EP2238349B1 - Reciprocating compressor having a valve plate comprising a disk valve - Google Patents

Reciprocating compressor having a valve plate comprising a disk valve Download PDF

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Publication number
EP2238349B1
EP2238349B1 EP09702133A EP09702133A EP2238349B1 EP 2238349 B1 EP2238349 B1 EP 2238349B1 EP 09702133 A EP09702133 A EP 09702133A EP 09702133 A EP09702133 A EP 09702133A EP 2238349 B1 EP2238349 B1 EP 2238349B1
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EP
European Patent Office
Prior art keywords
valve
concave
reciprocating compressor
lamella
piston
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EP09702133A
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German (de)
French (fr)
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EP2238349A2 (en
Inventor
Eduard Gerum
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Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
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Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
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    • 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
    • F04B39/1066—Valve plates
    • 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
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1087—Valve seats

Definitions

  • the present invention relates to a reciprocating compressor for generating compressed air with at least one cylinder in which a movable piston via a crank for compressing sucked ambient air is arranged, wherein a valve plate having at least one flap valve as a pressure valve, a cylinder space cylinder head side limited.
  • the field of application of the present invention extends primarily to the vehicle sector, in which piston compressors are used for compressing ambient air, primarily in the area of compressed-air-operated brake systems.
  • the reciprocating compressors draw their drive energy either directly from the internal combustion engine of the vehicle or are equipped with a separate drive, usually an electric motor.
  • a generic piston compressor DE 19631415 A1 shows a älnlichen compressor.
  • This essentially consists of a compressor housing forming a plurality of cylinders, in which each associated piston is arranged so that it can move in an oscillating manner via a common crank drive.
  • a valve plate is provided which limits the cylinder space on the cylinder head side.
  • the valve plate contains a suction on the intake side designed in the manner of a check valve and also one of the type Non-return valve trained, but oppositely acting pressure valve. In both cases space-saving finned valves are used.
  • Each louver valve has a spring plate consisting of valve lamella, which is tongue-like and is attached at one end to the valve plate. At the opposite end, the valve lamella covers a cylindrical opening through the valve plate, which connects to or from the cylinder space.
  • the valve blades are flat in cross-section and housed sunk in a shallow recess of the valve plate so that they do not protrude beyond the surface of the valve plate. At this recess, a shallow conical funnel connects, which establishes the connection to the cylindrical opening, which opens into the cylinder chamber.
  • the piston At the top dead center of the piston results in the cylinder chamber remaining dead volume, which results from the distance of the piston to the valve plate plus the volume of the cylindrical openings for the lamella valve.
  • the cylindrical openings take up a significant part of the dead volume.
  • the distance from the piston to the valve plate is determined by the thickness of the suction valve, which is usually present next to the pressure valve. Since the suction valve is usually arranged on the underside of a valve plate, ultimately determines the distance between the piston and the suction valve, the dead volume in the cylinder.
  • the disadvantage of the prior art is that the dead volume has a significant influence on the efficiency and the delivery rate of the compressor, that is to say it should be as minimal as possible, ideally zero.
  • the lamella valve has a flat valve lamella in the initial state, which is pressed by the system pressure on the valve plate on this, so that the cylindrical opening is closed in the direction of the cylinder chamber and thus is sealed. If the pressure in the cylinder chamber rises above the system pressure, the valve lamella is lifted off the valve plate and the compressed air is released from the valve Cylinder space promoted in the cylinder head.
