  • the compressed air tank is filled with compressed air until a specifiable pressure level is reached.
  • a control valve disposed between the compressor and the air reservoir opens, so that the air supplied from the compressor escapes.
  • the compressor itself often can not be switched off because it is e.g. is fixedly coupled to the vehicle engine.
  • Knorr Brakes Power Reduction System
  • WABCO ESS System, Energy Saving System
  • a multistage reciprocating compressor for compressing compressible media having at least one upstream compressor stage and at least one downstream compressor stage, each compressor stage including at least one piston guided in a cylinder space, an inlet valve chamber connected to the cylinder space through an intake valve, and one with the cylinder space through an exhaust valve having connected outlet valve chamber.
  • the object of the present invention is to provide a multi-stage compressor of the type described, which has a lower power consumption in the absence of back pressure .DELTA.p than known multi-stage and single-stage compressor.
  • the multistage reciprocating compressor for compressing compressible media comprises at least one upstream and at least one downstream compressor stage, each compressor stage comprising at least one piston guided in a cylinder chamber and one inlet valve chamber connected to the cylinder chamber through an inlet valve and one outlet valve chamber connected to the cylinder chamber through an outlet valve , and is characterized in that at least one upstream compressor stage, the inlet valve chamber is connected by at least one additional valve to the cylinder chamber, which is in an open position at rest and moves to a closed position when the differential pressure .DELTA.p between the exhaust valve chamber of the farthest downstream compressor stage and the inlet valve chamber of the upstream compressor stage exceeds a predetermined value.
  • the medium to be compressed enters the first compressor stage at a pressure p.
  • This first compressor stage is arranged upstream of all subsequent compressor stages.
  • the medium is compressed and fed to the next compressor stage, in which it is further compressed, etc.
  • the medium eventually exits at the pressure p + ⁇ p.
  • the invention Exceeds the differential pressure Ap between the input and the output of the multi-stage compressor, a predetermined value, the invention provided additional valve from the open position, in which it is in the rest position, moved to a closed position, so that the medium in this upstream compressor stage is compressed, ie that equipped with the additional valve, upstream of the last compressor stage arranged compressor stage operates.
  • the filling of the pressure vessel is stopped by opening the overflow valve so that the medium can escape.
  • the differential pressure ⁇ p between the input and the output of the multi-stage compressor drops to a value close to zero.
  • the additional valve moves back to the open position, so that the medium within the compressor stage equipped with the additional valve is not compressed, i. that equipped with the additional valve, upstream of the last compressor stage arranged compressor stage is idle.
  • the discharge valve chamber of the compressor stage located furthest downstream is connected to the additional valve provided in the inlet valve chamber of at least one upstream compressor stage through a pipeline.
  • a pneumatic actuation of the additional valves or by the medium to be compressed itself is provided.
  • the outlet valve chamber of the last compressor stage is connected to the arranged in the inlet valve chamber of the upstream compressor stage or compressor stages additional valve.
  • This embodiment has the advantage that the valve is actuated by the differential pressure ⁇ p without the interposition of complicated control or regulating devices.
  • the compressor according to the invention can be produced inexpensively, is self-regulating and maintenance-free.
  • the outlet valve chamber of the compressor stage located furthest downstream is connected to the additional valves arranged in the inlet valve chambers of a plurality of upstream compressor stages by a branching pipeline.
  • a spring is provided which holds the additional valve in the idle state and at a differential pressure Ap, which is below the predetermined value, in the open position or moves from the closed position to the open position.
  • the provision of the additional valve in the open position could again be done magnetically, electrically or in another suitable manner.
  • actuators or special structural designs of the additional valve would be required.
  • the provision of the additional valve by a Federist contrast mechanically easier to implement and cheaper to produce.
  • the spring is a leaf spring with an end designed as a fork, which engages in a groove provided for this purpose of the additional valve.
  • a further advantageous solution is the use of a helical spring into which the additional valve is inserted. Further constructive embodiments using one or more springs are possible without departing from the spirit of the invention.
  • a heat exchanger for cooling the compressible medium is provided between at least two compressor stages.
  • the differential pressure ⁇ p required to actuate the additional valve.
  • This differential pressure ⁇ p acts via a pipeline to the additional valve. If the differential pressure ⁇ p reaches a predetermined value, the pressure force on the auxiliary valve exceeds the associated spring force of the spring, whereby the additional valve closes and the lower, i. upstream stages begin to work.
  • This system has the advantage over similar systems for single-stage compressors, to get along directly with the pressure level at the compressor outlet for controlling such a valve. No additional signalers, control devices or the like are needed.
  • the system automatically detects when no air delivery is required. It works safely and is immune to interference.
  • the system is simple in construction and therefore inexpensive to produce.
  • the multi-stage piston compressor for compressing compressible media has two compressor stages 1,2.
  • Each compressor stage 1, 2 consists of a piston (not shown) guided in a cylinder chamber 11,21 and an inlet valve chamber 13,23 connected to the cylinder chamber 11,21 through an inlet valve 12,22 and one with the cylinder chamber 11,21 Outlet valve 14,24 connected outlet valve chamber 15,25.
  • the last compressor stage 2 upstream compressor stage 1 has an additional valve 16, through which the inlet valve chamber 13 is connected to the cylinder chamber 11.
  • the outlet valve chamber 25 of the last compressor stage 2 which is thus arranged furthest downstream, is connected to the additional valve 16 arranged in the inlet valve chamber 13 of the first compressor stage 1, which is arranged upstream, through a pipeline 3.
  • a spring 18 is provided which keeps the auxiliary valve 16 in the open position and at a differential pressure ⁇ p between the inlet and the outlet of the multi-stage compressor, which is below a predetermined value in the open position or . Moved from the closed position to the open position.
  • the predetermined value of the differential pressure is proportional to the spring rate of the spring 18 in this embodiment.
  • the spring 18 is a leaf spring with an end running as a fork. The forked end of the leaf spring 18 engages in a designated groove 17 of the additional valve 16 a.
  • a heat exchanger 4 is provided for cooling the compressible medium.
  • the additional valve 16 is in Fig. 1 shown in the closed position.
  • the container to be filled (not shown) does not have the desired internal pressure. Therefore, the spill valve (not shown) is closed and the multi-stage compressor operates against the internal pressure of the closed system.
  • the differential pressure ⁇ p between the discharge valve chamber 25 of the compressor stage 2 located furthest downstream and the inlet valve chamber 13 of the upstream compressor stage 1 has exceeded the predetermined value. This differential pressure is applied through the pipe 3 to the additional valve 16 and is sufficient to move the additional valve 16 against the force of the spring 18 in the closed position. As a result, there is no permanent connection between the inlet valve chamber 13 and the cylinder chamber 11 of the first compressor stage 1 and the medium is compressed in the first compressor stage 1.
  • Fig. 2 the auxiliary valve 16 is shown in the open position.
  • the container to be filled (not shown) has reached the desired internal pressure. Therefore, the spill valve (not shown) is opened and the multi-stage compressor does not work against the internal pressure of the closed system.
  • the differential pressure ⁇ p between the exhaust valve chamber 25 of the compressor stage 2 located farthest downstream and the inlet valve chamber 13 of the upstream compressor stage 1 is approximately zero, that is, the differential pressure ⁇ p has fallen below the predetermined value.
  • the force of the spring 18 moves the additional valve 16 back into the open position.

