EP0346285B1 - Valve arrangement - Google Patents

Valve arrangement Download PDF

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Publication number
EP0346285B1
EP0346285B1 EP89810419A EP89810419A EP0346285B1 EP 0346285 B1 EP0346285 B1 EP 0346285B1 EP 89810419 A EP89810419 A EP 89810419A EP 89810419 A EP89810419 A EP 89810419A EP 0346285 B1 EP0346285 B1 EP 0346285B1
Authority
EP
European Patent Office
Prior art keywords
valve
lid
valve arrangement
arrangement according
diaphragm
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
EP89810419A
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German (de)
French (fr)
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EP0346285A1 (en
Inventor
Heinz Baumann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Atlas Copco Schweiz AG
Original Assignee
Gebrueder Sulzer AG
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Publication date
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Publication of EP0346285A1 publication Critical patent/EP0346285A1/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
    • F04B39/102—Adaptations or arrangements of distribution members the members being disc valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7922—Spring biased
    • Y10T137/7929—Spring coaxial with valve
    • Y10T137/7937—Cage-type guide for stemless valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87571—Multiple inlet with single outlet
    • Y10T137/87587—Combining by aspiration

Definitions

  • the invention relates to a valve arrangement, in particular for piston compressors, pumps or the like, with a component which contains a passage opening through which a fluid can flow and a disk-like valve body which covers the passage opening and interacts with a valve seat surrounding it and which, together with a valve seat which can be braced against it
  • the spring element is freely movable in a fluid flow-through recess of a guide part that at least partially surrounds the valve seat, said recess being designed at a distance from the valve seat that allows the valve body to be lifted off, with inwardly projecting shoulders on which the Part of the spring element facing away from the valve body rests under pretension.
  • valve body formed by a flat plate is braced against the valve seat by a coil spring.
  • This valve construction requires a relatively large, high installation space to accommodate the coil spring.
  • Valve arrangements used in reciprocating compressors are known, each having an annular or concentric slot valve plate, which together with a spring plate by a central screw or e.g. are clamped by three corresponding fastening elements distributed over the valve between a valve seat part which can be placed on the passage opening and a holding plate which can be braced against the latter, the valve seat part and the holding plate being provided with openings through which the fluid can flow.
  • These known, multi-part valve constructions each require a relatively large installation space and, in addition, a relatively large amount of work when assembling and installing the valve.
  • the invention has for its object to provide a valve arrangement of the type mentioned improved in this regard in a simplified, compact and inexpensive construction, in particular with a low overall height, which enables an embodiment with a small clearance and correspondingly small dimensions of the required installation space.
  • valve body is designed with a central local elevation on the side facing away from the valve seat, and in that the spring element is formed by a round spring plate which can be loosely braced against this elevation, the elevation being a support surface for a central supporting surface the spring plate.
  • valve body and the spring element enables a particularly flat, compact design of the valve, its installation height essentially only by the thicknesses of the valve body and the spring plate and is determined by the stroke of the valve body.
  • simple installation and removal of the spring element in particular is ensured, since the flat spring plate, when untensioned, is correspondingly easier to handle than a helical spring, for example.
  • the pistons 5 and 7 are coupled via a yoke 14 connecting their piston rods 12 and 13 to a sliding piece 15 which is mounted on a crank pin 16 of a crankshaft 17.
  • the crankshaft 17 is connected to a motor, not shown, for example an electric motor.
  • the slider 15 is guided transversely to the axis 10 between two guideways 18 formed in the yoke 14.
  • the pistons 6 and 7 are via a yoke 22 connecting their piston rods 20 and 21, respectively coupled to a second slider, not shown, mounted on the crank pin 16, which is displaceably guided transversely to the axis 11 in the yoke 22, which is offset by 90 ° relative to the yoke 14.
  • the compression space 31 of the cylinder 1 forming the first compression stage is delimited by an end plate 35 which is inserted into the cylinder head 27 and which is provided with several, for example four through openings 36 arranged offset in the circumferential direction are provided.
  • the passage openings 36, of which only one is visible in FIG. 1, are each provided with a pressure valve 37.
  • the pressure valves 37 are each arranged on the side of the end plate 35 facing away from the piston 5 in a recess 38 of a guide part, according to FIG.
  • a plurality of passage openings 42 are also formed in the piston 5, each of which is provided with a suction valve 41.
  • a connection is established between the compression space 31 and a cylinder space 43 separated from it by the piston 5, which is connected to a feed line (not shown) for the medium to be compressed, e.g. Natural gas, is connected.
  • the suction valves 41 are arranged on the side of the piston 5 facing the compression space 31, each in a recess 44 of a further guide part detachably fastened to the piston 5, as shown in the illustration of a holding plate 45.
  • the compression spaces 32 and 33 are each one on the cylinder insert 24 and 25th attached end plate 46 and 47 limited.
  • the end plates 46 and 47 each contain a central through-opening 36 provided with the pressure valve 37, for example four, provided with suction valves 41, circumferentially offset through-openings 42, of which only one is also visible in FIG. 1.
  • the recess 38 receiving the pressure valve 37 is formed in the cylinder cover 28 and 29, respectively.
  • the recesses 44 receiving the suction valves 41 are each formed in the end part of the cylinder insert 24 or 25 facing the inside of the end plate 46 or 47, which serves as a guide part for the suction valves 41.
  • the recesses 38 are each connected to the compression space 32 or 33 by a lateral opening.
  • both a passage opening 36 provided with the pressure valve 37 and a passage opening 42 provided with the suction valve 41 are formed in the cylinder cover 30, the recess 38 receiving the pressure valve 37 in a connecting nipple 50 which can be screwed into the cylinder cover 30 of a pressure line leading away from the compressor 51 is formed, while the recess 44 receiving the suction valve 41 is formed in a nipple 52 which connects the compression space 34 to a flow channel 58 formed in the cylinder cover 30.
  • the piston 5 is shown in its top dead center position, in which the compression space 31 is the smallest.
  • the gas supplied to the cylinder space 43 is sucked through the passage opening 42 with the suction valve 41 open.
  • the gas compressed to a pressure of, for example, 5 bar, with the pressure valve 37 open is passed through the passage opening 36 into a cylinder space 55 and from there via a connecting cylinder cover 27 and 28 Flow channel 56 and an annular channel 48 of the second compression stage formed by the cylinder 2 are supplied.