  • the dead volume of the pressure hole is inevitable.
  • the valve plate is made relatively thick, resulting in a particularly long-lasting cylindrical breakthrough and thus results in a relatively large dead volume.
  • the invention includes the technical teaching that serving as a pressure valve blade valve on the side facing away from the piston has a machined into the valve plate concave valve seat recess, the contour of which is sealingly adapted to an equally concave valve blade.
  • the advantage of the solution according to the invention lies, in particular, in the fact that, due to the concave valve seat recess, the lamellar valve has a rather flat cylindrical opening in the direction of the cylinder space, which generates correspondingly less dead volume.
  • the present invention concave valve lamella can be made of a deep-drawn sheet metal part. This is fixed in a conventional manner with an attachment point, such as a screw, on the valve plate.
  • the diameter of the cylindrical passage extending in the direction of the cylinder space extends from the bottom region of the concave valve seat recess, ie its vertex, in the direction of the cylinder space, wherein the diameter of the aperture is smaller than the thickness of the valve plate.
  • the concave valve seat recess has a diameter in the edge region which corresponds at least to twice the diameter of the cylindrical opening.
  • the concave valve seat recess should have a diameter in the edge region, which is larger than the edge diameter of the valve lamella.
  • the depth of the concave valve seat recess should correspond at least to the thickness of the valve blade in order to effect a sufficiently large degree of deflection, and thus also an effective minimization of the dead volume.
  • that is the degree of deflection of the valve lamella and the remaining length of the cylindrical aperture can be determined by the strength of the valve blade and the valve plate.
  • valve blade assumes a substantially planar shape in the open state of the louver valve as a result of elastic deformation.
  • the space required for the open state space is significantly lower than in prior art louvered valves.
  • Fig.1 is arranged in the cylinder 1 of a reciprocating compressor, an axially movable piston 2 for compressing sucked ambient air.
  • the intake valve is not shown here, but it is the pressure valve.
  • This is designed in the manner of a lamella valve 3, which is part of a valve plate 4. With the valve plate 4, a cylinder chamber 5 is limited cylinder head side.
  • the lamella valve 3 On the side facing away from the piston 2, the lamella valve 3 has a concave valve seat recess 6 incorporated in the valve plate 4.
  • the cross-sectional contour of the Ventilsitzaus aloneung 6 is adapted to the contour of an equally concave shaped valve blade 7 such that the valve blade 7 with the Ventilsitzausnaturalung 6 form a kind seat valve.
  • the concave-shaped valve blade 7 is a deep-drawn sheet metal part, which is attached to a - not shown here - on the valve plate 4. From the bottom region of the concave Ventilsitzaus principleung 6, a cylindrical opening 8 extends in the direction of the cylinder chamber 5. Because of the concave valve seat recess 6 shortened axial extent of the opening 8, the dead volume, which occupies the piston 2 in the top dead center shown here, minimal.
  • Fig.2 takes the valve blade 7 in the open state of the louver valve 3 in consequence of elastic deformation to an almost flat shape.
  • the compressed air flows during the open state of the louver valve 3 laterally between the edge of the valve blade 7 and the edge region of the concave Ventililsitzaus principleung 6 over, which has a larger diameter in the edge region, as the edge diameter of the valve blade. 7
  • the invention is not limited to the preferred embodiment described above. On the contrary, modifications are conceivable which are included in the scope of protection of the following claims.
  • the principle according to the invention to uncharged compressors.
  • the dead volume can be significantly reduced so that the delivery rate and the power consumption of the reciprocating compressor are correspondingly improved.
  • Analogous to the solution according to the invention for the pressure valve can also be thought of for the suction valve of the valve plate, a flat recess on the underside of the valve plate, so that the suction valve no longer raised rests on the valve plate.
  • the piston bottom shelter can be reduced by the thickness of the valve lamella, including fasteners.