Abstract

The multi level piston compressor has an intake valve chamber (13) whereby upstream compressor level (1) is arranged on the intake valve. An auxiliary valve (16) is connected with the cylinder space (11). The auxiliary valve is in stand still state in open position and moves in closed position. The differential pressure is examined in the down stream compressor level (2) of the exhaust valve chamber (25).

Description

Die Erfindung betrifft einen mehrstufigen Kolbenverdichter mit reduzierter Leistungsaufnahme bei fehlendem Gegendruck (Leerlauf).The invention relates to a multi-stage piston compressor with reduced power consumption in the absence of back pressure (idle).

Kolbenverdichter dienen der Kompression von Gasen, meist Luft, die als Arbeitsmedium zum Betrieb verschiedenster Aggregate genutzt werden soll. Im Betrieb arbeiten derartige Verdichter z.B. auf einen Druckluftbehälter, d.h. der Druckluftbehälter wird mit komprimierter Luft befüllt, bis ein vorgebbares Druckniveau erreicht ist. Zu diesem Zeitpunkt öffnet ein zwischen dem Verdichter und dem Druckluftbehälter angeordnetes Regelventil, so dass die vom Verdichter geförderte Luft entweicht. Der Verdichter selbst kann oftmals nicht abgeschaltet werden, da er z.B. mit dem Fahrzeugmotor fest gekoppelt ist.Piston compressors are used for the compression of gases, usually air, which is to be used as a working medium for the operation of various aggregates. In operation, such compressors operate e.g. to a compressed air tank, i. The compressed air tank is filled with compressed air until a specifiable pressure level is reached. At this time, a control valve disposed between the compressor and the air reservoir opens, so that the air supplied from the compressor escapes. The compressor itself often can not be switched off because it is e.g. is fixedly coupled to the vehicle engine.

Zwischen dem Regelventil und dem Verdichter befinden sich jedoch im Allgemeinen längere Druckleitungen, so dass der Verdichter bei geöffnetem Regelventil immer noch gegen den Rohrleitungswiderstand bzw. gegen einen gewissen Gegendruck arbeiten muss. Zudem tritt in diesem Fall bei mehrstufigen Verdichtern auf Grund der unterschiedlichen Hubvolumina der einzelnen Stufen der Effekt auf, dass die unteren Stufen eine deutliche indizierte Arbeit leisten müssen.However, there are generally longer pressure lines between the control valve and the compressor, so that the compressor still has to work against the pipe resistance or against a certain back pressure with the control valve open. In addition, in this case occurs in multi-stage compressors due to the different stroke volumes of the individual stages of the effect that the lower levels must perform a significant indexed work.

Um hier Abhilfe zu schaffen, sind derzeit bei einstufigen Verdichtern aufwändige Regeleinrichtungen vorgesehen, die zusätzliche Leitungen und Messeinrichtungen erfordern. Mit diesen Regeleinrichtungen wird dann bei Erreichen des voreingestellten Druckes im Behälterzusätzlich am Verdichterein Überströmventil elektromechanisch oder pneumatisch geöffnet, so dass der weiter laufende Verdichter nicht mehr gegen einen Gegendruck arbeitet. Die Folge ist eine Energieeinsparung und es treten nur noch Reibungsverluste auf.To remedy this situation, sophisticated control devices are currently provided for single-stage compressors, which require additional lines and measuring equipment. With these control devices, an overflow valve is then opened electromechanically or pneumatically upon reaching the preset pressure in the tank, additionally at the compressor, so that the further running compressor no longer works against a back pressure. The result is an energy saving and there are only frictional losses.

