EP1395755B1 - Multi-stage piston-type compressor - Google Patents

Multi-stage piston-type compressor Download PDF

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Publication number
EP1395755B1
EP1395755B1 EP02745080A EP02745080A EP1395755B1 EP 1395755 B1 EP1395755 B1 EP 1395755B1 EP 02745080 A EP02745080 A EP 02745080A EP 02745080 A EP02745080 A EP 02745080A EP 1395755 B1 EP1395755 B1 EP 1395755B1
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EP
European Patent Office
Prior art keywords
valve
closing diaphragm
pressure chamber
overflow
return valve
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
EP02745080A
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German (de)
French (fr)
Other versions
EP1395755A1 (en
Inventor
Iwan Antufjew
Marko SCHRÖDTER
Stefan Beetz
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Continental AG
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Continental AG
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Publication of EP1395755A1 publication Critical patent/EP1395755A1/en
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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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • F04B39/108—Adaptations or arrangements of distribution members the members being reed valves circular reed 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
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/02—Multi-stage pumps of stepped piston type
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
    • 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
    • F04B39/0005—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 adaptations of pistons
    • F04B39/0016—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 adaptations of pistons with valve arranged in the piston
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/102—Adaptations or arrangements of distribution members the members being disc valves
    • F04B39/1026—Adaptations or arrangements of distribution members the members being disc valves without spring
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • F04B39/1086—Adaptations or arrangements of distribution members the members being reed valves flat annular reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber

Definitions

  • the invention relates to a reciprocating compressor according to the preamble of claim 1.
  • Such reciprocating compressors are used in all technical areas where there is a need for compressed air.
  • piston compressors are used in the automotive industry for air suspension and / or air damping.
  • Such a piston compressor in a two-stage design is described for example in DE 197 15 291 A1.
  • This reciprocating compressor consists of a compressor housing, in which a cylindrical low pressure chamber with a larger Niederdmckkolben and a cylindrical high pressure chamber are formed with a smaller high pressure piston.
  • the low-pressure chamber and the high-pressure chamber are located on a common axis and the low-pressure piston and the high-pressure piston are formed into a one-piece pressure piston with a common piston rod.
  • the low-pressure chamber has an inlet with an inlet check valve
  • the high-pressure chamber has an outlet with an outlet check valve
  • both pressure chambers are connected by an overflow channel in which an overflow check valve is arranged.
  • a crank pin of a crankshaft which is driven for example by an electric motor and their rotating movement in a linear movement on the one-piece pressure piston converts. This linear movement results in an oscillating movement on the pressure piston.
  • the inlet check valve, the outlet check valve, and the spill check valve have spring steel gaskets which, as in the case of the inlet check and overflow check valves, are fastened by a central screw and which sealingly cover a plurality of flow channels arranged on a pitch circle or, as in the case of Outlet check valve is held by a laterally offset screw and seal an adjacent flow channel.
  • the metallic sealing washers do not adequately seal. This is due to the fact that the closing force of the sealing washers is applied exclusively by the residual stresses of the spring steel. This closing force often counteracts even a clamping force, which starts from the fastening screw and prevents the pressure-balanced state, a smooth support of the gasket. Leaks also occur due to the fact that, over time, fatigue phenomena occur on the sealing disk and that the sealing disks do not fit perfectly against the sealing surface for this reason. To compensate for these adverse effects, the sealing discs are usually made stronger. However, this in turn increases the installation space of such a sealing disc and reduces the volume of the corresponding pressure chamber. Such reciprocating compressors are then not very powerful.
  • the invention is therefore based on the object to develop a generic reciprocating compressor whose check valves have a very low closing force and at the same time ensure a high density.
  • valve housing 4 with a cylindrical, stepped in diameter interior, which is in a low-pressure chamber 5 with a larger diameter and divides into a high-pressure chamber 6 with a smaller diameter.
  • the low pressure chamber 5 is closed with a valve housing bottom 7 and the high pressure chamber 6 with a valve housing cover 8 sealingly outwards.
  • the valve housing cover 8 is connected to the housing of the air dryer unit 3 or made in one piece.
  • a one-piece compressor piston 9 is fitted, which accordingly consists of a low-pressure piston 10 with a larger diameter, a high-pressure piston 11 with a smaller diameter and a common piston rod 12.
  • a crankcase is formed, in which engages in a rectangular orientation, the connecting rod 13 of the crankshaft 14 of the drive motor 2.
  • the low pressure chamber 5 and the high pressure chamber 6 have connections to each other and to the outside.
  • an inlet check valve 15 which connects the low-pressure chamber 5 with the atmosphere.
  • This inlet check valve 15 includes a plurality of arranged on a common circular path inlet openings 16 and a, all inlet openings 16 covering, first sealing membrane 17.
  • the closure membrane 17 is fitted in an inner counterbore, which has a crowned or angled bottom hole.