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

Abstract

The invention relates to a reciprocating compressor for generating compressed air, having at least one cylinder (1) in which a piston (2), for compressing ambient air sucked in is disposed, said piston being movable via a crank drive, wherein a valve plate (4) having at least one disk valve (3) as the pressure valve delimits a cylinder chamber (5) on the cylinder head side, wherein the disk valve (3) has a concave valve seat recess (6) incorporated into the valve plate (4) on the side facing away from the piston (2), the contour of said recess being adjusted in a sealing manner to a valve disk (7) likewise shaped in a concave manner.

Description

Die vorliegende Erfindung betrifft einen Kolbenkompressor zur Erzeugung von Druckluft mit mindestens einem Zylinder, in dem ein über einen Kurbeltrieb bewegbarer Kolben zum Komprimieren angesaugter Umgebungsluft angeordnet ist, wobei eine mindestens ein Lamellenventil als Druckventil aufweisende Ventilplatte einen Zylinderraum zylinderkopfseitig begrenzt.The present invention relates to a reciprocating compressor for generating compressed air with at least one cylinder in which a movable piston via a crank for compressing sucked ambient air is arranged, wherein a valve plate having at least one flap valve as a pressure valve, a cylinder space cylinder head side limited.

Das Einsatzgebiet der vorliegenden Erfindung erstreckt sich vornehmlich auf den Fahrzeugbereich, in welchem Kolbenkompressoren zum Komprimieren von Umgebungsluft vornehmlich im Bereich von druckluftbetriebenen Bremssystemen zum Einsatz kommen. Die Kolbenkompressoren beziehen ihre Antriebsenergie entweder direkt vom Verbrennungsmotor des Fahrzeuges oder sind mit einem separaten Antrieb, meist einem Elektromotor, ausgestattet.The field of application of the present invention extends primarily to the vehicle sector, in which piston compressors are used for compressing ambient air, primarily in the area of compressed-air-operated brake systems. The reciprocating compressors draw their drive energy either directly from the internal combustion engine of the vehicle or are equipped with a separate drive, usually an electric motor.

Aus der US 2005/0175494 geht ein gattungsgemäßer Kolbenkompressor hervor DE 19631415 A1 zeigt einen älnlichen Kompressor. Dieser besteht im Wesentlichen aus einem mehrere Zylinder bildenden Kompressorgehäuse, in dem je zugeordnete Kolben über einen gemeinsamen Kurbeltrieb oszillierend bewegbar angeordnet sind. Durch die Arbeitsbewegung der Kolben wird Umgebungsluft angesaugt, innerhalb des Zylinders komprimiert und als Druckluft zur weiteren Verwendung ausgestoßen. Zur Steuerung des Verdichtungszyklus ist eine Ventilplatte vorgesehen, die den Zylinderraum zylinderkopfseitig begrenzt. Die Ventilplatte enthält ansaugseitig ein nach Art eines Rückschlagventils ausgebildetes Ansaugventil sowie ein ebenfalls nach Art eines Rückschlagventils ausgebildetes, jedoch entgegengesetzt wirkendes Druckventil. In beiden Fällen kommen bauraumsparende Lamellenventile zum Einsatz. Jedes Lamellenventil weist eine aus Federblech bestehende Ventillamelle auf, die zungenartig ausgebildet ist und an einem Ende an der Ventilplatte angebracht ist. Mit dem gegenüberliegenden Ende deckt die Ventillamelle einen zylindrischen Durchbruch durch die Ventilplatte ab, welcher die Verbindung von oder zum Zylinderraum herstellt. Die Ventillamellen sind im Querschnitt eben ausgebildet und in einer flachen Ausnehmung der Ventilplatte derartig versenkt untergebracht, dass diese nicht über die Oberfläche der Ventilplatte hervorstehen. An dieser Ausnehmung schließt sich ein flacher konischer Trichter an, der die Verbindung zu dem zylindrischen Durchbruch herstellt, der in den Zylinderraum einmündet.From the US 2005/0175494 goes out a generic piston compressor DE 19631415 A1 shows a älnlichen compressor. This essentially consists of a compressor housing forming a plurality of cylinders, in which each associated piston is arranged so that it can move in an oscillating manner via a common crank drive. By the working movement of the piston ambient air is sucked in, compressed inside the cylinder and ejected as compressed air for further use. To control the compression cycle, a valve plate is provided which limits the cylinder space on the cylinder head side. The valve plate contains a suction on the intake side designed in the manner of a check valve and also one of the type Non-return valve trained, but oppositely acting pressure valve. In both cases space-saving finned valves are used. Each louver valve has a spring plate consisting of valve lamella, which is tongue-like and is attached at one end to the valve plate. At the opposite end, the valve lamella covers a cylindrical opening through the valve plate, which connects to or from the cylinder space. The valve blades are flat in cross-section and housed sunk in a shallow recess of the valve plate so that they do not protrude beyond the surface of the valve plate. At this recess, a shallow conical funnel connects, which establishes the connection to the cylindrical opening, which opens into the cylinder chamber.