Derartige Systeme werden von Knorr Bremsen (Power Reduction System) und WABCO (ESS-System, Energiesparsystem) eingesetzt.Such systems are used by Knorr Brakes (Power Reduction System) and WABCO (ESS System, Energy Saving System).

Aus der deutschen Offenlegungsschrift 1 403 953 ist ein mehrstufiger Kolbenverdichter zur Verdichtung kompressibler Medien mit mindestens einer stromaufwärts angeordneten Verdichterstufe und mindestens einer stromabwärts angeordneten Verdichterstufe bekannt, wobei jede Verdichterstufe mindestens einen in einem Zylinderraum geführten Kolben, eine mit dem Zylinderraum durch ein Einlassventil verbundene Einlassventilkammer und eine mit dem Zylinderraum durch ein Auslassventil verbundene Auslassventilkammer aufweist.From the German Offenlegungsschrift 1 403 953 a multistage reciprocating compressor is known for compressing compressible media having at least one upstream compressor stage and at least one downstream compressor stage, each compressor stage including at least one piston guided in a cylinder space, an inlet valve chamber connected to the cylinder space through an intake valve, and one with the cylinder space through an exhaust valve having connected outlet valve chamber.

Die Aufgabe der vorliegenden Erfindung besteht darin, einen mehrstufigen Verdichter der beschriebenen Art anzugeben, der bei fehlendem Gegendruck Δp eine geringere Leistungsaufnahme aufweist als bekannte mehr- und einstufige Verdichter.The object of the present invention is to provide a multi-stage compressor of the type described, which has a lower power consumption in the absence of back pressure .DELTA.p than known multi-stage and single-stage compressor.

Erfindungsgemäß wird die Aufgabe gelöst durch einen mehrstufigen Verdichter mit den Merkmalen des Anspruchs 1. Vorteilhafte Ausgestaltungen der Erfindung sind Gegenstand der abhängigen Ansprüche.According to the invention the object is achieved by a multi-stage compressor with the features of claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.

Der mehrstufige Kolbenverdichter zur Verdichtung kompressibler Medien umfasst mindestens eine stromaufwärts und mindestens eine stromabwärts angeordnete Verdichterstufe, wobei jede Verdichterstufe mindestens einen in einem Zylinderraum geführten Kolben sowie je eine mit dem Zylinderraum durch ein Einlassventil verbundene Einlassventilkammer und eine mit dem Zylinderraum durch ein Auslassventil verbundene Auslassventilkammer aufweist, und ist dadurch gekennzeichnet, dass bei mindestens einer stromaufwärts angeordneten Verdichterstufe die Einlassventilkammer durch mindestens ein Zusatzventil mit dem Zylinderraum verbunden ist, das sich im Ruhezustand in einer Öffnungsstellung befindet und das sich in eine Schließstellung bewegt, wenn der Differenzdruck Δp zwischen der Auslassventilkammer der am weitesten stromabwärts angeordneten Verdichterstufe und der Einlassventilkammer der stromaufwärts angeordneten Verdichterstufe einen vorgebbaren Wert überschreitet.The multistage reciprocating compressor for compressing compressible media comprises at least one upstream and at least one downstream compressor stage, each compressor stage comprising at least one piston guided in a cylinder chamber and one inlet valve chamber connected to the cylinder chamber through an inlet valve and one outlet valve chamber connected to the cylinder chamber through an outlet valve , and is characterized in that at least one upstream compressor stage, the inlet valve chamber is connected by at least one additional valve to the cylinder chamber, which is in an open position at rest and moves to a closed position when the differential pressure .DELTA.p between the exhaust valve chamber of the farthest downstream compressor stage and the inlet valve chamber of the upstream compressor stage exceeds a predetermined value.

Das zu komprimierende Medium tritt mit einem Druck p in die erste Verdichterstufe ein. Diese erste Verdichterstufe ist gegenüber allen nachfolgenden Verdichterstufen stromaufwärts angeordnet. In der ersten Verdichterstufe wird das Medium komprimiert und der nächsten Verdichterstufe zugeleitet, in deres weiterverdichtet wird usw.. Aus der letzten Verdichterstufe, d.h. der am weitesten stromabwärts angeordneten Verdichterstufe, tritt das Medium schließlich mit dem Druck p+Δp aus.The medium to be compressed enters the first compressor stage at a pressure p. This first compressor stage is arranged upstream of all subsequent compressor stages. In the first stage of compression, the medium is compressed and fed to the next compressor stage, in which it is further compressed, etc. From the last compressor stage, i. At the most downstream stage of the compressor, the medium eventually exits at the pressure p + Δp.

Überschreitet der Differenzdruck Δp zwischen dem Eingang und dem Ausgang des mehrstufigen Verdichters einen vorgebbaren Wert, so wird das erfindungsgemäß vorgesehene Zusatzventil aus der Öffnungsstellung, in der es sich in der Ruhelage befindet, in eine Schließstellung bewegt, so dass das Medium in dieser stromaufwärts angeordneten Verdichterstufe komprimiert wird, d.h. dass die mit dem Zusatzventil ausgestattete, stromaufwärts vor der letzten Verdichterstufe angeordnete Verdichterstufe arbeitet.Exceeds the differential pressure Ap between the input and the output of the multi-stage compressor, a predetermined value, the invention provided additional valve from the open position, in which it is in the rest position, moved to a closed position, so that the medium in this upstream compressor stage is compressed, ie that equipped with the additional valve, upstream of the last compressor stage arranged compressor stage operates.