  • a centrally attached and mushroom-like fastening element 18 fixes the closure membrane 17 and holds the closure membrane 17 under a slight tension on the bottom of the counterbore.
  • this introduced by the fastening element 18 voltage is selected so that the first sealing membrane 17 is rotatable in its position and does not lift off from the inlet openings 16 in the pressure-balanced state.
  • the sealing membrane 17 and the fastening element 18 are flush in the counterbore so that no volume of the low-pressure chamber 5 is lost.
  • a continuous overflow channel 19 which connects the low-pressure chamber 5 and the high-pressure chamber 6 to one another, is furthermore located in the compressor piston 9.
  • an overflow check valve 20 is arranged in the high-pressure-side opening region of this overflow channel 19, which functionally connects or disconnects the low-pressure chamber 5 and the high-pressure chamber 6.
  • the mouth of the overflow channel 19 is expanded to a kidney-shaped in cross-section chamber 21, wherein the kidney shape follows a circular path.
  • the overflow check valve 20 consists of a cup sleeve 22 made of plastic, which rests with its bottom on the end face of the high-pressure piston 11 and sealingly abuts against the inner wall of the high-pressure chamber 6.
  • overflow check valve 20 further includes a specially designed valve holder 23 which is fittingly inserted into the interior of the cup 22 and the sleeve is shown in more detail in FIG.
  • This valve holder 23 therefore has an outer shape, which is aligned with the interior of the cup 22.
  • a cylindrical recess 24 is introduced, the axis of which is arranged at a certain amount of eccentricity away from the axis of the high-pressure piston 11. This amount of eccentricity as well as the size and the radial position of the cylindrical recess 24 ensure that the cylindrical recess 24 is in register with the kidney-shaped chamber 21 of the overflow channel 19.
  • the valve holder 23 is equipped outside the cylindrical recess 24 with distributed arranged fastening elements 25 for position-determining anchoring with the high pressure piston 11.
  • a first through hole 26 having a smaller diameter
  • a second through hole 27 having a larger diameter, which have an equal or different distance from the axis of the cylindrical recess 24 and in their position and in their extension are designed so that they are in register with the kidney-shaped chamber 21 of the overflow 19.
  • a freely resting second closure membrane 28 is fitted with such a game that it is freely movable in the direction of rotation and in the axial direction and the annular space between the second closure membrane 28 and the inner wall of the cylindrical recess 24 is suitable as an air passage.
  • the cylindrical recess 24 is further covered with a stop grid 29, on the one hand limits the axial stroke of the second closure membrane 28 and on the other hand grants the released compressed air flow a largely free passage.
  • the structure of the lattice struts is chosen freely, wherein the openings in the stop grid 29 are made so small that the second sealing membrane 28 can not jam.
  • the breakthroughs can also be different sizes.
  • the high-pressure chamber 6 has an outlet check valve 30 for connecting the high-pressure chamber 6 to a consumer line.
  • This outlet check valve 30 is arranged according to the Fig. 3 between the valve housing 4 and the valve housing cover 8 and consists of a circumferentially clamped valve plate 31 and a third sealing membrane 32.
  • the valve plate 31 is sealed against the valve housing 4 and against the valve housing cover 8 and has
  • the third sealing membrane 32 is designed as a ring and thus has a central flow bore 34. With its periphery, the third sealing membrane 32 between the valve plate 31 and the valve housing cover 8 is held while the flow bore 34 with its Diameter is sufficiently smaller than the pitch circle diameter of the diameter of the outlet openings is designed so that the outlet openings 33 are completely covered by the third sealing membrane 32.
  • the third sealing membrane 32 is installed without constructive bias, so that the closing force results only from the material-specific residual stress.
  • the first sealing membrane 17 of the inlet check valve 15, the second sealing membrane 28 of the overflow check valve 28 and the third sealing membrane 32 of the outlet check valve 30 are made of plastic, in particular of an elastic polymer, which has a high dielectric strength, high temperature resistance and elastic properties with memory Effect.
  • both the low-pressure piston 10 and the high-pressure piston 11 move between two opposing reversal points and thus form two alternately changing low-pressure chamber 5 and high-pressure chamber 6.
  • a negative pressure arises, which raises the first closing membrane 17 on its outer circumference and allows outside air to flow through the inlet openings 16.
  • This opening pressure results from the sum of the material tension of the closure membrane 17 and the installation-related bias on the closure membrane 17.
  • the negative pressure closes the second closure membrane 28 of the overflow check valve 20.
  • the low pressure chamber 5 With the reverse movement of the valve piston 9, the low pressure chamber 5 is reduced, so that the air clamped there is conveyed under pressure through the overflow 19 to the high pressure chamber 6.
  • the air first flows into the kidney-shaped chamber 21 of the overflow channel 19 and loads from there the second sealing membrane 28 in the area and in the circumference of the first through-bore 26 and the second through-bore 27.
  • a first opening force and the second Through hole 27 a second opening force on the second sealing membrane 28, both of which act in parallel.
  • the exposed second closure membrane 28 is in a lopsided position and by radial force components in a radial rotational movement, which is directed from the smaller flow bore 26 to the larger flow bore 27 and the the position of the second closure membrane 28 to the two through holes 26, 27 changed steadily.
  • Such an overload quickly leads to strike through and failure of the overflow check valve 20.
  • the exposed second closure membrane 28 opposes the flow of compressed air flow only a slightest resistance.