  • the gas sucked into the compression chamber 32 through the passage openings 42 during the suction stroke of the piston 6 is reduced to a pressure of e.g. Compressed 20 bar and supplied with the pressure valve 37 open via a flow channel 57 connecting the cylinder covers 28 and 29 and an annular channel 49 to the third compression stage formed by the cylinder 3.
  • Fig. 1 the piston 7 of the cylinder 3 is shown in the bottom dead center position, in which the compression space 33 is largest.
  • the gas sucked into the compression space 33 during the suction stroke of the piston 7 is reduced to a pressure of e.g. 60 bar compressed and fed via the flow channel 58 connecting the cylinder covers 29 and 30 and through connection channels 59 and 60 formed in the nipple 52 to the fourth compression stage formed by the cylinder 4.
  • the gas sucked into the compression space 34 during the suction stroke of the piston 8 is brought to a pressure of e.g. 180 bar compressed and supplied with the pressure valve 37 open via the pressure line 51 to a gas fuel tank, not shown, which e.g. can be designed as a fuel tank of a motor vehicle.
  • All pressure valves 37 and suction valves 41 are, apart from any different dimensions of the interacting parts, essentially the same design.
  • the pressure valve 37 contains a disk-shaped round valve body 61 and which completely covers the associated passage opening 36 a round spring plate 62, under the action of which the valve body 61 loosely rests with a flat contact surface against a valve seat 63 surrounding the passage opening 36.
  • the valve seat 63 is formed directly on the end plate 35 delimiting the compression space 31.
  • the valve body 61 is provided on the side facing away from the valve seat 63 with a central elevation 64, which can be formed, for example, by a cylindrical extension or, as shown in FIG.
  • a bearing surface 65 for a central supporting surface 66 of the spring plate 62 is formed on the elevation 64.
  • the spring plate 62 is held clamped in the recess 38 of the holding plate 40 surrounding the pressure valve 37 against the valve body 61, the recess 38 being designed with a shoulder 67 narrowing in cross section.
  • the shoulder 67 protrudes at a distance from the valve body 61 which allows the valve body 61 to be lifted off and thus forms an abutment for the edge part 71 of the spring plate 62 which can be biased against it.
  • the recess 38 can be designed with local, niche-like extensions 68 which are distributed over its circumference and which ensure a low-loss flow through the recess 38 through the gas emerging from the compression space 31 when the pressure valve 37 is open. It goes without saying that a different number of extensions, or possibly only a single corresponding connection opening, can also be provided.
  • three slots 70 are formed in the spring plate 62 over their surface in the circumferential direction, each of which, one on an annular edge portion 71 the reference point 72 lying on the spring plate 62, runs spirally essentially over the four quadrants A, B, C and D of the surface of the spring plate 62 against its central support surface 66.
  • This support surface 66 which corresponds to the contact surface 65 of the elevation 64, is determined by an imaginary circle inscribed between the inner ends 73 of the three slots 70.
  • the slots 70 are designed such that, starting from their respective reference point 72, they each have an initial section E running along the edge section 71 with a width increasing in the area of the first quadrant A towards the second quadrant B and decreasing at the beginning of the second quadrant B.
  • the course of the slots 71 is selected such that webs 74 remain between them, each of which has a width H which, starting from the edge part 71, continuously decreases slightly over the first half of its length and against the second half of its length the central support surface 66 continuously increases slightly.
  • the support surface 66 can be made relatively small without an opening, and thus, like the corresponding contact surface 65 of the elevation 64. This construction therefore results, with optimal use of the material of the spring plate 62, in a design with relatively long, favorably stressed webs 74, which allow a relatively large spring travel with a small diameter of the spring plate 62. Accordingly, a maximum deflection of the spring plate is obtained if a minimum clearance is maintained 62 achieved so that the structural dimensions of the compressor can be kept correspondingly small.
  • the valve design according to the invention is particularly suitable for small, dry-running compressors, the valve body 61 and spring plates 62 e.g. Can have diameters of about 10 to 12 mm.
  • the spring plates 62 can be made of spring steel or another material suitable for leaf springs, such as titanium or beryllium, and each have a thickness of 0.1 to 0.3 mm. It goes without saying that designs with dimensions other than those described are also possible.
  • the valve bodies 61 can be made of metal or a plastic, e.g. Polyether ether ketone (PEEK).
  • the plastic design in particular, enables a cost-effective, low-mass and low-noise valve arrangement to be achieved, which responds quickly and which guarantees operation with minimal wear and a correspondingly long service life.
  • An optimal ratio between the maximum deflection and the spring force of the spring plate 62 can be achieved in versions in which the bearing surface 65 formed on the elevation 64 and the central support surface 66 of the spring plate 62 have a diameter which is approximately 1/4 to 1/8 of the diameter of the valve body 61.
  • Modified embodiments can contain valve bodies, each of which is designed with a conical or lenticular contact surface and which cooperate with correspondingly designed valve seats.
  • An embodiment is also possible in which the valve seat is formed on an exchangeable insert.
  • the invention is not limited to use on compressors of the type described and illustrated above, but is also for other, single or multi-stage designs, as well as for other applications, e.g. suitable for pipes, breathing air compressors, compressors for low-temperature technology or compressors for compressing CO2, nitrogen and similar media.
  • the valve arrangement according to the invention is also suitable for use on pumps or lines for liquid media, e.g. Water or liquid gas, suitable.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Description

Die Erfindung betrifft eine Ventilanordnung, insbesondere für Kolbenkompressoren, Pumpen oder dergleichen, mit einem Bauteil, der eine von einem Fluid durchströmbare Durchtrittsöffnung enthält, und einem scheibenartigen Ventilkörper, welcher die Durchtrittsöffnung überdeckt und mit einem diese umgebenden Ventilsitz zusammenwirktund welcher zusammen mit einem gegen ihn verspannbaren Federelement frei beweglich in einer gegen die Durchtrittsöffnung hin offenen, vom Fluid durchströmbaren Ausnehmung eines den Ventilsitz zumindest teilweise umgebenden Führungsteils angeordnet ist, wobei diese Ausnehmung in einem ein Abheben des Ventilkörpers zulassenden Abstand vom Ventilsitz mit nach innen vorstehenden Absätzen ausgeführt ist, an denen die dem Ventilkörper abgewandte Partie des Federelementes unter Vorspannung anliegt.The invention relates to a valve arrangement, in particular for piston compressors, pumps or the like, with a component which contains a passage opening through which a fluid can flow and a disk-like valve body which covers the passage opening and interacts with a valve seat surrounding it and which, together with a valve seat which can be braced against it The spring element is freely movable in a fluid flow-through recess of a guide part that at least partially surrounds the valve seat, said recess being designed at a distance from the valve seat that allows the valve body to be lifted off, with inwardly projecting shoulders on which the Part of the spring element facing away from the valve body rests under pretension.