Wenn der zu füllende Druckbehälter einen vorgegebenen Innendruck erreicht hat, wird die Befüllung des Druckbehälters beendet, indem das Überstromventil geöffnet wird, so dass das Medium entweichen kann. Dadurch sinkt der Differenzdruck Δp zwischen dem Eingang und dem Ausgang des mehrstufigen Verdichters auf einen Wert nahe Null. In dieser Situation bewegt sich das Zusatzventil erfindungsgemäß in die Öffnungsstellung zurück, so dass das Medium innerhalb der mit dem Zusatzventil ausgestatteten Verdichterstufe nicht komprimiert wird, d.h. dass sich die mit dem Zusatzventil ausgestattete, stromaufwärts vor der letzten Verdichterstufe angeordnete Verdichterstufe im Leerlauf befindet.When the pressure vessel to be filled has reached a predetermined internal pressure, the filling of the pressure vessel is stopped by opening the overflow valve so that the medium can escape. As a result, the differential pressure Δp between the input and the output of the multi-stage compressor drops to a value close to zero. In this situation, according to the invention, the additional valve moves back to the open position, so that the medium within the compressor stage equipped with the additional valve is not compressed, i. that equipped with the additional valve, upstream of the last compressor stage arranged compressor stage is idle.

In der Erfindung ist die Austassventilkammer der am weitesten stromabwärts angeordneten Verdichterstufe mit dem in der Einlassventilkammer mindestens einer stromaufwärts angeordneten Verdichterstufe vorgesehenen Zusatzventil durch eine Rohrleitung verbunden.In the invention, the discharge valve chamber of the compressor stage located furthest downstream is connected to the additional valve provided in the inlet valve chamber of at least one upstream compressor stage through a pipeline.

Vorteilhaft ist eine pneumatische Betätigung des oder der Zusatzventile durch das zu komprimierende Medium selbst. Hierzu wird die Auslassventilkammer der letzten Verdichterstufe mit dem in der Einlassventilkammer der stromaufwärts angeordneten Verdichterstufe oder Verdichterstufen angeordneten Zusatzventil verbunden. Diese Ausgestaltung hat den Vorteil, dass das Ventil ohne Zwischenschaltung aufwändiger Steuer- oder Regeleinrichtungen durch den Differenzdruck Δp betätigt wird. Hierdurch kann der erfindungsgemäße Verdichter kostengünstig hergestellt werden, ist selbstregelnd und wartungsfrei.Advantageously, a pneumatic actuation of the additional valves or by the medium to be compressed itself. For this purpose, the outlet valve chamber of the last compressor stage is connected to the arranged in the inlet valve chamber of the upstream compressor stage or compressor stages additional valve. This embodiment has the advantage that the valve is actuated by the differential pressure Δp without the interposition of complicated control or regulating devices. As a result, the compressor according to the invention can be produced inexpensively, is self-regulating and maintenance-free.

In einer weiteren Ausgestaltung der Erfindung ist die Auslassventilkammer der am weitesten stromabwärts angeordneten Verdichterstufe mit den in den Einlassventilkammern mehrerer stromaufwärts angeordneter Verdichterstufen angeordneten Zusatzventilen durch eine sich verzweigende Rohrleitung verbunden.In a further embodiment of the invention, the outlet valve chamber of the compressor stage located furthest downstream is connected to the additional valves arranged in the inlet valve chambers of a plurality of upstream compressor stages by a branching pipeline.

Sind mehr als zwei Verdichterstufen vorgesehen und mehrere der stromaufwärts angeordneten Verdichterstufen mit einem Zusatzventil ausgestattet, so muss jeder dieser Verdichterstufen der Druck, der am Ausgang des Verdichters anliegt, zugeführt werden, wenn die Betätigung des Zusatzventils auf diesem Wege erfolgen soll. Dies kann beispielsweise dadurch geschehen, dass von der letzten Verdichterstufe jeweils eine Rohrleitung zu einer der stromaufwärts angeordneten Verdichterstufen geführt wird. Die Verwendung einer einzigen, sich verzweigenden Rohrleitung hat demgegenüberden Vorteil, dass der mehrstufige Verdichter kostengünstiger herstellbar ist und an der letzten Verdichterstufe Bauraum eingespart wird, da nur eine Rohrleitung angeschlossen werden muss.If more than two compressor stages are provided and several of the upstream compressor stages equipped with an additional valve, so each of these compressor stages, the pressure applied to the output of the compressor, be supplied when the operation of the additional valve to take place in this way. This can be done, for example, by guiding a pipeline from the last compressor stage to one of the upstream compressor stages. The use of a single, branching pipeline has the advantage that the multi-stage compressor is less expensive to produce and at the last compressor stage space is saved, since only one pipe must be connected.

Gemäß einer weiteren Ausgestaltung der Erfindung ist eine Feder vorgesehen, die das Zusatzventil im Ruhezustand und bei einem Differenzdruck Δp, der unterhalb des vorgegebenen Wertes fiegt, in der Öffnungsstellung hält bzw. aus der Schließstellung in die Öffnungsstellung bewegt.According to a further embodiment of the invention, a spring is provided which holds the additional valve in the idle state and at a differential pressure Ap, which is below the predetermined value, in the open position or moves from the closed position to the open position.