Abstract

In order to achieve a high level of impermeability with a low closing force for the sealing elements of a multistage piston compressor, the overflow channel ( 19 ) in the valve piston ( 9 ) opens into at least two passages ( 26, 27 ) and the sealing plate of the overflow check valve ( 20 ) that is located in the valve piston ( 9 ) is configured as a freely guided closing membrane ( 28 ) with a limited stroke. The passages ( 26, 27 ) of the overflow channel ( 19 ) have different diameters, are arranged on a graduated circle at a radial distance from the axis of the closing membrane ( 28 ) and are completely covered by the closing membrane ( 28 ).

Description

Die Erfindung bezieht sich auf einen Kolbenverdichter nach dem Oberbegriff des Anspruchs 1.
Derartige Kolbenverdichter werden in allen technischen Bereichen eingesetzt, wo ein Bedarf an Druckluft besteht. In erster Linie kommen solche Kolbenverdichter in der Fahrzeugindustrie für die Luftfederung und/oder Luftdämpfung zur Anwendung.The invention relates to a reciprocating compressor according to the preamble of claim 1.
Such reciprocating compressors are used in all technical areas where there is a need for compressed air. First and foremost, such piston compressors are used in the automotive industry for air suspension and / or air damping.

Ein solcher, Kolbenverdichter in einer zweigestuften Ausführung ist beispielsweise in der DE 197 15 291 A1 beschrieben. Dieser Kolbenverdichter besteht aus einem Verdichtergehäuse, in dem eine zylindrische Niederdruckkammer mit einem größeren Niederdmckkolben und eine zylindrische Hochdruckkammer mit einem kleineren Hochdruckkolben ausgebildet sind. Dabei befinden sich die Niederdruckkammer und die Hochdruckkammer auf einer gemeinsamen Achse und der Niederdruckkolben und der Hochdruckkolben sind zu einem einstückigen Druckkolben mit einer gemeinsamen Kolbenstange ausgeformt. Die Niederdruckkammer besitzt einen Einlass mit einem Einlassrückschlagventil, die Hochdruckkammer besitzt einen Auslass mit einem Auslassrückschlagventil und beide Druckkammern sind durch einen Überströmkanal verbunden, in dem ein Überströmrückschlagventil angeordnet ist. In die gemeinsame Kolbenstange des Niederdruckkolbens und des Hochdruckkolbens greift in rechtwinkliger Ausrichtung ein Kurbelzapfen einer Kurbelwelle ein, die beispielsweise von einem Elektromotor angetrieben wird und die ihre rotierende Bewegung in eine lineare Bewegung am einteiligen Druckkolben umwandelt. Aus dieser linearen Bewegung ergibt sich am Druckkolben eine oszillierende Bewegung.
Das Einlassrückschlagventil, das Auslassrückschlagventil und das Überströmrückschlagventil besitzen Dichtscheiben aus Federstahl, die, wie im Falle des Einlassrückscklagventiles und des Überströmrückschlagventiles, durch eine mittige Schraube befestigt sind und die in dichtender Weise mehrere auf einem Teilkreis angeordnete Strömungskanäle überdecken, oder die, wie im Fall des Auslassrückschlagventiles, durch eine seitlich versetzte Schraube gehalten wird und die einen daneben liegenden Strömungskanal abdichten.
Diese Rückschlagventile erfüllen ihre Aufgabe nur unzureichend. So ist festzustellen, dass die metallischen Dichtscheiben nicht ausreichend abdichten. Das ist darauf zurückzuführen, dass die Schließkraft der Dichtscheiben ausschließlich durch die Eigenspannungen des Federstahles aufgebracht wird. Dieser Schließkraft wirkt oftmals noch eine Spannkraft entgegen, die von der Befestigungsschraube ausgeht und die im druckausgeglichenen Zustand eine glatte Auflage der Dichtscheibe verhindert. Undichtigkeiten treten auch dadurch auf, dass mit der Zeit Ermüdungserscheinungen an der Dichtscheibe auftreten und dass die Dichtscheiben aus diesem Grund nicht einwandfrei an der Dichtfläche anliegen. Zum Ausgleich dieser nachteiligen Wirkungen werden die Dichtscheiben in der Regel stärker ausgeführt. Das erhöht aber wiederum den Einbauraum einer solchen Dichtscheibe und verringert das Volumen der entsprechenden Druckkammer. Solche Kolbenverdichter sind dann nicht sehr leistungsfähig. Die durch die Verstärkung der Dichtscheibe erzielte höhere Schließkraft erhöht aber gleichzeitig die erforderliche Öffnungskraft für den freien Durchfluss, die vom Systemdruck aufgebracht werden muss. Auch das verringert den Wirkungsgrad des Kolbenverdichters erheblich.
Es hat sich auch gezeigt, dass das Material der Dichtscheiben wegen der hohen Frequenzen des Kolbenverdichters recht schnell ermüdet und daher nur eine geringe Lebensdauer der Dichtscheiben zu verzeichnen ist.Such a piston compressor in a two-stage design is described for example in DE 197 15 291 A1. This reciprocating compressor consists of a compressor housing, in which a cylindrical low pressure chamber with a larger Niederdmckkolben and a cylindrical high pressure chamber are formed with a smaller high pressure piston. In this case, the low-pressure chamber and the high-pressure chamber are located on a common axis and the low-pressure piston and the high-pressure piston are formed into a one-piece pressure piston with a common piston rod. The low-pressure chamber has an inlet with an inlet check valve, the high-pressure chamber has an outlet with an outlet check valve, and both pressure chambers are connected by an overflow channel in which an overflow check valve is arranged. In the common piston rod of the low-pressure piston and the high-pressure piston engages in a rectangular orientation, a crank pin of a crankshaft, which is driven for example by an electric motor and their rotating movement in a linear movement on the one-piece pressure piston converts. This linear movement results in an oscillating movement on the pressure piston.
The inlet check valve, the outlet check valve, and the spill check valve have spring steel gaskets which, as in the case of the inlet check and overflow check valves, are fastened by a central screw and which sealingly cover a plurality of flow channels arranged on a pitch circle or, as in the case of Outlet check valve is held by a laterally offset screw and seal an adjacent flow channel.
These check valves do not perform their task adequately. Thus, it should be noted that the metallic sealing washers do not adequately seal. This is due to the fact that the closing force of the sealing washers is applied exclusively by the residual stresses of the spring steel. This closing force often counteracts even a clamping force, which starts from the fastening screw and prevents the pressure-balanced state, a smooth support of the gasket. Leaks also occur due to the fact that, over time, fatigue phenomena occur on the sealing disk and that the sealing disks do not fit perfectly against the sealing surface for this reason. To compensate for these adverse effects, the sealing discs are usually made stronger. However, this in turn increases the installation space of such a sealing disc and reduces the volume of the corresponding pressure chamber. Such reciprocating compressors are then not very powerful. However, the higher closing force achieved by the reinforcement of the sealing disc also increases the required opening force for the free flow, which must be applied by the system pressure. This also reduces the efficiency of the reciprocating compressor considerably.
It has also been shown that the material of the sealing discs fatigues quite quickly because of the high frequencies of the reciprocating compressor and therefore only a short service life of the sealing discs is recorded.

Letztlich ist auch die Herstellung der Dichtscheiben aus Federstahl sehr aufwendig, da einerseits das Material schwer zu bearbeiten ist und andererseits hohe Anforderungen an die Qualität der Dichtfläche an der Dichtscheibe gestellt werden.Ultimately, the production of sealing washers made of spring steel is very expensive, since on the one hand, the material is difficult to work and on the other hand, high demands are placed on the quality of the sealing surface on the gasket.

Der Erfindung liegt daher die Aufgabe zu Grunde, einen gattungsgemäßen Kolbenverdichter zu entwickeln, dessen Rückschlagventile eine sehr geringe Schließkraft aufweisen und gleichzeitig eine hohe Dichtigkeit gewährleisten.The invention is therefore based on the object to develop a generic reciprocating compressor whose check valves have a very low closing force and at the same time ensure a high density.