Im oberen Todpunkt des Kolbens ergibt sich im Zylinderraum ein verbleibendes Totvolumen, welches sich aus dem Abstand des Kolbens zur Ventilplatte plus dem Volumen der zylindrischen Durchbrüche zum Lamellenventil ergibt. Die zylindrischen Durchbrüche nehmen dabei einen erheblichen Teil des Totvolumens ein. Dabei wird der Abstand vom Kolben zur Ventilplatte aus durch die Dicke des neben dem Druckventil gewöhnlich vorhandenen Saugventil bestimmt. Da das Saugventil meist an der Unterseite einer Ventilplatte angeordnet ist, bestimmt letztlich der Abstand zwischen Kolben und dem Saugventil das Totvolumen im Zylinder.At the top dead center of the piston results in the cylinder chamber remaining dead volume, which results from the distance of the piston to the valve plate plus the volume of the cylindrical openings for the lamella valve. The cylindrical openings take up a significant part of the dead volume. The distance from the piston to the valve plate is determined by the thickness of the suction valve, which is usually present next to the pressure valve. Since the suction valve is usually arranged on the underside of a valve plate, ultimately determines the distance between the piston and the suction valve, the dead volume in the cylinder.

Nachteilig erweist sich beim Stand der Technik, dass das Totvolumen einen maßgeblichen Einfluss auf den Wirkungsgrad und die Förderleistung des Kompressors besitzt, also möglichst minimal, idealerweise Null sein sollte. Aus fertigungstechnischen Gründen ist jedoch ein gewisser Kolbenunterstand unvermeidlich. Das Lamellenventil besitzt eine im Ausgangszustand ebene Ventillamelle, welche durch den Systemdruck über der Ventilplatte auf diese gedrückt wird, so dass der zylindrische Durchbruch in Richtung Zylinderraum verschlossen ist und damit dicht ist. Steigt im Zylinderraum der Druck über dem Systemdruck an, so wird die Ventillamelle von der Ventilplatte abgehoben und die Druckluft wird aus dem Zylinderraum in den Zylinderkopf gefördert. Hierbei ist das Totvolumen der Druckbohrung unvermeidlich. Insbesondere bei Ventilplatten mit Wasserkühlung ist die Ventilplatte relativ dick ausgeführt, woraus sich ein besonders langbauender zylindrischer Durchbruch und damit ein relativ großes Totvolumen ergibt.The disadvantage of the prior art is that the dead volume has a significant influence on the efficiency and the delivery rate of the compressor, that is to say it should be as minimal as possible, ideally zero. For manufacturing reasons, however, a certain piston shelter is inevitable. The lamella valve has a flat valve lamella in the initial state, which is pressed by the system pressure on the valve plate on this, so that the cylindrical opening is closed in the direction of the cylinder chamber and thus is sealed. If the pressure in the cylinder chamber rises above the system pressure, the valve lamella is lifted off the valve plate and the compressed air is released from the valve Cylinder space promoted in the cylinder head. Here, the dead volume of the pressure hole is inevitable. Especially with valve plates with water cooling, the valve plate is made relatively thick, resulting in a particularly long-lasting cylindrical breakthrough and thus results in a relatively large dead volume.

Die vorgenannte erläuterte Problematik kommt insbesondere bei Kolbenkompressoren mit Turboaufladung zum tragen, da die Förderleistung hierbei um einen Faktor 2-3 höher liegt als bei normalen Kolbenkompressoren. Dies bedeutet, dass die zwei bis dreifache Menge Druckluft durch die Druckventil gefördert werden muss. Bleiben die Druckventile unverändert gegenüber einem Kompressor ohne Aufladung, so ergeben sich totvolumenbedingt besonders hohe Verluste. Werden entsprechend der erhöhten Förderleistung sogar zusätzliche Druckventile in die Zylinderplatte integriert, erhöht sich das Totvolumen um den Faktor der zusätzlichen zylindrischen Durchbrüche.The aforementioned problem explained comes especially in piston compressors with turbocharging wear, since the delivery rate here is a factor of 2-3 higher than normal reciprocating compressors. This means that two to three times the amount of compressed air must be pumped through the pressure valve. If the pressure valves remain unchanged with respect to a compressor without charging, dead volume-related results in particularly high losses. If additional pressure valves are integrated into the cylinder plate in accordance with the increased delivery rate, the dead volume increases by the factor of the additional cylindrical breakthroughs.