Die Rückstellung des Zusatzventils in die Öffnungsstellung könnte wiederum magnetisch, elektrisch oder auf eine andere geeignete Weise erfolgen. Hierzu wären wiederum Stellglieder oder besondere konstruktive Gestaltungen des Zusatzventils erforderlich. Die Rückstellung des Zusatzventils durch eine Federist demgegenüber mechanisch einfacher zu realisieren und kostengünstiger herzustellen.The provision of the additional valve in the open position could again be done magnetically, electrically or in another suitable manner. For this purpose, in turn actuators or special structural designs of the additional valve would be required. The provision of the additional valve by a Federist contrast mechanically easier to implement and cheaper to produce.

Vorteilhaft ist die Feder eine Blattfeder mit einem als Gabel ausgeführten Ende, die in eine dafür vorgesehene Rille des Zusatzventils eingreift Eine weitere vorteilhafte Lösung ist die Verwendung einer Schraubenfeder, in die das Zusatzventil eingesetzt ist. Weitere konstruktive Ausgestaltungen unter Verwendung einer oder mehrerer Federn sind möglich, ohne vom Grundgedanken der Erfindung abzuweichen.Advantageously, the spring is a leaf spring with an end designed as a fork, which engages in a groove provided for this purpose of the additional valve. A further advantageous solution is the use of a helical spring into which the additional valve is inserted. Further constructive embodiments using one or more springs are possible without departing from the spirit of the invention.

In einer vorteilhaften Weiterbildung der Erfindung ist zwischen mindestens zwei Verdichterstufen ein Wärmetauscher zum Kühlen des kompressiblen Mediums vorgesehen.In an advantageous development of the invention, a heat exchanger for cooling the compressible medium is provided between at least two compressor stages.

Durch den Wärmeentzug zwischen zwei Verdichterstufen wird dem Effekt entgegengewirkt, dass das Medium, das sich durch die Kompression erwärmt, sich ausdehnt, so dass sich der Wirkungsgrad des Verdichters verschlechtert.The heat extraction between two compressor stages counteracts the effect that the medium, which heats up by the compression, expands, so that the efficiency of the compressor deteriorates.

Die selbsttätige Steuerung des zwischen den jeweifigen Zylinderräumen und ihren zugehörigen Einlassventilkammern angeordneten Zusatzventil, die nach einer beschriebenen Ausgestaltung der Erfindung durch den Gegendruck der Rohrleitung (Differenzdruck Δp) erfolgen kann, ermöglicht eine automatische Umschaltung der betreffenden Verdichterstufen zwischen Arbeitsbetrieb (Medium wird komprimiert) und Leerlauf (Medium wird nicht komprimiert). Dabei wird der Tatsache Rechnung getragen, dass zur Sicherstellung der Betätigung des oder der Zusatzventile die letzte Verdichterstufe selbst nicht über ein solches Zusatzventil im Leerlauf "undicht° gemacht werden darf.The automatic control of arranged between the jeweifigen cylinder chambers and their associated inlet valve chambers additional valve, which can be done according to a described embodiment of the invention by the back pressure of the pipe (differential pressure Ap), allows automatic switching of the respective compressor stages between working (medium is compressed) and idle (Medium is not compressed). In this case, the fact is taken into account that to ensure the actuation of the additional valves or the last compressor stage itself must not be made on such an additional valve idle "leaking °.

Beim Übergang vom Leerlauf zum Lastfall baut zunächst gerade die letzte Verdichterstufe, wenn auch mit geringerem Volumenstrom, den zur Betätigung des Zusatzventils benötigten Differenzdruck Δp auf. Dieser Differenzdruck Δp wirkt über eine Rohrleitung auf das Zusatzventil ein. Erreicht der Differenzdruck Δp einen vorgegebenen Wert, übersteigt die Druckkraft am Zusatzventil die zugehörige Federkraft der Feder, wodurch das Zusatzventil schließt und die unteren, d.h. stromaufwärts angeordneten Stufen zu arbeiten beginnen.During the transition from idling to load case, the last compressor stage initially builds, albeit with a smaller volume flow, the differential pressure Δp required to actuate the additional valve. This differential pressure Δp acts via a pipeline to the additional valve. If the differential pressure Δp reaches a predetermined value, the pressure force on the auxiliary valve exceeds the associated spring force of the spring, whereby the additional valve closes and the lower, i. upstream stages begin to work.

Dieses System hat gegenüber ähnlichen Systemen für einstufige Verdichter den Vorteil, direkt mit dem Druckniveau am Verdichtersaustritt zur Ansteuerung eines solchen Ventils auszukommen. Es werden keine zusätzlichen Signalgeber, Steuereinrichtungen oder ähnliches benötigt. Das System erkennt selbstständig, wann keine Luftförderung erforderlich ist. Es arbeitet sicher und ist störunanfällig. Das System ist einfach im Aufbau und daher kostengünstig herstellbar.This system has the advantage over similar systems for single-stage compressors, to get along directly with the pressure level at the compressor outlet for controlling such a valve. No additional signalers, control devices or the like are needed. The system automatically detects when no air delivery is required. It works safely and is immune to interference. The system is simple in construction and therefore inexpensive to produce.

Nachfolgend wird ein Ausführungsbeispiel der erfindungsgemäßen Lösung anhand von Figuren näher erläutert. Dabei zeigen

Fig. 1
den erfindungsgemäßen Verdichter im Arbeitsbetrieb und
Fig. 2
den erfindungsgemäßen Verdichter im Leerlauf.
An exemplary embodiment of the solution according to the invention will be explained in more detail below with reference to figures. Show
Fig. 1
the compressor according to the invention in the working mode and
Fig. 2
the compressor according to the invention in idle.