Diese Aufgabe wird durch die kennzeichnenden Merkmale des Anspruches 1 gelöst. Weitere Ausgestaltungsmöglichkeiten ergeben sich aus den Unteransprüchen 2 bis 7. Der neue Kolbenverdichter beseitigt die genannten Nachteile des Standes der Technik.This object is solved by the characterizing features of claim 1. Further refinements result from the dependent claims 2 to 7. The new piston compressor eliminates the disadvantages of the prior art.

Die Erfindung soll anhand eines Ausführungsbeispieles näher erläutert werden.
Dazu zeigen:

Fig. 1:
einen zweistufigen Kolbenverdichter in einer schematischen Schnittdarstellung,
Fig. 2:
eine Einzelheit des Kolbenverdichters mit der Darstellung des Einlassrückschlagventiles,
Fig. 3:
eine Einzelheit des Kolbenverdichters mit der Darstellung des Überströmrückschlagventiles und des Auslassrückschlagventiles und
Fig. 4:
eine Draufsicht zum Überströmrückschlagventil gehörenden Ventileinsatzes.
The invention will be explained in more detail with reference to an embodiment.
To show:
Fig. 1:
a two-stage reciprocating compressor in a schematic sectional view,
Fig. 2:
a detail of the reciprocating compressor with the representation of the inlet check valve,
3:
a detail of the reciprocating compressor with the representation of the overflow check valve and the outlet check valve and
4:
a plan view of Überströmrückschlagventil belonging valve core.

Nach der Fig. 1 besteht ein zweistufiger Kolbenverdichter in seinen Hauptbestandteilen aus dem eigentlichen Kolbenverdichter 1, einem Antriebsmotor 2 und einer Lufttrocknereinheit 3.
Zum Kolbenverdichter 1 gehört ein Ventilgehäuse 4 mit einem zylindrischen, im Durchmesser gestuften Innenraum, der sich in eine Niederdruckkammer 5 mit einem größeren Durchmesser und in eine Hochdruckkammer 6 mit einem kleineren Durchmesser aufteilt. Die Niederdruckkammer 5 ist mit einem Ventilgehäuseboden 7 und die Hochdruckkammer 6 mit einem Ventilgehäusedeckel 8 dichtend nach außen verschlossen. Dabei ist der Ventilgehäusedeckel 8 mit dem Gehäuse der Lufttrocknereinheit 3 verbunden oder einstückig ausgeführt. In den Innenraum des Ventilgehäuses 4 ist ein einstückiger Verdichterkolben 9 eingepasst, der dementsprechend aus einem Niederdruckkolben 10 mit einem größeren Durchmesser, einem Hochdruckkolben 11 mit einem kleineren Durchmesser und einer gemeinsamen Kolbenstange 12 besteht. Im äußeren Bereich der Kolbenstange 12 ist ein Kurbelgehäuse ausgebildet, in das in rechtwinkliger Ausrichtung das Pleuel 13 der Kurbelwelle 14 des Antriebsmotors 2 eingreift.1, a two-stage reciprocating compressor in its main components from the actual reciprocating compressor 1, a drive motor 2 and an air dryer unit. 3
For piston compressor 1 includes a valve housing 4 with a cylindrical, stepped in diameter interior, which is in a low-pressure chamber 5 with a larger diameter and divides into a high-pressure chamber 6 with a smaller diameter. The low pressure chamber 5 is closed with a valve housing bottom 7 and the high pressure chamber 6 with a valve housing cover 8 sealingly outwards. In this case, the valve housing cover 8 is connected to the housing of the air dryer unit 3 or made in one piece. In the interior of the valve housing 4, a one-piece compressor piston 9 is fitted, which accordingly consists of a low-pressure piston 10 with a larger diameter, a high-pressure piston 11 with a smaller diameter and a common piston rod 12. In the outer region of the piston rod 12, a crankcase is formed, in which engages in a rectangular orientation, the connecting rod 13 of the crankshaft 14 of the drive motor 2.

Die Niederdruckkammer 5 und die Hochdruckkammer 6 besitzen Verbindungen untereinander und nach außen.The low pressure chamber 5 and the high pressure chamber 6 have connections to each other and to the outside.

So befindet sich gemäß der Fig. 2 im Ventilgehäuseboden 7 des Kolbenverdichters 1 ein Einlassrückschlagventil 15, das die Niederdruckkammer 5 mit der Atmosphäre verbindet. Zu diesem Einlassrückschlagventil 15 gehören mehrere, auf einer gemeinsamen Kreisbahn angeordnete Einlassöffnungen 16 und eine, alle Einlassöffnungen 16 abdeckende, erste Verschlussmembran 17. Dabei ist die Verschlussmembran 17 in eine innenliegende Senkbohrung eingepasst, die einen balligen oder einen winkligen Bohrungsgrund aufweist. Ein mittig angesetztes und pilzartiges Befestigungselement 18 fixiert die Verschlussmembran 17 und hält die Verschlussmembran 17 unter einer leichten Spannung auf den Grund der Senkbohrung. Dabei ist diese durch das Befestigungselement 18 eingebrachte Spannung so gewählt, dass die erste Verschlussmembran 17 in ihrer Position drehfähig ist und sich im druckausgeglichenen Zustand nicht von den Einlassöffnungen 16 abhebt. Außerdem sind die Verschlussmembran 17 und das Befestigungselement 18 bündig in die Senkbohrung eingelassen, damit kein Volumen der Niederdruckkammer 5 verloren geht.Thus, as shown in FIG. 2 in the valve housing bottom 7 of the reciprocating compressor 1, an inlet check valve 15 which connects the low-pressure chamber 5 with the atmosphere. To this inlet check valve 15 includes a plurality of arranged on a common circular path inlet openings 16 and a, all inlet openings 16 covering, first sealing membrane 17. The closure membrane 17 is fitted in an inner counterbore, which has a crowned or angled bottom hole. A centrally attached and mushroom-like fastening element 18 fixes the closure membrane 17 and holds the closure membrane 17 under a slight tension on the bottom of the counterbore. In this case, this introduced by the fastening element 18 voltage is selected so that the first sealing membrane 17 is rotatable in its position and does not lift off from the inlet openings 16 in the pressure-balanced state. In addition, the sealing membrane 17 and the fastening element 18 are flush in the counterbore so that no volume of the low-pressure chamber 5 is lost.