Bei einer aus der FR-A-2 339 116 bekannten Ventilanordnung der genannten Art ist der durch eine flache Platte gebildete Ventilkörper durch eine Schraubenfeder gegen den Ventilsitz verspannt. Diese Ventilkonstruktion erfordert einen relativ grossen, hohen Einbauraum zur Aufnahme der Schraubenfeder.In a valve arrangement of the type mentioned known from FR-A-2 339 116, the valve body formed by a flat plate is braced against the valve seat by a coil spring. This valve construction requires a relatively large, high installation space to accommodate the coil spring.

Es sind auch andere, z.B. bei Kolbenkompressoren verwendete Ventilanordnungen bekannt, welche je eine ringförmige oder mit konzentrischen Schlitzen versehene Ventilplatte aufweisen, die zusammen mit einer Federplatte durch eine zentrale Schraube oder z.B. durch drei entsprechende, über das Ventil verteilte Befestigungselemente zwischen einem auf die Durchtrittsöffnung aufsetzbaren Ventilsitzteil und einer gegen diesen verspannbaren Halteplatte eingespannt sind, wobei der Ventilsitzteil und die Halteplatte mit vom Fluid durchströmbaren Durchbrüchen versehen sind. Auch diese bekannten, mehrteiligen Ventilkonstruktionen erfordern jeweils einen relativ grossen Einbauraum und zusätzlich einen relativ grossen Arbeitsaufwand beim Zusammenbau und beim Einbau des Ventils.There are also others, e.g. Valve arrangements used in reciprocating compressors are known, each having an annular or concentric slot valve plate, which together with a spring plate by a central screw or e.g. are clamped by three corresponding fastening elements distributed over the valve between a valve seat part which can be placed on the passage opening and a holding plate which can be braced against the latter, the valve seat part and the holding plate being provided with openings through which the fluid can flow. These known, multi-part valve constructions each require a relatively large installation space and, in addition, a relatively large amount of work when assembling and installing the valve.

Der Erfindung liegt die Aufgabe zugrunde, eine in dieser Hinsicht verbesserte Ventilanordnung der eingangs genannten Art in einer vereinfachten, kompakten und kostengünstigen Bauweise, insbesondere mit geringer Bauhöhe zu schaffen, welche eine Ausführung mit geringem Schadraum und entsprechend geringen Abmessungen des erforderlichen Einbauraumes ermöglicht.The invention has for its object to provide a valve arrangement of the type mentioned improved in this regard in a simplified, compact and inexpensive construction, in particular with a low overall height, which enables an embodiment with a small clearance and correspondingly small dimensions of the required installation space.

Diese Aufgabe wird erfindungsgemäss dadurch gelöst, dass der Ventilkörper auf der dem Ventilsitz abgewandten Seite mit einer zentralen örtlichen Erhebung ausgeführt ist, und dass das Federelement durch eine lose gegen diese Erhebung verspannbare, runde Federplatte gebildet ist, wobei die Erhebung eine Auflagefläche für eine zentrale Stützfläche der Federplatte aufweist.This object is achieved according to the invention in that the valve body is designed with a central local elevation on the side facing away from the valve seat, and in that the spring element is formed by a round spring plate which can be loosely braced against this elevation, the elevation being a support surface for a central supporting surface the spring plate.

Die erfindungsgemässe Ausbildung des Ventilkörpers und des Federelementes ermöglicht eine besonders flache, kompakte Ausführung des Ventils, dessen Einbauhöhe im wesentlichen nur durch die Dicken des Ventilkörpers und der Federplatte sowie durch den Hub des Ventilkörpers bestimmt ist. Zugleich wird ein einfacher Ein- und Ausbau insbesondere des Federelementes gewährleistet, da die in ungespanntem Zustand flache Federplatte entsprechend leichter zu handhaben ist als etwa eine Schraubenfeder.The inventive design of the valve body and the spring element enables a particularly flat, compact design of the valve, its installation height essentially only by the thicknesses of the valve body and the spring plate and is determined by the stroke of the valve body. At the same time, simple installation and removal of the spring element in particular is ensured, since the flat spring plate, when untensioned, is correspondingly easier to handle than a helical spring, for example.

Ausgestaltungen der Erfindung sind in den abhängigen Patentansprüchen angegeben.Embodiments of the invention are specified in the dependent claims.

Weitere Merkmale ergeben sich aus der folgenden Beschreibung eines in der Zeichnung schematisch dargestellten Ausführungsbeispiels der Erfindung. Es zeigen:

  • Fig. 1 einen mit Ventilanordnungen nach der Erfindung versehenen Hubkolbenkompressor in einem durch zwei Horizontalebenen geführten Schnitt;
  • Fig. 2 eine der Ventilanordnungen nach der Erfindung in einem Ausschnitt aus der Fig. 1 in einer grösseren Darstellung;
  • Fig. 3 die Ventilanordnung nach Fig. 2 in einer Draufsicht;
  • Fig. 4 eine Einzelheit der Ventilanordnung in einer Draufsicht.
Further features result from the following description of an exemplary embodiment of the invention shown schematically in the drawing. Show it:
  • 1 shows a reciprocating compressor provided with valve arrangements according to the invention in a section taken through two horizontal planes;
  • 2 shows one of the valve arrangements according to the invention in a detail from FIG. 1 in a larger representation;
  • 3 shows the valve arrangement according to FIG. 2 in a top view;
  • Fig. 4 shows a detail of the valve assembly in a plan view.