Es ist daher die Aufgabe der vorliegenden Erfindung, insbesondere für einen aufgeladenen Kolbenkompressor eine hinreichende Anzahl von Druckventilen bei gleichzeitig minimalem Totvolumen bereitzustellen.It is therefore the object of the present invention, in particular for a supercharged piston compressor to provide a sufficient number of pressure valves while minimizing dead volume.

Die Aufgabe wird ausgehend von einem Kolbenkompressor gemäß dem Oberbegriff von Anspruch 1 in Verbindung mit dessen kennzeichnenden Merkmalen gelöst. Die nachfolgenden abhängigen Ansprüche geben vorteilhafte Weiterbildungen der Erfindung wieder.The object is achieved on the basis of a reciprocating compressor according to the preamble of claim 1 in conjunction with its characterizing features. The following dependent claims give advantageous developments of the invention.

Die Erfindung schließt die technische Lehre ein, dass das als Druckventil dienende Lamellenventil auf der dem Kolben abgewandten Seite eine in die Ventilplatte eingearbeitete konkave Ventilsitzausnehmung aufweist, deren Kontur an eine ebenso konkav geformte Ventillamelle dichtend angepasst ist.The invention includes the technical teaching that serving as a pressure valve blade valve on the side facing away from the piston has a machined into the valve plate concave valve seat recess, the contour of which is sealingly adapted to an equally concave valve blade.

Der Vorteil der erfindungsgemäßen Lösung liegt insbesondere darin, dass das Lamellenventil aufgrund der konkaven Ventilsitzausnehmung über einen recht flachen zylindrischen Durchbruch in Richtung Zylinderraum besitzt, der entsprechend wenig Totvolumen erzeugt.The advantage of the solution according to the invention lies, in particular, in the fact that, due to the concave valve seat recess, the lamellar valve has a rather flat cylindrical opening in the direction of the cylinder space, which generates correspondingly less dead volume.

Vorzugsweise kann die erfindungsgemäß konkav geformte Ventillamelle aus einem tief gezogenen Blechteil hergestellt werden. Dieses ist in herkömmlicher Weise mit einem Befestigungspunkt, beispielsweise einer Verschraubung, an der Ventilplatte fixiert.Preferably, the present invention concave valve lamella can be made of a deep-drawn sheet metal part. This is fixed in a conventional manner with an attachment point, such as a screw, on the valve plate.

Der Durchmesser des in Richtung Zylinderraum verlaufenden zylindrischen Durchbruchs erstreckt sich vom Bodenbereich der konkaven Ventilsitzausnehmung, also deren Scheitelpunkt, in Richtung Zylinderraum, wobei der Durchmesser des Durchbruchs kleiner als die Dicke der Ventilplatte ist.The diameter of the cylindrical passage extending in the direction of the cylinder space extends from the bottom region of the concave valve seat recess, ie its vertex, in the direction of the cylinder space, wherein the diameter of the aperture is smaller than the thickness of the valve plate.

Gemäß der Erfindung ist vorgesehen, dass die konkave Ventilsitzausnehmung im Randbereich einen Durchmesser besitzt, der mindestens dem Doppelten des Durchmessers des zylindrischen Durchbruchs entspricht. Durch diese geometrischen Verhältnisse lässt sich eine Ventilsitzausnehmung schaffen, welche den dichtenden Sitz der korrespondierenden Ventillamellen hinreichend unterstützt.According to the invention, it is provided that the concave valve seat recess has a diameter in the edge region which corresponds at least to twice the diameter of the cylindrical opening. By means of these geometric conditions, it is possible to create a valve seat recess which sufficiently supports the sealing seat of the corresponding valve blades.