So befindet sich weiterhin im Verdichterkolben 9 ein durchgängiger Überströmkanal 19, der die Niederdruckkammer 5 und die Hochdruckkammer 6 miteinander verbindet. Gemäß der Fig. 3 ist im hochdruckseitigen Mündungsbereich dieses Überströmkanals 19 ein Überströmrückschlagventil 20 angeordnet, das die Niederdruckkammer 5 und die Hochdruckkammer 6 funktionsbedingt miteinander verbindet oder trennt. Dazu ist die Mündung des Überströmkanals 19 zu einer im Querschnitt nierenförmigen Kammer 21 aufgeweitet, wobei die Nierenform einer Kreisbahn folgt.
Das Überströmrückschlagventil 20 besteht aus einer Topfmanschette 22 aus Kunststoff, die mit ihrem Boden auf die Stirnfläche des Hochdruckkolben 11 aufliegt und an der Innenwand der Hochdruckkammer 6 dichtend anliegt. Im Bereich des Überströmkanals 19 ist die Topfmanschette 22 durchbrochen.
Zum Überströmrückschlagventil 20 gehört weiterhin ein besonders ausgeführter Ventilhalter 23, der passend in den Innenraum der Topfmanschette 22 eingesetzt ist und der in der Fig. 4 näher gezeigt wird. Dieser Ventilhalter 23 besitzt demnach eine äußere Form, die auf den Innenraum der Topfmanschette 22 ausgerichtet ist. Von der Seite der Hochdruckkammer 6 ist eine zylindrische Ausnehmung 24 eingebracht, deren Achse um einen bestimmten Exzentrizitätsbetrag von der Achse des Hochdruckkolbens 11 entfernt angeordnet ist. Dieser Exentrizitätsbetrag sowie die Größe und die radiale Lage der zylindrischen Ausnehmung 24 gewährleisten, dass die zylindrische Ausnehmung 24 in Überdeckung mit der nierenförmigen Kammer 21 des Überströmkanals 19 liegt. Der Ventilhalter 23 ist außerhalb der zylindrischen Ausnehmung 24 mit verteilt angeordneten Befestigungselementen 25 zur lagebestimmenden Verankerung mit dem Hochdruckkolben 11 ausgerüstet.
Im äußeren radialen Bereich der zylindrischen Ausnehmung 24 befinden sich eine erste Durchgangsbohrung 26 mit einem kleineren Durchmesser und eine zweite Durchgangsbohrung 27 mit einem größeren Durchmesser, die einen gleichen oder unterschiedlichen Abstand zur Achse der zylindrischen Ausnehmung 24 aufweisen und die in ihrer Lage und in ihrer Ausdehnung so ausgelegt sind, dass sie mit der nierenförmigen Kammer 21 des Überströmkanals 19 in Überdeckung liegen. Neben der ersten Durchgangsbohrung 26 und der zweiten Durchgangsbohrung 27 können in gleicher Art weitere Durchgangsbohrungen eingesetzt werden. In die zylindrische Ausnehmung 24 ist eine frei aufliegende zweite Verschlussmembran 28 mit einem solchen Spiel eingepasst, dass sie in Drehrichtung und in axialer Richtung frei beweglich ist und der ringförmige Zwischenraum zwischen der zweiten Verschlussmembran 28 und der Innenwand der zylindrischen Ausnehmung 24 als Luftdurchtritt geeignet ist. Zur Verringerung der Reibungswiderstände sind die benachbarten Kanten der zylindrischen Ausnehmung 24 und der zweiten Verschlussmembran 28 abgerundet bzw. gebrochen ausgeführt.
Die zylindrische Ausnehmung 24 ist weiterhin mit einem Anschlaggitter 29 abgedeckt, das einerseits den axialen Hub der zweiten Verschlussmembran 28 begrenzt und andererseits dem freigegebenen Druckluftstrom einen weitestgehend freien Durchtritt gewährt. Dabei ist die Struktur der Gitterstreben frei gewählt, wobei die Durchbrüche im Anschlaggitter 29 so klein ausgeführt sind, dass sich die zweite Verschlussmembran 28 nicht verklemmen kann. Die Durchbrüche können auch unterschiedlich groß sein.Thus, a continuous overflow channel 19, which connects the low-pressure chamber 5 and the high-pressure chamber 6 to one another, is furthermore located in the compressor piston 9. According to FIG. 3, an overflow check valve 20 is arranged in the high-pressure-side opening region of this overflow channel 19, which functionally connects or disconnects the low-pressure chamber 5 and the high-pressure chamber 6. For this purpose, the mouth of the overflow channel 19 is expanded to a kidney-shaped in cross-section chamber 21, wherein the kidney shape follows a circular path.
The overflow check valve 20 consists of a cup sleeve 22 made of plastic, which rests with its bottom on the end face of the high-pressure piston 11 and sealingly abuts against the inner wall of the high-pressure chamber 6. In the region of the overflow channel 19, the cup sleeve 22 is broken.
For overflow check valve 20 further includes a specially designed valve holder 23 which is fittingly inserted into the interior of the cup 22 and the sleeve is shown in more detail in FIG. This valve holder 23 therefore has an outer shape, which is aligned with the interior of the cup 22. From the side of the high-pressure chamber 6, a cylindrical recess 24 is introduced, the axis of which is arranged at a certain amount of eccentricity away from the axis of the high-pressure piston 11. This amount of eccentricity as well as the size and the radial position of the cylindrical recess 24 ensure that the cylindrical recess 24 is in register with the kidney-shaped chamber 21 of the overflow channel 19. The valve holder 23 is equipped outside the cylindrical recess 24 with distributed arranged fastening elements 25 for position-determining anchoring with the high pressure piston 11.
In the outer radial region of the cylindrical recess 24 are a first through hole 26 having a smaller diameter and a second through hole 27 having a larger diameter, which have an equal or different distance from the axis of the cylindrical recess 24 and in their position and in their extension are designed so that they are in register with the kidney-shaped chamber 21 of the overflow 19. Next to the first through hole 26 and the second through hole 27 further through holes can be used in the same way. In the cylindrical recess 24, a freely resting second closure membrane 28 is fitted with such a game that it is freely movable in the direction of rotation and in the axial direction and the annular space between the second closure membrane 28 and the inner wall of the cylindrical recess 24 is suitable as an air passage. To reduce the frictional resistance, the adjacent edges of the cylindrical recess 24 and the second sealing membrane 28 are rounded or broken executed.
The cylindrical recess 24 is further covered with a stop grid 29, on the one hand limits the axial stroke of the second closure membrane 28 and on the other hand grants the released compressed air flow a largely free passage. The structure of the lattice struts is chosen freely, wherein the openings in the stop grid 29 are made so small that the second sealing membrane 28 can not jam. The breakthroughs can also be different sizes.