Der Kompressor nach Fig. 1 weist vier Zylinder 1, 2, 3 und 4 auf, in denen Kolben 5, 6, 7 und 8 geführt sind. Die Zylinder 1 und 2 weisen eine in der Zeichnungsebene liegende gemeinsame Achse 10 auf, während die Zylinder 2 und 4 auf einer gegenüber der Zeichnungsebene zurückversetzten gemeinsamen Achse 11 angeordnet sind. Die Kolben 5 und 7 sind über ein ihre Kolbenstangen 12 bzw. 13 verbindendes Joch 14 mit einem Gleitstück 15 gekoppelt, welches auf einem Kurbelzapfen 16 einer Kurbelwelle 17 gelagert ist. Die Kurbelwelle 17 ist mit einem nicht dargestellten Motor, z.B. einem Elektromotor, verbunden. Das Gleitstück 15 ist zwischen zwei im Joch 14 ausgebildeten Führungsbahnen 18 quer zur Achse 10 verschiebbar geführt. Die Kolben 6 und 7 sind über ein ihre Kolbenstangen 20 bzw. 21 verbindendes Joch 22 mit einem auf dem Kurbelzapfen 16 gelagerten, nicht dargestellten zweiten Gleitstück gekoppelt, welches in dem gegenüber dem Joch 14 um 90° versetzten Joch 22 quer zur Achse 11 verschiebbar geführt ist.1 has four cylinders 1, 2, 3 and 4, in which pistons 5, 6, 7 and 8 are guided. The cylinders 1 and 2 have a common axis 10 lying in the plane of the drawing, while the cylinders 2 and 4 are arranged on a common axis 11 set back from the plane of the drawing. The pistons 5 and 7 are coupled via a yoke 14 connecting their piston rods 12 and 13 to a sliding piece 15 which is mounted on a crank pin 16 of a crankshaft 17. The crankshaft 17 is connected to a motor, not shown, for example an electric motor. The slider 15 is guided transversely to the axis 10 between two guideways 18 formed in the yoke 14. The pistons 6 and 7 are via a yoke 22 connecting their piston rods 20 and 21, respectively coupled to a second slider, not shown, mounted on the crank pin 16, which is displaceably guided transversely to the axis 11 in the yoke 22, which is offset by 90 ° relative to the yoke 14.

Die in Zylindereinsätzen 23, 24, 25 und 26 geführten Kolben 5, 6, 7 und 8 begrenzen in den durch lösbar befestigte Zylinderdeckel 27, 28, 29 und 30 abgeschlossenen Zylindern 1, 2, 3 und 4 je einen Kompressionsraum 31, 32, 33 bzw. 34. Der Kompressionsraum 31 des die erste Verdichtungsstufe bildenden Zylinders 1 ist durch eine in den Zylinderkopf 27 eingesetzte Stirnplatte 35 begrenzt, die mit mehreren, z.B. vier, in Umfangsrichtung gegeneinander versetzt angeordneten Durchtrittsöffnungen 36 versehen sind. Die Durchtrittsöffnungen 36, von denen in der Fig. 1 nur eine sichtbar ist, sind je mit einem Druckventil 37 versehen. Die Druckventile 37 sind auf der dem Kolben 5 abgewandten Seite der Stirnplatte 35 je in einer Ausnehmung 38 eines Führungsteils, gemäss Fig. 1 einer Halteplatte 40, angeordnet, die auf der Stirnplatte 35 lösbar befestigt ist. Im Kolben 5 sind ebenfalls mehrere Durchtrittsöffnungen 42 ausgebildet, welche je mit einem Saugventil 41 versehen sind. Entsprechend wird jeweils - während des Saughubes des Kolbens 5 und bei geöffneten Saugventilen 41 - eine Verbindung zwischen dem Kompressionsraum 31 und einem von diesem durch den Kolben 5 getrennten Zylinderraum 43 hergestellt, der an eine nicht dargestellte Zuführleitung für das zu komprimierende Medium, z.B. Erdgas, angeschlossen ist. Die Saugventile 41 sind auf der dem Kompressionsraum 31 zugewandten Seite des Kolbens 5 je in einer Ausnehmung 44 eines am Kolben 5 lösbar befestigten weiteren Führungsteils, darstellungsgemäss einer Halteplatte 45, angeordnet.The pistons 5, 6, 7 and 8, which are guided in cylinder inserts 23, 24, 25 and 26, each define a compression space 31, 32, 33 in the cylinders 1, 2, 3 and 4 which are closed by detachably fastened cylinder covers 27, 28, 29 and 30 or 34. The compression space 31 of the cylinder 1 forming the first compression stage is delimited by an end plate 35 which is inserted into the cylinder head 27 and which is provided with several, for example four through openings 36 arranged offset in the circumferential direction are provided. The passage openings 36, of which only one is visible in FIG. 1, are each provided with a pressure valve 37. The pressure valves 37 are each arranged on the side of the end plate 35 facing away from the piston 5 in a recess 38 of a guide part, according to FIG. 1 of a holding plate 40, which is detachably fastened on the end plate 35. A plurality of passage openings 42 are also formed in the piston 5, each of which is provided with a suction valve 41. Correspondingly - during the suction stroke of the piston 5 and with the suction valves 41 open - a connection is established between the compression space 31 and a cylinder space 43 separated from it by the piston 5, which is connected to a feed line (not shown) for the medium to be compressed, e.g. Natural gas, is connected. The suction valves 41 are arranged on the side of the piston 5 facing the compression space 31, each in a recess 44 of a further guide part detachably fastened to the piston 5, as shown in the illustration of a holding plate 45.

In den Zylindern 2 und 3 sind die Kompressionsräume 32 und 33 je durch eine auf den Zylindereinsatz 24 bzw. 25 aufgesetzte Stirnplatte 46 bzw. 47 begrenzt. Die Stirnplatten 46 und 47 enthalten je eine mit dem Druckventil 37 versehene zentrale Durchtrittsöffnung 36 eine Anzahl, z.B. vier, mit Saugventilen 41 versehene, in Umfangsrichtung gegeneinander versetzte Durchtrittsöffnungen 42, von denen in der Fig. 1 ebenfalls jeweils nur eine sichtbar ist. Die das Druckventil 37 aufnehmende Ausnehmung 38 ist jeweils im Zylinderdeckel 28 bzw. 29 ausgebildet. Die die Saugventile 41 aufnehmenden Ausnehmungen 44 sind jeweils in der der Innenseite der Stirnplatte 46 bzw. 47 zugekehrten Stirnpartie des Zylindereinsatzes 24 bzw. 25 ausgebildet, die als Führungsteil für die Saugventile 41 dient. Die Ausnehmungen 38 sind je durch eine seitliche Oeffnung mit Kompressionsraum 32 bzw. 33 verbunden.In the cylinders 2 and 3, the compression spaces 32 and 33 are each one on the cylinder insert 24 and 25th attached end plate 46 and 47 limited. The end plates 46 and 47 each contain a central through-opening 36 provided with the pressure valve 37, for example four, provided with suction valves 41, circumferentially offset through-openings 42, of which only one is also visible in FIG. 1. The recess 38 receiving the pressure valve 37 is formed in the cylinder cover 28 and 29, respectively. The recesses 44 receiving the suction valves 41 are each formed in the end part of the cylinder insert 24 or 25 facing the inside of the end plate 46 or 47, which serves as a guide part for the suction valves 41. The recesses 38 are each connected to the compression space 32 or 33 by a lateral opening.