Der mehrstufige Kolbenverdichter zur Verdichtung kompressibler Medien gemäß Ausführungsbeispiel weist zwei Verdichterstufen 1,2 auf. Jede Verdichterstufe 1,2 besteht aus einem in einem Zylinderraum 11,21 geführten Kolben (nicht dargestellt) sowie je einer mit dem Zylinderraum 11,21 durch ein Einlassventil 12,22 verbundenen Einlassventilkammer 13,23 und einer mit dem Zylinderraum 11,21 durch ein Auslassventil 14,24 verbundenen Auslassventilkammer 15,25. Die gegenüber der letzten Verdichterstufe 2 stromaufwärts angeordnete Verdichterstufe 1 weist ein Zusatzventil 16 auf, durch das die Einlassventilkammer 13 mit dem Zylinderraum 11 verbunden ist.The multi-stage piston compressor for compressing compressible media according to the embodiment has two compressor stages 1,2. Each compressor stage 1, 2 consists of a piston (not shown) guided in a cylinder chamber 11,21 and an inlet valve chamber 13,23 connected to the cylinder chamber 11,21 through an inlet valve 12,22 and one with the cylinder chamber 11,21 Outlet valve 14,24 connected outlet valve chamber 15,25. The opposite The last compressor stage 2 upstream compressor stage 1 has an additional valve 16, through which the inlet valve chamber 13 is connected to the cylinder chamber 11.

Die Auslassventilkammer 25 der letzten und damit am weitesten stromabwärts angeordneten Verdichterstufe 2 ist mit dem in der Einlassventilkammer 13 der ersten, stromaufwärts angeordneten Verdichterstufe 1 angeordneten Zusatzventil 16 durch eine Rohrleitung 3 verbunden.The outlet valve chamber 25 of the last compressor stage 2, which is thus arranged furthest downstream, is connected to the additional valve 16 arranged in the inlet valve chamber 13 of the first compressor stage 1, which is arranged upstream, through a pipeline 3.

In der Einlassventilkammer 13 der ersten, stromaufwärts angeordneten Verdichterstufe 1 ist eine Feder 18 vorgesehen, die das Zusatzventil 16 im Ruhezustand und bei einem Differenzdruck Δp zwischen dem Einlass und dem Auslass des mehrstufigen Verdichters, der unterhalb eines vorgegebenen Wertes liegt, in der Öffnungsstellung hält bzw. aus der Schließstellung in die Öffnungsstellung bewegt. Der vorgegebene Wert des Differenzdrucks ist bei diesem Ausführungsbeispiel proportional zur Federrate der Feder 18.In the inlet valve chamber 13 of the first, upstream compressor stage 1, a spring 18 is provided which keeps the auxiliary valve 16 in the open position and at a differential pressure Δp between the inlet and the outlet of the multi-stage compressor, which is below a predetermined value in the open position or . Moved from the closed position to the open position. The predetermined value of the differential pressure is proportional to the spring rate of the spring 18 in this embodiment.

Die Feder 18 ist eine Blattfeder mit einem als Gabel ausgeführten Ende. Das gabelförmige Ende der Blattfeder 18 greift in eine dafür vorgesehene Rille 17 des Zusatzventils 16 ein.The spring 18 is a leaf spring with an end running as a fork. The forked end of the leaf spring 18 engages in a designated groove 17 of the additional valve 16 a.

Zwischen den beiden Verdichterstufen 1,2 ist ein Wärmetauscher 4 zum Kühlen des kompressiblen Mediums vorgesehen.Between the two compressor stages 1,2, a heat exchanger 4 is provided for cooling the compressible medium.

Das Zusatzventil 16 ist in Fig. 1 in der Schließstellung dargestellt. Der zu befüllende Behälter (nicht dargestellt) hat nicht den gewünschten Innendruck. Daher ist das Überströmventil (nicht dargestellt) geschlossen und der mehrstufige Verdichter arbeitet gegen den Innendruck des geschlossenen Systems. Der Differenzdruck Δp zwischen der Auslassventilkammer25 der am weitesten stromabwärts angeordneten Verdichterstufe 2 und der Einlassventilkammer 13 der stromaufwärts angeordneten Verdichterstufe 1 hat den vorgegebenen Wert überschritten. Dieser Differenzdruck liegt durch die Rohrleitung 3 am Zusatzventil 16 an und reicht aus, um das Zusatzventil 16 gegen die Kraft der Feder 18 in die Schließstellung zu bewegen. Dadurch ist keine ständige Verbindung zwischen der Einlassventilkammer 13 und dem Zylinderraum 11 der ersten Verdichterstufe 1 gegeben und das Medium wird in der ersten Verdichterstufe 1 komprimiert.The additional valve 16 is in Fig. 1 shown in the closed position. The container to be filled (not shown) does not have the desired internal pressure. Therefore, the spill valve (not shown) is closed and the multi-stage compressor operates against the internal pressure of the closed system. The differential pressure Δp between the discharge valve chamber 25 of the compressor stage 2 located furthest downstream and the inlet valve chamber 13 of the upstream compressor stage 1 has exceeded the predetermined value. This differential pressure is applied through the pipe 3 to the additional valve 16 and is sufficient to move the additional valve 16 against the force of the spring 18 in the closed position. As a result, there is no permanent connection between the inlet valve chamber 13 and the cylinder chamber 11 of the first compressor stage 1 and the medium is compressed in the first compressor stage 1.