Weiterhin besitzt die Hochdruckkammer 6 ein Auslassrückschlagventil 30 zur Verbindung der Hochdruckkammer 6 mit einer Verbraucherleitung. Dieses Auslassrückschlagventil 30 ist nach der Fig. 3 zwischen dem Ventilgehäuse 4 und dem Ventilgehäusedeckel 8 angeordnet und besteht aus einer am Umfang eingespannten Ventilplatte 31 und einer dritten Verschlussmembran 32. Die Ventilplatte 31 ist gegenüber dem Ventilgehäuse 4 und gegenüber dem Ventilgehäusedeckel 8 abgedichtet ausgeführt und besitzt mehrere auf einem gemeinsamen Teilkreis angeordnete Auslassöffnungen 33. Die dritte Verschlussmembran 32 ist als ein Ring gestaltet und besitzt demnach eine mittige Durchflussbohrung 34. Mit ihrem Umfang ist die dritte Verschlussmembran 32 zwischen der Ventilplatte 31 und dem Ventilgehäusedeckel 8 festgehalten, während die Durchflussbohrung 34 mit ihrem Durchmesser so ausreichend kleiner als der Teilkreisdurchmesser der Durchmesser der Auslassöffnungen ausgelegt ist, dass die Auslassöffnungen 33 von der dritten Verschlussmembran 32 voll überdeckt werden.Furthermore, the high-pressure chamber 6 has an outlet check valve 30 for connecting the high-pressure chamber 6 to a consumer line. This outlet check valve 30 is arranged according to the Fig. 3 between the valve housing 4 and the valve housing cover 8 and consists of a circumferentially clamped valve plate 31 and a third sealing membrane 32. The valve plate 31 is sealed against the valve housing 4 and against the valve housing cover 8 and has The third sealing membrane 32 is designed as a ring and thus has a central flow bore 34. With its periphery, the third sealing membrane 32 between the valve plate 31 and the valve housing cover 8 is held while the flow bore 34 with its Diameter is sufficiently smaller than the pitch circle diameter of the diameter of the outlet openings is designed so that the outlet openings 33 are completely covered by the third sealing membrane 32.

Die dritte Verschlussmembran 32 ist ohne konstruktive Vorspannung eingebaut, so dass sich die Schließkraft nur aus der materialspezifischen Eigenspannung ergibt.
Die erste Verschlussmembran 17 des Einlassrückschlagventiles 15, die zweite Verschlussmembran 28 des Überströmrückschlagventiles 28 und die dritte Verschlussmembran 32 des Auslassrückschlagventiles 30 bestehen aus Kunststoff, insbesondere aus einem elastischen Polymer, das in der Hauptsache eine hohe Durchschlagsfestigkeit besitzt, hoch temperaturbeständig ist und elastische Eigenschaften mit Memory-Effekt aufweist.The third sealing membrane 32 is installed without constructive bias, so that the closing force results only from the material-specific residual stress.
The first sealing membrane 17 of the inlet check valve 15, the second sealing membrane 28 of the overflow check valve 28 and the third sealing membrane 32 of the outlet check valve 30 are made of plastic, in particular of an elastic polymer, which has a high dielectric strength, high temperature resistance and elastic properties with memory Effect.

Während des Betriebes wird die drehende Bewegung der vom Antriebsmotor 2 angetriebenen Kurbelwelle 14 über das Pleuel 13 in eine oszillierende Linearbewegung umgewandelt und auf den Ventilkolben 9 übertragen. Damit bewegen sich gleichermaßen der Niederdruckkolben 10 und der Hochdruckkolben 11 zwischen zwei gegenüberliegenden Umkehrpunkten und bilden so zwei sich im Volumen wechselweise verändernde Niederdruckkammer 5 und Hochdruckkammer 6.
Dabei entsteht bei einer sich vergrößernden Niederdruckkammer 5 ein solcher Unterdruck, der die erste Verschlussmembran 17 an seinem äußeren Umfang anheben und Außenluft durch die Einlassöffnungen 16 einströmen lässt. Dieser Öffnungsdruck ergibt sich aus der Summe der Materialspannung der Verschlussmembran 17 und der einbaubedingten Vorspannung an der Verschlussmembran 17. Gleichzeitig schließt der Unterdruck die zweite Verschlussmembran 28 des Überströmrückschlagventiles 20.
Am oberen Umkehrpunkt der Bewegung des Ventilkolbens 9 stellt sich an der ersten Verschlussmembran 17 ein ausgeglichener Druck zwischen der Niederdruckkammer 5 und der Atmosphäre ein, wodurch die Verschlussmembran 17 durch die genannten Kräfte der Vorspannung auf die Einlassöffnungen 16 gedrückt wird und diese verschließt. Auf Grund der optimalen Auswahl der Material- und Einbauspannungen treten einerseits beim Ansaugen geringste Durchflusswiderstände auf und schließt andererseits die erste Verschlussmembran 17 in kürzester Zeit nach dem Erreichen des oberen Umkehrpunktes. Das verbessert den Wirkungsgrad des Kolbenverdichters erheblich.During operation, the rotating movement of the driven by the drive motor 2 crankshaft 14 is converted via the connecting rod 13 in an oscillating linear motion and transmitted to the valve piston 9. Thus, both the low-pressure piston 10 and the high-pressure piston 11 move between two opposing reversal points and thus form two alternately changing low-pressure chamber 5 and high-pressure chamber 6.
In the event of an enlarging low-pressure chamber 5, such a negative pressure arises, which raises the first closing membrane 17 on its outer circumference and allows outside air to flow through the inlet openings 16. This opening pressure results from the sum of the material tension of the closure membrane 17 and the installation-related bias on the closure membrane 17. At the same time, the negative pressure closes the second closure membrane 28 of the overflow check valve 20.
At the upper reversal point of the movement of the valve piston 9, a balanced pressure is established between the low-pressure chamber 5 and the atmosphere at the first closure membrane 17, whereby the closure membrane 17 is pressed onto the inlet openings 16 by the said forces of the prestress and closes them. Due to the optimum selection of the material and installation voltages, on the one hand, the lowest flow resistance occurs during suction and, on the other hand, closes the first sealing membrane 17 in the shortest possible time after reaching the upper reversal point. This considerably improves the efficiency of the reciprocating compressor.