Damit die Druckluft im geöffneten Zustand des Druckventils ungehindert an der Ventillamelle vorbeiströmen kann, sollte die konkave Ventilsitzausnehmung im Randbereich einen Durchmesser besitzen, der größer als der Randdurchmesser der Ventillamelle ist.Thus, the compressed air in the open state of the pressure valve can freely flow past the valve lamella, the concave valve seat recess should have a diameter in the edge region, which is larger than the edge diameter of the valve lamella.

Als weitere, die Erfindung verbessernde Maßnahme sollte die Tiefe der konkaven Ventilsitzausnehmung mindestens der Dicke der Ventillamelle entsprechen, um einen genügend großen Durchbiegungsgrad, und damit auch eine wirksame Minimierung des Totvolumens zu bewirken. Prinzipiell gilt, dass der Grad der Durchbiegung der Ventillamelle und die verbleibende Länge des zylindrischen Durchbruchs durch die Festigkeit der Ventillamelle sowie der Ventilplatte bestimmt werden.As a further measure improving the invention, the depth of the concave valve seat recess should correspond at least to the thickness of the valve blade in order to effect a sufficiently large degree of deflection, and thus also an effective minimization of the dead volume. In principle, that is the degree of deflection of the valve lamella and the remaining length of the cylindrical aperture can be determined by the strength of the valve blade and the valve plate.

Die Ventillamelle nimmt im geöffneten Zustand des Lamellenventils in Folge elastischer Verformung eine im Wesentlichen ebene Form an. Somit ist der für den geöffneten Zustand erforderliche Bauraum deutlich geringer, als bei Lamellenventilen des Standes der Technik.The valve blade assumes a substantially planar shape in the open state of the louver valve as a result of elastic deformation. Thus, the space required for the open state space is significantly lower than in prior art louvered valves.

Weitere, die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispiels anhand der Figuren näher dargestellt. Es zeigt:

Fig.1
eine schematische Seitenansicht einer Kolben-Zylinder-Anordnung eines Kolbenkompressors mit Lamellenventil im geschlossenen Zustand, und
Fig.2
eine schematische Seitenansicht einer Kolben-Zylinder-Anordnung eines Kolbenkompressors mit Lamellenventil im geöffneten Zustand.
Further, measures improving the invention will be described in more detail below together with the description of a preferred embodiment with reference to FIGS. It shows:
Fig.1
a schematic side view of a piston-cylinder assembly of a reciprocating compressor with vane valve in the closed state, and
Fig.2
a schematic side view of a piston-cylinder assembly of a reciprocating compressor with vane valve in the open state.

Gemäß Fig.1 ist im Zylinder 1 eines Kolbenkompressors ein axial bewegbarer Kolben 2 zum Komprimieren angesaugter Umgebungsluft angeordnet. Aus Vereinfachungsgründen ist hier das Ansaugventil nicht weiter dargestellt, wohl jedoch das Druckventil. Dieses ist nach Art eines Lamellenventils 3 ausgebildet, welches Bestandteil einer Ventilplatte 4 ist. Mit der Ventilplatte 4 wird ein Zylinderraum 5 zylinderkopfseitig begrenzt.According to Fig.1 is arranged in the cylinder 1 of a reciprocating compressor, an axially movable piston 2 for compressing sucked ambient air. For reasons of simplification, the intake valve is not shown here, but it is the pressure valve. This is designed in the manner of a lamella valve 3, which is part of a valve plate 4. With the valve plate 4, a cylinder chamber 5 is limited cylinder head side.

Das Lamellenventil 3 weist auf der dem Kolben 2 abgewandten Seite eine in die Ventilplatte 4 eingearbeitete konkave Ventilsitzausnehmung 6 auf. Die Querschnittskontur der Ventilsitzausnehmung 6 ist an die Kontur einer ebenso konkav geformten Ventillamelle 7 derart angepasst, dass die Ventillamelle 7 mit der Ventilsitzausnehmung 6 eine Art Sitzventil bilden.On the side facing away from the piston 2, the lamella valve 3 has a concave valve seat recess 6 incorporated in the valve plate 4. The cross-sectional contour of the Ventilsitzausnehmung 6 is adapted to the contour of an equally concave shaped valve blade 7 such that the valve blade 7 with the Ventilsitzausnehmung 6 form a kind seat valve.