Im Zylinder 4 sind sowohl eine mit dem Druckventil 37 versehene Durchtrittsöffnung 36 als auch eine mit dem Saugventil 41 versehene Durchtrittsöffnung 42 im Zylinderdeckel 30 ausgebildet, wobei die das Druckventil 37 aufnehmende Ausnehmung 38 in einem in den Zylinderdeckel 30 einschraubbaren Anschlussnippel 50 einer vom Kompressor wegführenden Druckleitung 51 ausgebildet ist, während die das Saugventil 41 aufnehmende Ausnehmung 44 in einem Nippel 52 ausgebildet ist, der den Kompressionsraum 34 mit einem im Zylinderdeckel 30 ausgebildeten Strömungskanal 58 verbindet.In the cylinder 4, both a passage opening 36 provided with the pressure valve 37 and a passage opening 42 provided with the suction valve 41 are formed in the cylinder cover 30, the recess 38 receiving the pressure valve 37 in a connecting nipple 50 which can be screwed into the cylinder cover 30 of a pressure line leading away from the compressor 51 is formed, while the recess 44 receiving the suction valve 41 is formed in a nipple 52 which connects the compression space 34 to a flow channel 58 formed in the cylinder cover 30.

In der Fig. 1 ist der Kolben 5 in seiner oberen Totpunktlage dargestellt, in der der Kompressionsraum 31 am kleinsten ist. Während des Saughubes des Kolbens 5 wird das dem Zylinderraum 43 zugeführte Gas bei geöffnetem Saugventil 41 durch die Durchtrittsöffnung 42 angesaugt. Während des Druckhubes wird das dabei auf einen Druck von z.B. 5 bar verdichtete Gas bei geöffnetem Druckventil 37 durch die Durchtrittsöffnung 36 in einen Zylinderraum 55 und von diesem über einen die Zylinderdeckel 27 und 28 verbindenden Strömungskanal 56 und einen Ringkanal 48 der durch den Zylinder 2 gebildeten zweiten Verdichtungsstufe zugeführt.1, the piston 5 is shown in its top dead center position, in which the compression space 31 is the smallest. During the suction stroke of the piston 5, the gas supplied to the cylinder space 43 is sucked through the passage opening 42 with the suction valve 41 open. During the pressure stroke, the gas compressed to a pressure of, for example, 5 bar, with the pressure valve 37 open, is passed through the passage opening 36 into a cylinder space 55 and from there via a connecting cylinder cover 27 and 28 Flow channel 56 and an annular channel 48 of the second compression stage formed by the cylinder 2 are supplied.

Das beim Saughub des Kolbens 6 durch die Durchtrittsöffnungen 42 in den Kompressionsraum 32 angesaugte Gas wird beim folgenden Druckhub auf einen Druck von z.B. 20 bar verdichtet und bei geöffnetem Druckventil 37 über einen die Zylinderdeckel 28 und 29 verbindenden Strömungskanal 57 und einen Ringkanal 49 der durch den Zylinder 3 gebildeten dritten Verdichtungsstufe zugeführt.The gas sucked into the compression chamber 32 through the passage openings 42 during the suction stroke of the piston 6 is reduced to a pressure of e.g. Compressed 20 bar and supplied with the pressure valve 37 open via a flow channel 57 connecting the cylinder covers 28 and 29 and an annular channel 49 to the third compression stage formed by the cylinder 3.

In der Fig. 1 ist der Kolben 7 des Zylinders 3 in der unteren Totpunktlage dargestellt, in der der Kompressionsraum 33 am grössten ist. Das beim Saughub des Kolbens 7 in den Kompressionsraum 33 angesaugte Gas wird beim folgenden Druckhub auf einen Druck von z.B. 60 bar verdichtet und über den die Zylinderdeckel 29 und 30 verbindenden Strömungskanal 58 sowie durch im Nippel 52 ausgebildete Verbindungskanäle 59 und 60 der durch den Zylinder 4 gebildeten vierten Verdichtungsstufe zugeführt.In Fig. 1, the piston 7 of the cylinder 3 is shown in the bottom dead center position, in which the compression space 33 is largest. The gas sucked into the compression space 33 during the suction stroke of the piston 7 is reduced to a pressure of e.g. 60 bar compressed and fed via the flow channel 58 connecting the cylinder covers 29 and 30 and through connection channels 59 and 60 formed in the nipple 52 to the fourth compression stage formed by the cylinder 4.

Das beim Saughub des Kolbens 8 in den Kompressionsraum 34 angesaugte Gas wird beim Druckhub auf einen Druck von z.B. 180 bar verdichtet und bei geöffnetem Druckventil 37 über die Druckleitung 51 einem nicht dargestellten Gasbrennstoffbehälter zugeführt, der z.B. als Treibstofftank eines Kraftfahrzeuges ausgebildet sein kann.The gas sucked into the compression space 34 during the suction stroke of the piston 8 is brought to a pressure of e.g. 180 bar compressed and supplied with the pressure valve 37 open via the pressure line 51 to a gas fuel tank, not shown, which e.g. can be designed as a fuel tank of a motor vehicle.