Mit der umgekehrten Bewegung des Ventilkolbens 9 wird die Niederdruckkammer 5 verkleinert, sodass die dort eingespannte Luft unter Druck durch den Überströmkanal 19 zur Hochdruckkammer 6 befördert wird. Dabei strömt die Luft zunächst in die nierenförmige Kammer 21 des Überströmkanales 19 und belastet von dort die zweite Verschlussmembran 28 im Bereich und im Umfang der ersten Durchgangsbohrung 26 und der zweiten Durchgangsbohrung 27. Damit wirkt über die erste Durchgangsbohrung 26 eine erste Öffnungskraft und über die zweite Durchgangsbohrung 27 eine zweite Öffnungskraft auf die zweite Verschlussmembran 28 ein, die beide parallel zueinander wirken. Diese beiden Kräfte sind so unterschiedlich, wie die Querschnitte der beiden Durchgangsbohrungen 26 und 27. Damit kommt die freiliegende zweite Verschlussmembran 28 in eine Schieflage und durch radiale Kraftkomponenten in eine radiale Drehbewegung, die von der kleineren Durchflussbohrung 26 zur größeren Durchflussbohrung 27 gerichtet ist und die die Lage der zweiten Verschlussmembran 28 zu den beiden Durchgangsbohrungen 26, 27 stetig verändert. Das verlängert die Lebensdauer der zweiten Verschlussmembran 28 entscheidend, da die Belastung des Materials der Verschlussmembran 28 umlaufend verteilt wird und somit eine vorzeitige Überlastung nur einer bestimmten Stelle der Verschlussmembran 28 vermieden wird. Eine solche Überlastung führt schnell zum Durchschlagen und zu einem Ausfall des Überströmrückschlagventiles 20. Die freiliegende zweite Verschlussmembran 28 setzt dem durchfließenden Druckluftstrom nur einen geringsten Widerstand entgegen.
Am unteren Umkehrpunkt der Bewegung des Ventilkolbens 9 stellt sich wieder ein ausgeglichener Druck zwischen der Niederdruckkammer 5 und der Hochdruckkammer 6 ein, der das Überströmrückschlagventil 20 schließen lässt. Durch die freie und reibungsarme Führung der zweiten Verschlussmembran 28 erfolgt die Schließung äußerst reaktionsschnell.
Mit der die Hochdruckkammer 6 verkleinernden Bewegung des Ventilkolbens 9 wird die in der Hochdruckkammer 6 eingeschlossene Druckluft über das Auslassrückschlagventil 30 verdrängt. Dabei passiert die Druckluft die von der dritten Verschlussmembran 32 freigegebenen Auslassöffnungen 33. Am oberen Umkehrpunkt der Bewegung des Ventilkolbens 9 schließt das Auslassrückschlagventil 30 wiederum äußerst reaktionssclmell.With the reverse movement of the valve piston 9, the low pressure chamber 5 is reduced, so that the air clamped there is conveyed under pressure through the overflow 19 to the high pressure chamber 6. In this case, the air first flows into the kidney-shaped chamber 21 of the overflow channel 19 and loads from there the second sealing membrane 28 in the area and in the circumference of the first through-bore 26 and the second through-bore 27. Thus acts on the first through-bore 26, a first opening force and the second Through hole 27, a second opening force on the second sealing membrane 28, both of which act in parallel. These two forces are as different as the cross sections of the two through holes 26 and 27. Thus, the exposed second closure membrane 28 is in a lopsided position and by radial force components in a radial rotational movement, which is directed from the smaller flow bore 26 to the larger flow bore 27 and the the position of the second closure membrane 28 to the two through holes 26, 27 changed steadily. This prolongs the life of the second sealing membrane 28 decisively, since the loading of the material of the sealing membrane 28 is distributed circumferentially and thus premature overloading only a certain point of the sealing membrane 28 is avoided. Such an overload quickly leads to strike through and failure of the overflow check valve 20. The exposed second closure membrane 28 opposes the flow of compressed air flow only a slightest resistance.
At the lower reversal point of the movement of the valve piston 9 is again a balanced pressure between the low-pressure chamber 5 and the high-pressure chamber 6, which can close the overflow check valve 20. Due to the free and low-friction guidance of the second closure membrane 28, the closure is extremely responsive.
With the movement of the valve piston 9, which reduces the high-pressure chamber 6, the compressed air enclosed in the high-pressure chamber 6 is displaced via the outlet check valve 30. The compressed air passes from the third sealing membrane 32 released outlet openings 33. At the upper reversal point of the movement of the valve piston 9, the outlet check valve 30 closes again extremely reaction-clmell.