Die konkav geformte Ventillamelle 7 ist ein tiefgezogenes Blechteil, welches an einer - hier nicht weiter dargestellten Stelle - an der Ventilplatte 4 befestigt ist. Vom Bodenbereich der konkaven Ventilsitzausnehmung 6 erstreckt sich ein zylindrischer Durchbruch 8 in Richtung des Zylinderraums 5. Wegen der in Folge der konkaven Ventilsitzausnehmung 6 verkürzten Axialerstreckung des Durchbruchs 8 wird das Totvolumen, welches der Kolben 2 im hier dargestellten oberen Totpunkt einnimmt, minimal.The concave-shaped valve blade 7 is a deep-drawn sheet metal part, which is attached to a - not shown here - on the valve plate 4. From the bottom region of the concave Ventilsitzausnehmung 6, a cylindrical opening 8 extends in the direction of the cylinder chamber 5. Because of the concave valve seat recess 6 shortened axial extent of the opening 8, the dead volume, which occupies the piston 2 in the top dead center shown here, minimal.

Gemäß Fig.2 nimmt die Ventillamelle 7 im geöffneten Zustand des Lamellenventils 3 in Folge elastischer Verformung eine fast ebene Form an. Die Druckluft strömt während des geöffneten Zustands des Lamellenventils 3 seitlich zwischen dem Rand der Ventillamelle 7 und dem Randbereich der konkaven Ventilsitzausnehmung 6 vorbei, welcher im Randbereich einen größeren Durchmesser besitzt, als der Randdurchmesser der Ventillamelle 7.According to Fig.2 takes the valve blade 7 in the open state of the louver valve 3 in consequence of elastic deformation to an almost flat shape. The compressed air flows during the open state of the louver valve 3 laterally between the edge of the valve blade 7 and the edge region of the concave Ventililsitzausnehmung 6 over, which has a larger diameter in the edge region, as the edge diameter of the valve blade. 7

Die Erfindung ist nicht beschränkt auf das vorstehend beschriebene bevorzugte Ausführungsbeispiel. Es sind vielmehr auch Abwandlungen hiervon denkbar, welche vom Schutzbereich der nachfolgenden Ansprüche mit umfasst sind. So ist es beispielsweise auch möglich, das erfindungsgemäße Prinzip auch bei nicht aufgeladenen Kompressoren, anzuwenden. Auch hier lässt sich damit das Totvolumen deutlich reduzieren, so dass sich die Förderleistung sowie die Leistungsaufnahme des Kolbenkompressors entsprechend verbessert. Analog zur erfindungsgemäßen Lösung für das Druckventil kann auch für das Saugventil der Ventilplatte eine ebene Aussparung an der Unterseite der Ventilplatte angebacht werden, so dass das Saugventil nicht mehr erhaben an der Ventilplatte aufliegt. Damit lässt sich der Kolbenbodenunterstand um die Dicke der Ventillamelle samt Befestigungsmitteln reduzieren.The invention is not limited to the preferred embodiment described above. On the contrary, modifications are conceivable which are included in the scope of protection of the following claims. For example, it is also possible to apply the principle according to the invention to uncharged compressors. Here too, the dead volume can be significantly reduced so that the delivery rate and the power consumption of the reciprocating compressor are correspondingly improved. Analogous to the solution according to the invention for the pressure valve can also be thought of for the suction valve of the valve plate, a flat recess on the underside of the valve plate, so that the suction valve no longer raised rests on the valve plate. Thus, the piston bottom shelter can be reduced by the thickness of the valve lamella, including fasteners.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Zylindercylinder
22
Kolbenpiston
33
Lamellenventilreed valve
44
Ventilplattevalve plate
55
Zylinderraumcylinder space
66
VentilsitzausnehmungVentilsitzausnehmung
77
Ventillamellevalve blade
88th
Durchbruchbreakthrough

Claims (6)