Alle Druckventile 37 und Saugventile 41 sind, abgesehen von allfällig unterschiedlichen Abmessungen der zusammenwirkenden Teile, im wesentlichen gleich ausgebildet. Entsprechend der Darstellung in den Figuren 2, 3 und 4, die das Druckventil 37 des Zylinders 1 zeigen, enthält das Druckventil 37 einen die zugehörige Durchtrittsöffnung 36 vollständig überdeckenden, scheibenförmigen runden Ventilkörper 61 und eine runde Federplatte 62, unter deren Wirkung der Ventilkörper 61 mit einer ebenen Aufsetzfläche lose an einen die Durchtrittsöffnung 36 umgebenden Ventilsitz 63 anliegt. Darstellungsgemäss ist der Ventilsitz 63 unmittelbar an der den Kompressionsraum 31 begrenzenden Stirnplatte 35 ausgebildet. Der Ventilkörper 61 ist an der dem Ventilsitz 63 abgewandten Seite mit einer zentralen Erhebung 64 versehen, die z.B. durch einen zylindrischen Ansatz oder, wie in Fig. 2 dargestellt, durch eine kegelstumpffömige Verdickung des Ventilkörpers 61 gebildet sein kann. An der Erhebung 64 ist eine Auflagefläche 65 für eine zentrale Stützfläche 66 der Federplatte 62 ausgebildet. Die Federplatte 62 ist in der das Druckventil 37 umgebenden Ausnehmung 38 der Halteplatte 40 gegen den Ventilkörper 61 verspannt gehalten, wobei die Ausnehmung 38 mit einem ihren Querschnitt verengenden Absatz 67 ausgeführt ist. Der Absatz 67 ragt in einem ein Abheben des Ventilkörpers 61 zulassenden Abstand von diesem über den Ventilsitz 63 und bildet somit ein Widerlager für die an ihn unter Vorspannung anlegbare Randpartie 71 der Federplatte 62.All pressure valves 37 and suction valves 41 are, apart from any different dimensions of the interacting parts, essentially the same design. According to the illustration in FIGS. 2, 3 and 4, which show the pressure valve 37 of the cylinder 1, the pressure valve 37 contains a disk-shaped round valve body 61 and which completely covers the associated passage opening 36 a round spring plate 62, under the action of which the valve body 61 loosely rests with a flat contact surface against a valve seat 63 surrounding the passage opening 36. As shown, the valve seat 63 is formed directly on the end plate 35 delimiting the compression space 31. The valve body 61 is provided on the side facing away from the valve seat 63 with a central elevation 64, which can be formed, for example, by a cylindrical extension or, as shown in FIG. 2, by a truncated cone-shaped thickening of the valve body 61. A bearing surface 65 for a central supporting surface 66 of the spring plate 62 is formed on the elevation 64. The spring plate 62 is held clamped in the recess 38 of the holding plate 40 surrounding the pressure valve 37 against the valve body 61, the recess 38 being designed with a shoulder 67 narrowing in cross section. The shoulder 67 protrudes at a distance from the valve body 61 which allows the valve body 61 to be lifted off and thus forms an abutment for the edge part 71 of the spring plate 62 which can be biased against it.

Entsprechend der Darstellung in den Figuren 2 und 3 kann die Ausnehmung 38 mit über ihren Umfang verteilt angeordneten örtlichen, nischenartigen Erweiterungen 68 ausgeführt sein, die bei geöffnetem Druckventil 37 eine verlustarme Durchströmung der Ausnehmung 38 durch das aus dem Kompressionsraum 31 austretende Gas gewährleisten. Es versteht sich, dass auch eine andere Anzahl Erweiterungen, oder gegebenenfalls nur eine einzige entsprechende Verbindungsöffnung, vorgesehen sein kann.According to the representation in FIGS. 2 and 3, the recess 38 can be designed with local, niche-like extensions 68 which are distributed over its circumference and which ensure a low-loss flow through the recess 38 through the gas emerging from the compression space 31 when the pressure valve 37 is open. It goes without saying that a different number of extensions, or possibly only a single corresponding connection opening, can also be provided.

Wie insbesondere aus der Fig. 4 hervorgeht, sind in der Federplatte 62 drei über ihre Fläche in Umfangsrichtung gegeneinander versetzte Schlitze 70 ausgebildet, von denen jeder, von einem auf einer kreisringförmigen Randpartie 71 der Federplatte 62 liegenden Bezugspunkt 72 ausgehend, spiralartig im wesentlichen über die vier Quadranten A, B, C und D der Fläche der Federplatte 62 gegen deren zentrale Stützfläche 66 verläuft. Diese Stützfläche 66, welche der Auflagefläche 65 der Erhebung 64 entspricht, ist durch einen zwischen die inneren Enden 73 der drei Schlitze 70 eingeschriebenen, gedachten Kreis bestimmt. Die Schlitze 70 sind dabei so ausgeführt, dass sie, von ihrem jeweiligen Bezugspunkt 72 ausgehend, je einen entlang der Randpartie 71 verlaufenden Anfangsabschnitt E mit im Bereich des ersten Quadranten A gegen den zweiten Quadranten B hin zunehmender und am Anfang des zweiten Quadranten B abnehmender Breite, und einen über den Rest des zweiten Quadranten B und im wesentlichen über den dritten Quadranten C verlaufenden mittleren Abschnitt F mit im wesentlichen konstanter, geringer Breite sowie einen im Bereich des vierten Quadranten D verlaufenden Endabschnitt G mit gegen die Stützfläche 66 hin wieder zunehmender Breite aufweisen.As can be seen in particular from FIG. 4, three slots 70 are formed in the spring plate 62 over their surface in the circumferential direction, each of which, one on an annular edge portion 71 the reference point 72 lying on the spring plate 62, runs spirally essentially over the four quadrants A, B, C and D of the surface of the spring plate 62 against its central support surface 66. This support surface 66, which corresponds to the contact surface 65 of the elevation 64, is determined by an imaginary circle inscribed between the inner ends 73 of the three slots 70. The slots 70 are designed such that, starting from their respective reference point 72, they each have an initial section E running along the edge section 71 with a width increasing in the area of the first quadrant A towards the second quadrant B and decreasing at the beginning of the second quadrant B. , and have a central section F running over the remainder of the second quadrant B and essentially over the third quadrant C with an essentially constant, small width and an end section G running in the area of the fourth quadrant D with a width increasing again towards the support surface 66 .