Liste der BezugszeichenList of reference numbers

11
Kolbenverdichterpiston compressor
22
Antriebsmotordrive motor
33
LufttrocknereinheitAir dryer unit
44
Ventilgehäusevalve housing
55
NiederdruckkammerLow-pressure chamber
66
HochdruckkammerHigh-pressure chamber
77
VentilgehäusebodenValve housing bottom
88th
VentilgehäusedeckelValve cover
99
Verdichterkolbenpistons compressor
1010
NiederdruckkolbenLow-pressure piston
1111
HochdruckkolbenHigh pressure piston
1212
Kolbenstangepiston rod
1313
Pleuelpleuel
1414
Kurbelwellecrankshaft
1515
EinlassrückschlagventilInlet check valve
1616
Einlassöffnungeninlets
1717
Erste VerschlussmembranFirst sealing membrane
1818
Befestigungselementfastener
1919
Überströmkanaloverflow
2020
ÜberströmrückschlagventilÜberströmrückschlagventil
2121
Nierenförmige KammerKidney shaped chamber
2222
Topfmanschettecup seal
2323
Ventilhaltervalve holder
2424
Zylindrische AusnehmungCylindrical recess
2525
Befestigungselementfastener
2626
Erste DurchgangsbohrungFirst through hole
2727
Zweite DurchgangsbohrungSecond through-hole
2828
Zweite VerschlussmembranSecond sealing membrane
2929
Anschlaggitterstop grid
3030
Auslassrückschlagventiloutlet check valve
3131
Ventilplattevalve plate
3232
Dritte VerschlussmembranThird sealing membrane
3333
Auslassöffnungoutlet
3434
DurchflussbohrungFlow bore

Claims (7)

  1. Multi-stage piston compressor, consisting of a valve housing (4) and of a displaceable valve piston (9) driven in linear oscillation by a drive motor (2) and produced in one piece, with a low-pressure piston (10) and a high-pressure piston (11) which together form at least one variable-volume low-pressure chamber (5) having an inlet non-return valve (15) and at least one variable-volume high-pressure chamber (6) having an outlet non-return valve (30), in each case a low-pressure chamber (5) and a high-pressure chamber (6) being connected to one another via an overflow duct (19) in which an overflow non-return valve (20) opening in the direction of the high-pressure chamber (6) is inserted, the overflow non-return valve (20) being equipped with a sealing disc, characterized in that the overflow duct (19) issues into at least two passage bores (26, 27), and the sealing disc of the overflow non-return valve (20) is designed as a loosely guided and stroke-limited closing diaphragm (28), the passage bores (26, 27) of the overflow duct (19) having different diameters and being arranged on a common reference circle at a radial distance from the axis of the closing diaphragm (28) and being covered completely by the closing diaphragm (28).
  2. Multi-stage piston compressor according to Claim 1, characterized in that the closing diaphragm (28) is fitted into a recess (24) of a valve holder (23) and is covered by an abutment grid (29).
  3. Multi-stage piston compressor according to Claim 2, characterized in that the two throughflow bores (26, 27) of different diameter are introduced into the cylindrical recess (24) of the valve holder (23) and possess a connection to the overflow duct (19), the overflow duct (19) being designed in the region of issue as a kidney-shaped chamber (21).
  4. Multi-stage piston compressor according to Claim 1, characterized in that the closing diaphragm (28) consists of an elastic polymer with a high puncture strength, with high temperature compatibility and with memory properties.
  5. Single-stage or multi-stage piston compressor according to Claim 4, characterized in that the inlet non-return valve (15) is equipped with a first closing diaphragm (17) and the outlet non-return valve (30) is equipped with a third closing diaphragm (32), the said closing diaphragms likewise consisting of an elastic polymer with identical properties.
  6. Single-stage or multi-stage piston compressor according to Claim 5, in which the inlet non-return valve (15) is equipped with a plurality of inlet ports (16) arranged on a reference circle, characterized in that the first closing diaphragm (17) of the inlet non-return valve (15) is fitted into a countersunk bore of the valve-housing bottom (7), with a cambered or angled bore base, and is fixed under tension by means of a centrally attached mushroom-like fastening element (18), the fastening element (18) penetrating into the countersunk bore only to an extent such that it is flush with the inner face of the valve-housing bottom (7) and pretensions the first closing diaphragm (17) only to an extent such that the closing diaphragm (17) still remains rotatable.
  7. Single-stage or multi-stage piston compressor according to Claim 5, in which the outlet non-return valve (30) possesses a plurality of outlet ports (33) arranged on a common reference circle, characterized in that the outlet ports (33) are introduced into a valve plate (31) which is tension-mounted between the valve housing (4) and a valve-housing cover (8), and the third closing diaphragm (32) is designed as a ring and is held with its outer circumference, without tension, between the valve plate (31) and the valve-housing cover (8), the third closing diaphragm (32) covering the outlet ports (33) with its inner circumference.
EP02745080A 2001-05-25 2002-05-24 Multi-stage piston-type compressor Expired - Lifetime EP1395755B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10125420A DE10125420C1 (en) 2001-05-25 2001-05-25 Multi-stage reciprocating compressor with interconnected high- and low pressure cylinders, employs plastic disc closure in non return valve
DE10125420 2001-05-25
PCT/DE2002/001887 WO2002095227A1 (en) 2001-05-25 2002-05-24 Multi-stage piston-type compressor

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EP1395755A1 EP1395755A1 (en) 2004-03-10
EP1395755B1 true EP1395755B1 (en) 2006-12-13

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EP (1) EP1395755B1 (en)
AT (1) ATE348266T1 (en)
DE (2) DE10125420C1 (en)
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US7351044B2 (en) 2008-04-01
DE50208956D1 (en) 2007-01-25
EP1395755A1 (en) 2004-03-10
US20060104844A1 (en) 2006-05-18
ATE348266T1 (en) 2007-01-15
DE10125420C1 (en) 2002-10-24
WO2002095227A1 (en) 2002-11-28

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