  1. Reciprocating compressor for the generation of compressed air, comprising at least one cylinder (1) in which a piston (2) movable via a driving crank mechanism for compressing ambient air taken in, wherein a valve plate (4) provided with at least one reed valve (3) as compression valve defines a cylinder space (5) on the side of the cylinder head, with said reed valve (3) having a concave valve seat recess (6) worked into said valve plate (4) on the side turned away from said piston (2), whose contour is matched for sealing with a valve lamella (7) having an equal concave shape, characterized in that a cylindrical through-passage (8) extends from the bottom region of said concave valve seat recess (6) towards said cylinder space (5), whose diameter is smaller than the thickness of said valve plate (4), and that said concave valve seat recess (6) presents a diameter in the edge region, which corresponds at least to twice the diameter of said cylindrical through-passage (8).
  2. Reciprocating compressor according to Claim 1,
    characterized in that said valve lamella (7) having a concave shape is made of a deep-drawn metal sheet part.
  3. Reciprocating compressor according to Claim 1,
    characterized in that said concave valve seat recess (6) presents a diameter in its edge region, which is wider than the edge diameter of said valve lamella (7).
  4. Reciprocating compressor according to Claim 3,
    characterized in that in the opened state of said reed valve (3), the out-flowing air flows laterally along between the edge of said valve lamella (7) and said edge region of said concave valve seat recess (6).
  5. Reciprocating compressor according to Claim 1,
    characterized in that the depth of said concave valve seat recess (6) corresponds at least to the thickness of said valve lamella (7).
  6. Reciprocating compressor according to Claim 1,
    characterized in that in the opened state of said reed valve, said valve lamella (7) adopts a planar shape on account of elastic deformation.
EP09702133A 2008-01-17 2009-01-13 Reciprocating compressor having a valve plate comprising a disk valve Not-in-force EP2238349B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008004809A DE102008004809B4 (en) 2008-01-17 2008-01-17 Piston compressor with a valve plate having a lamella valve
PCT/EP2009/000137 WO2009090033A2 (en) 2008-01-17 2009-01-13 Reciprocating compressor having a valve plate comprising a disk valve

Publications (2)

Publication Number Publication Date
EP2238349A2 EP2238349A2 (en) 2010-10-13
EP2238349B1 true EP2238349B1 (en) 2012-03-14

Family

ID=40785810

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09702133A Not-in-force EP2238349B1 (en) 2008-01-17 2009-01-13 Reciprocating compressor having a valve plate comprising a disk valve

Country Status (4)

Country Link
EP (1) EP2238349B1 (en)
AT (1) ATE549514T1 (en)
DE (1) DE102008004809B4 (en)
WO (1) WO2009090033A2 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016223497A1 (en) 2016-11-28 2018-05-30 Volkswagen Aktiengesellschaft Valve unit and compressor with such a valve unit

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1920772U (en) * 1964-04-15 1965-08-05 Erich Becker DIAPHRAGM PUMP.
JPS60122287A (en) * 1983-12-06 1985-06-29 Mitsubishi Electric Corp Discharge valve apparatus of compressor
US5263643A (en) * 1992-12-24 1993-11-23 Therm-O-Disc, Incorporated Thermally responsive relief valve
US5584676A (en) * 1994-10-27 1996-12-17 Tecumseh Products Company Compressor discharge valve having a guided spherical head
DE19631415C2 (en) 1995-08-11 1998-07-09 Knorr Bremse Systeme Valve plate for piston compressors, in particular for the generation of compressed air in motor vehicles
JP3742862B2 (en) * 2003-03-05 2006-02-08 ダイキン工業株式会社 Compressor
JP2005188421A (en) * 2003-12-26 2005-07-14 Daikin Ind Ltd Compressor
AT8188U1 (en) * 2004-11-02 2006-03-15 Acc Austria Gmbh REFRIGERANT COMPRESSOR

Also Published As

Publication number Publication date
WO2009090033A2 (en) 2009-07-23
DE102008004809A1 (en) 2009-07-23
EP2238349A2 (en) 2010-10-13
WO2009090033A3 (en) 2009-09-24
DE102008004809B4 (en) 2011-03-17
ATE549514T1 (en) 2012-03-15

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