Der Verlauf der Schlitze 71 ist so gewählt, dass zwischen ihnen Stege 74 verbleiben, welche je mit einer Breite H ausgeführt sind, die, von der Randpartie 71 ausgehend, über die erste Hälfte ihrer Längenerstreckung kontinuierlich geringfügig abnimmt und über die zweite Hälfte ihrer Längenerstreckung gegen die zentrale Stützfläche 66 hin kontinuierlich geringfügig zunimmt. Die Stützfläche 66 kann ohne Oeffnung, und damit, wie die entsprechende Auflagefläche 65 der Erhebung 64, relativ klein ausgeführt sein. Diese Konstruktion ergibt daher, bei optimaler Ausnützung des Materials der Federplatte 62, eine Ausführung mit relativ langen, günstig beanspruchten Stegen 74, die bei kleinem Durchmesser der Federplatte 62 einen relativ grossen Federweg zulassen. Entsprechend wird bei Einhaltung eines minimalen Schadraumes eine maximale Auslenkung der Federplatte 62 erzielt, so dass die baulichen Abmessungen des Kompressors entsprechend klein gehalten werden können.The course of the slots 71 is selected such that webs 74 remain between them, each of which has a width H which, starting from the edge part 71, continuously decreases slightly over the first half of its length and against the second half of its length the central support surface 66 continuously increases slightly. The support surface 66 can be made relatively small without an opening, and thus, like the corresponding contact surface 65 of the elevation 64. This construction therefore results, with optimal use of the material of the spring plate 62, in a design with relatively long, favorably stressed webs 74, which allow a relatively large spring travel with a small diameter of the spring plate 62. Accordingly, a maximum deflection of the spring plate is obtained if a minimum clearance is maintained 62 achieved so that the structural dimensions of the compressor can be kept correspondingly small.

Die erfindungsgemässe Ventilausführung ist insbesondere für kleine, trockenlaufende Kompressoren geeignet, wobei die Ventilkörper 61 und Federplatten 62 z.B. Durchmesser von ca. 10 bis 12 mm aufweisen können. Die Federplatten 62 können aus Federstahl oder einem anderen, für Blattfedern geeigneten Material, wie Titan oder Beryllium, ausgeführt sein und je eine Dicke von 0,1 bis 0,3 mm aufweisen. Es versteht sich, dass auch Ausführungen mit anderen als den beschriebenen Abmessungen möglich sind. Die Ventilkörper 61 können aus Metall oder einem Kunststoff, z.B. Polyätherätherketon (PEEK), bestehen. In Verbindung mit der vorstehend beschriebenen Federplatte 62 kann insbesondere durch die Kunststoffausführung eine kostengünstige, massenund geräuscharme Ventilanordnung erzielt werden, welche jeweils schnell anspricht und welche einen Betrieb mit minimalem Verschleiss und entsprechend langen Standzeiten gewährleistet. Ein optimales Verhältnis zwischen der maximalen Auslenkung und der Federkraft der Federplatte 62 kann bei Ausführungen erzielt werden, bei denen die an der Erhebung 64 ausgebildete Auflagefläche 65 und die zentrale Stützfläche 66 der Federplatte 62 einen Durchmesser aufweisen, der etwa 1/4 bis 1/8 des Durchmessers des Ventilkörpers 61 beträgt.The valve design according to the invention is particularly suitable for small, dry-running compressors, the valve body 61 and spring plates 62 e.g. Can have diameters of about 10 to 12 mm. The spring plates 62 can be made of spring steel or another material suitable for leaf springs, such as titanium or beryllium, and each have a thickness of 0.1 to 0.3 mm. It goes without saying that designs with dimensions other than those described are also possible. The valve bodies 61 can be made of metal or a plastic, e.g. Polyether ether ketone (PEEK). In connection with the spring plate 62 described above, the plastic design, in particular, enables a cost-effective, low-mass and low-noise valve arrangement to be achieved, which responds quickly and which guarantees operation with minimal wear and a correspondingly long service life. An optimal ratio between the maximum deflection and the spring force of the spring plate 62 can be achieved in versions in which the bearing surface 65 formed on the elevation 64 and the central support surface 66 of the spring plate 62 have a diameter which is approximately 1/4 to 1/8 of the diameter of the valve body 61.

Abgewandelte Ausführungsformen können Ventilkörper enthalten, die je mit einer konischen oder linsenförmigen Aufsetzfläche ausgeführt sind und mit entsprechend ausgebildeten Ventilsitzen zusammenwirken. Es ist auch eine Ausführung möglich, bei der der Ventilsitz an einem auswechselbaren Einsetzteil ausgebildet ist.Modified embodiments can contain valve bodies, each of which is designed with a conical or lenticular contact surface and which cooperate with correspondingly designed valve seats. An embodiment is also possible in which the valve seat is formed on an exchangeable insert.

Die Erfindung ist nicht auf die Verwendung an Kompressoren der vorstehend beschriebenen und dargestellten Art beschränkt, sondern ist auch für andere, ein- oder mehrstufige Ausführungen, sowie für andere Anwendungen, z.B. für Leitungen, Atemluftkompressoren, Kompressoren für die Tieftemperaturtechnik oder Kompressoren zum Verdichten von CO₂, Stickstoff und dergleichen Medien geeignet. Die erfindungsgemässe Ventilanordnung ist ebenso für die Verwendung an Pumpen oder Leitungen für flüssige Medien, z.B. Wasser oder Flüssiggas, geeignet.The invention is not limited to use on compressors of the type described and illustrated above, but is also for other, single or multi-stage designs, as well as for other applications, e.g. suitable for pipes, breathing air compressors, compressors for low-temperature technology or compressors for compressing CO₂, nitrogen and similar media. The valve arrangement according to the invention is also suitable for use on pumps or lines for liquid media, e.g. Water or liquid gas, suitable.