In Fig. 2 ist das Zusatzventil 16 in der Öffnungsstellung dargestellt. Der zu befüllende Behälter (nicht dargestellt) hat den gewünschten Innendruck erreicht. Daher ist das Überströmventil (nicht dargestellt) geöffnet und der mehrstufige Verdichter arbeitet nicht gegen den Innendruck des geschlossenen Systems. Der Differenzdruck Δp zwischen der Auslassventilkammer 25 der am weitesten stromabwärts angeordneten Verdichterstufe 2 und der Einlassventilkammer 13 der stromaufwärts angeordneten Verdichterstufe 1 ist annähernd Null, d.h. der Differenzdruck Δp hat den vorgegebenen Wert unterschritten. Die Kraft der Feder 18 bewegt das Zusatzventil 16 zurück in die Öffnungsstellung. Dadurch besteht nun eine ständige Verbindung zwischen der Einlassventilkammer 13 und dem Zylinderraum 11 der ersten Verdichterstufe 1, so dass das Medium in der ersten Verdichterstufe 1 nicht komprimiert wird, d.h. die erste Verdichterstufe 1 befindet sich im Leerlauf.In Fig. 2 the auxiliary valve 16 is shown in the open position. The container to be filled (not shown) has reached the desired internal pressure. Therefore, the spill valve (not shown) is opened and the multi-stage compressor does not work against the internal pressure of the closed system. The differential pressure Δp between the exhaust valve chamber 25 of the compressor stage 2 located farthest downstream and the inlet valve chamber 13 of the upstream compressor stage 1 is approximately zero, that is, the differential pressure Δp has fallen below the predetermined value. The force of the spring 18 moves the additional valve 16 back into the open position. As a result, there is now a permanent connection between the inlet valve chamber 13 and the cylinder chamber 11 of the first compressor stage 1, so that the medium in the first compressor stage 1 is not compressed, ie the first compressor stage 1 is idling.

Claims (5)

  1. Multi-stage piston type compressor for compressing compressible media, with at least one compressor stage arranged upstream and at least one arranged downstream (1, 2), wherein each compressor stage (1,2) has at least one piston guided in a cylinder chamber (11, 21), as well as in each case an inlet valve chamber (13, 23) connected to the cylinder chamber (11, 21) by means of an inlet valve (12, 22) and an outlet valve chamber (15, 25) connected to the cylinder chamber (11, 21) by means of an outlet valve (14, 24) characterised in that, with at least one compressor stage (1) arranged upstream, the inlet valve chamber (13) is connected by means of at least one additional valve (16) to the cylinder chamber (11), which in the state of rest is located in an open position and which moves into a closed position when the differential pressure Δp between the outlet valve chamber (25) of the compressor stage (2) located furthest downstream and the inlet valve chamber (13) of the compressor stage (1) arranged upstream exceeds a predetermined value, and that the outlet valve chamber (25) of the compressor stage (2) arranged furthest downstream is connected to the additional valve (16) arranged in the inlet valve chamber (13) of at least one compressor stage (1) arranged upstream by means of a pipe (3).
  2. Multi-stage piston type compressor according to Claim 1,
    characterised in that the outlet valve chamber (25) of the compressor stage (2) arranged furthest downstream is connected to the additional valves (16 arranged in the inlet valve chambers (13) of a plurality of compressor stages (1) arranged upstream by means of a branched pipe (3).
  3. Multi-stage piston type compressor according to one of Claims 1 or 2,
    characterised in that a spring (18) is provided, which holds the additional valve (16) in the state of rest and under a differential pressure Δp, which is below the specified value, holds it in the open position or moves it out of the closed position into the open position.
  4. Multi-stage piston type compressor according to Claim 3,
    characterised in that the spring (18) is a leaf spring with an end designed as a fork, which engages in a groove (17) of the additional valve (16) provided for this purpose.
  5. Multi-stage piston type compressor according to any one of Claims 1 to 4,
    characterised in that a heat exchanger (4) for cooling the compressible medium is provided between at least two compressor stages (1, 2).
EP05022666.1A 2004-10-19 2005-10-18 Multi-stage piston type compressor with reduced power input during idle running Active EP1650434B2 (en)

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Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007006641A1 (en) 2007-02-06 2008-08-07 Voith Patent Gmbh Crank gear for two-stage piston compressor i.e. brake air compressor, has bolt bearing i.e. antifriction bearing, for supporting piston pin, pin bearing i.e. friction bearing, on crank shaft, and connection for making admission of oil mist
DE102007037687B3 (en) * 2007-08-09 2008-09-25 Voith Patent Gmbh Lenkhelfpumpenantrieb
DE102009053133A1 (en) * 2009-11-05 2011-05-12 Voith Patent Gmbh Piston compressor with idling valve
DE102011050714A1 (en) * 2011-05-30 2012-12-06 Continental Reifen Deutschland Gmbh compressor unit
DE102012108576A1 (en) 2012-09-13 2014-03-13 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Multi-stage reciprocating compressor with idling valves for generating an idling function
DE102013001147A1 (en) 2013-01-24 2014-07-24 Voith Patent Gmbh Multi-stage piston compressor
DE102014202265A1 (en) 2014-02-07 2015-08-13 Voith Patent Gmbh Compressor for a compressed air system, in particular of a motor vehicle
DE102019119944A1 (en) 2019-07-24 2021-01-28 Voith Patent Gmbh Valve device for a reciprocating compressor
DE102021104789A1 (en) 2021-03-01 2022-09-01 Voith Patent Gmbh air compressor unit