Claims (10)

1. A valve arrangement, more particularly for reciprocating compressors, pumps or the like, comprising a component (5, 30, 35, 46, 47) having a passage (36, 42) through which a fluid can flow, and a discoid lid (61) which covers the passage (36, 42) and co-operates with a valve seat (63) extending around said passage and which, together with a resilient element urgeable against it, is disposed for free movement in a recess (38, 44) in a guide part extending around the valve seat (13) at least to some extent, said recess (38, 44) being adapted to have a fluid flow therethrough and being open towards the passage (36, 42), and being formed with inwardly projecting steps (67) at a distance from the valve seat (63) such as to permit lifting of the lid (61), that part (71) of the resilient element which is remote from the lid (67) bearing with prestressing against said steps (67), characterised in that the lid (61) has, on the side remote from the valve seat (63), a central local protuberance (64) and in that the resilient element is formed by a round diaphragm plate (62) urgeable loosely against said protuberance (64), the protuberance (64) having an abutment surface (65) for a central thrust surface (66) of the diaphragm (62).
2. A valve arrangement according to claim 1, characterised in that the valve seat (63) co-operating with the lid (61) is devised directly on the component (5, 30, 35, 46, 47) containing the passage (36, 42).
3. A valve arrangement according to claim 1 or 2, characterised in that the lid (61) is made of plastics, for example, polyether etherketone.
4. A valve arrangement according to any of the previous claims, characterised in that the protuberance (64) of the valve lid (61) is frustum-shaped and in that the abutment surface (65) facing the diaphragm (62) has a diameter of from ¼ to ⅛ of the valve lid diameter.
5. A valve arrargement according to any of the previous claims, characterised in that the diaphragm (62) is made of spring steel and is from 0.1 to 0.3 mm thick.
6. A valve arrangement according to any of the previous claims, characterised in that the diaphragm (62) is formed with three slots (70) and each slot, starting from a reference position (72) on the edge part (71), extends in a spiral substantially over the four quadrants (A, B, C, D) of the surface of the diaphragm (62) towards the central thrust surface (66), the thrust surface (66) which remains between the inner ends (73) of the slots (70) corresponding to the abutment surface (65) on the valve lid protuberance (64).
7. A valve arrangement according to claim 6, characterlsed in that each slot (70) has, starting from the reference position (72): an initial part (E) which extends substantially over a first quadrant (A) with a width increasing towards the second quadrant (B) and decreasing at the start thereof; a central part (F) which extends over the remainder of the second quadrant (B) and over the third quadrant (C) with a reduced and substantially constant width; and a terminal part (G) which extends over the fourth quadrant (D) with a width increasing towards the first quadrant (A).
8. A valve arrangement according to claim 6 or 7, characterised in that the slots (70) bound three webs (74) which extend from the edge part (71) towards the central thrust surface (66) and which, starting from the edge part (71), each have a width (H) decreasing continuously substantlally over the first half of web length and increasing continuously substantially over the second half of web length towards the central thrust surface (66).
9. A valve arrangement according to any of the previous claims, characterised in that the recess (38, 44) receiving the lid (61) and the diaphragm (67) has on its periphery at least one local widering (68) increasing its cross-section.
10. Use of a valve arrangement according to any of the previous claims in a reciprocating compressor for compressing gas, such as natural gas, to be stored as fuel in a motor vehicle.
EP89810419A 1988-06-09 1989-06-05 Valve arrangement Expired - Lifetime EP0346285B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH220988 1988-06-09
CH2209/88 1988-06-09

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EP0346285A1 EP0346285A1 (en) 1989-12-13
EP0346285B1 true EP0346285B1 (en) 1992-04-29

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EP (1) EP0346285B1 (en)
AU (1) AU618605B2 (en)
CA (1) CA1327189C (en)
DE (1) DE58901264D1 (en)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4200838C2 (en) * 1992-01-15 1994-12-22 Knf Neuberger Gmbh Pump with valves controlled by the medium
WO2004022407A1 (en) 2002-09-05 2004-03-18 Quadeltrad, Sl Inner rolling platform for moving a rigid container comprising a positioning receptacle
EP1604114B1 (en) * 2003-03-17 2017-12-13 Arçelik Anonim Sirketi A compressor
US7617826B1 (en) 2004-02-26 2009-11-17 Ameriflo, Inc. Conserver
US8146592B2 (en) * 2004-02-26 2012-04-03 Ameriflo, Inc. Method and apparatus for regulating fluid flow or conserving fluid flow
US7766036B2 (en) * 2004-11-12 2010-08-03 Lg Electronics Inc. Discharge valve and valve assembly of reciprocating compressor having the same
KR20120007527A (en) 2009-05-07 2012-01-20 파커-한니핀 코포레이션 Self-aligning axially constrained regulator valve assembly
KR102240032B1 (en) * 2014-07-21 2021-04-14 엘지전자 주식회사 A linear compressor
KR102233610B1 (en) 2014-07-21 2021-03-30 엘지전자 주식회사 A linear compressor
DE202014009180U1 (en) 2014-11-14 2015-01-14 Technische Universität Ilmenau Pressure gradient-controlled lamellar valve with adjustable stiffness

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1998444A (en) * 1927-12-29 1935-04-23 Sullivan Machinery Co Valve mechanism
GB427276A (en) * 1933-09-12 1935-04-18 British Thomson Houston Co Ltd Improvements in and relating to compressor valves
US2155236A (en) * 1937-09-14 1939-04-18 Westinghouse Air Brake Co Compressor unloading device
US2792790A (en) * 1950-08-07 1957-05-21 Frank R Capps Fluid pump
US2754844A (en) * 1952-07-08 1956-07-17 Durabla Mfg Company Valve
US2800142A (en) * 1954-11-15 1957-07-23 A V Roe Canada Ltd Pressure regulating and check valve
US3664371A (en) * 1970-10-23 1972-05-23 Us Navy Resilient poppet valve
US3911502A (en) * 1974-08-23 1975-10-14 Us Health Composite heart valve poppet
DE2454956A1 (en) * 1974-11-20 1976-05-26 Zlof Dieter Dipl Betriebsw Multi-stage piston compressor - has housing containing piston, piston drive, valve controlled stage connections
AU516210B2 (en) * 1975-12-24 1981-05-21 Commonwealth Scientific And Industrial Research Organisation Vacuum pump
AT351327B (en) * 1976-01-26 1979-07-25 Hoerbiger Ventilwerke Ag CHECK VALVE
US4368755A (en) * 1978-12-20 1983-01-18 Copeland Corporation Valve assembly
JPS5759238U (en) * 1980-09-26 1982-04-07
US4469126A (en) * 1981-11-04 1984-09-04 Copeland Corporation Discharge valve assembly for refrigeration compressors
US4543989A (en) * 1981-11-04 1985-10-01 Copeland Corporation Discharge valve assembly for refrigeration compressors
GB2135430B (en) * 1983-02-22 1986-08-13 Value Company Limited Metallic Valve component

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AU3614389A (en) 1989-12-14
AU618605B2 (en) 1992-01-02
CA1327189C (en) 1994-02-22
US4981421A (en) 1991-01-01
US4936327A (en) 1990-06-26
DE58901264D1 (en) 1992-06-04
EP0346285A1 (en) 1989-12-13

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