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE366401C (en) † 1921-09-02 1923-01-04 Josef Heinrici Glasses with length adjustable wire brackets
DE374317C (en) † 1922-04-01 1923-04-21 Ehrhardt & Sehmer Akt Ges Device to protect against excessive pressure in the individual stages of multi-stage compressors
DE405798C (en) † 1924-11-08 Hugo Heinrich Multi-stage compressor with stages that can be switched one behind the other or in parallel
DE681654C (en) † 1938-08-26 1939-09-28 Knorr Bremse Akt Ges Idle control device for with negative pressure as a closing force for the automatic suction valve working piston compressor
DE857259C (en) † 1940-02-13 1952-11-27 Hoerbiger & Co Multi-stage piston compressor with infinitely variable delivery rate control through synchronously switched on additional rooms in the individual compressor stages
AT187616B (en) † 1955-04-19 1956-11-10 Hoerbiger & Co Stepless delivery rate control for piston compressors
DE954000C (en) † 1948-12-16 1956-12-13 Hoerbiger & Co Control of multi-stage reciprocating compressors
DE1403953A1 (en) † 1962-07-06 1968-11-21 Atlas Copco Ab Reciprocating compressors
DE1775366A1 (en) † 1967-08-03 1971-07-08 Svenska Tempus Ab Valve
DE1628165A1 (en) † 1966-11-24 1972-01-13 Hoerbiger Ventilwerke Ag Method and device for controlling a compressor system
DE2449233A1 (en) † 1973-11-05 1975-05-07 Luft U Kaeltetechnik Veb K DEVICE FOR REGULATING THE CRANKCASE PRESSURE IN A MULTICYLINDER RECIPIENT COMPRESSOR
DE2901513A1 (en) † 1979-01-16 1980-07-24 Knorr Bremse Gmbh Compressor output pressure control - has spring loaded piston valve connecting outlet chamber to inlet at given pressure level
DE3032002C2 (en) † 1980-08-25 1986-01-16 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen Device for regulating the flow rate of a single or multi-stage compressor arrangement, in particular for screw compressors
EP0091994B1 (en) † 1982-04-21 1987-03-04 WABCO Vermögensverwaltungs-GmbH Apparatus for generating gas under pressure
DE4105593A1 (en) † 1990-03-16 1991-09-19 Hoerbiger Ventilwerke Ag METHOD FOR CONTINUOUSLY REGULATING THE FLOW RATE OF PISTON COMPRESSORS AND DEVICE FOR CARRYING OUT THE METHOD

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2028412A1 (en) * 1969-01-16 1970-10-09 Iwata Air Compressor Mfg
DE3329790C2 (en) * 1983-08-18 1995-11-30 Wabco Gmbh Valve carrier for piston compressors
DE3446096A1 (en) * 1984-12-18 1986-06-19 Wabco Westinghouse Fahrzeugbremsen GmbH, 3000 Hannover SEAT VALVE DEVICE
DE4026684A1 (en) * 1990-08-23 1992-02-27 Knorr Bremse Ag Power economy device for piston compressor - involves suction valve with control pressure switchable between work and no-load positions

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE405798C (en) † 1924-11-08 Hugo Heinrich Multi-stage compressor with stages that can be switched one behind the other or in parallel
DE366401C (en) † 1921-09-02 1923-01-04 Josef Heinrici Glasses with length adjustable wire brackets
DE374317C (en) † 1922-04-01 1923-04-21 Ehrhardt & Sehmer Akt Ges Device to protect against excessive pressure in the individual stages of multi-stage compressors
DE681654C (en) † 1938-08-26 1939-09-28 Knorr Bremse Akt Ges Idle control device for with negative pressure as a closing force for the automatic suction valve working piston compressor
DE857259C (en) † 1940-02-13 1952-11-27 Hoerbiger & Co Multi-stage piston compressor with infinitely variable delivery rate control through synchronously switched on additional rooms in the individual compressor stages
DE954000C (en) † 1948-12-16 1956-12-13 Hoerbiger & Co Control of multi-stage reciprocating compressors
AT187616B (en) † 1955-04-19 1956-11-10 Hoerbiger & Co Stepless delivery rate control for piston compressors
DE1403953A1 (en) † 1962-07-06 1968-11-21 Atlas Copco Ab Reciprocating compressors
DE1628165A1 (en) † 1966-11-24 1972-01-13 Hoerbiger Ventilwerke Ag Method and device for controlling a compressor system
DE1775366A1 (en) † 1967-08-03 1971-07-08 Svenska Tempus Ab Valve
DE2449233A1 (en) † 1973-11-05 1975-05-07 Luft U Kaeltetechnik Veb K DEVICE FOR REGULATING THE CRANKCASE PRESSURE IN A MULTICYLINDER RECIPIENT COMPRESSOR
DE2901513A1 (en) † 1979-01-16 1980-07-24 Knorr Bremse Gmbh Compressor output pressure control - has spring loaded piston valve connecting outlet chamber to inlet at given pressure level
DE3032002C2 (en) † 1980-08-25 1986-01-16 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen Device for regulating the flow rate of a single or multi-stage compressor arrangement, in particular for screw compressors
EP0091994B1 (en) † 1982-04-21 1987-03-04 WABCO Vermögensverwaltungs-GmbH Apparatus for generating gas under pressure
DE4105593A1 (en) † 1990-03-16 1991-09-19 Hoerbiger Ventilwerke Ag METHOD FOR CONTINUOUSLY REGULATING THE FLOW RATE OF PISTON COMPRESSORS AND DEVICE FOR CARRYING OUT THE METHOD

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ATE384871T1 (en) 2008-02-15
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EP1650434B1 (en) 2008-01-23
DE502005002636D1 (en) 2008-03-13

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