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EP2191136B1 - Piston air compressor - Google Patents

Piston air compressor Download PDF

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Publication number
EP2191136B1
EP2191136B1 EP20080773797 EP08773797A EP2191136B1 EP 2191136 B1 EP2191136 B1 EP 2191136B1 EP 20080773797 EP20080773797 EP 20080773797 EP 08773797 A EP08773797 A EP 08773797A EP 2191136 B1 EP2191136 B1 EP 2191136B1
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EP
European Patent Office
Prior art keywords
piston
air
piston compressor
air compressor
cylinder
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.)
Active
Application number
EP20080773797
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German (de)
French (fr)
Other versions
EP2191136A1 (en
Inventor
Heinrich Diekmeyer
Heinrich Schlossarczyk
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.)
ZF CV Systems Hannover GmbH
Original Assignee
Wabco GmbH
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Publication of EP2191136A1 publication Critical patent/EP2191136A1/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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/16—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by adjusting the capacity of dead spaces of working chambers
    • 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
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/08—Actuation of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • F04B49/035—Bypassing
    • 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

Definitions

  • the invention relates to a reciprocating compressor comprising a suction chamber and a separate from the suction chamber Zuschaltraum.
  • piston air compressors are used for example in the form of one-cylinder reciprocating compressors in pneumatic systems of trucks.
  • Such a piston air compressor has a piston running in a cylinder, which compresses air on its way from a bottom dead center to a top dead center, which then exits the piston air compressor as compressed air through a diaphragm valve, which acts as a check valve.
  • the compressed air is passed via a pressure line in an air treatment plant, which dries the compressed air and forwards them via a control valve to consumers, such as a compressed air tank.
  • the piston air compressor is switched to idle.
  • the pressure line remains under pressure.
  • a Zuschaltraum is switched into the one-cylinder piston air compressor.
  • the piston compresses the air in the Zuschaltraum and the compressed air pushes back the piston on its way from top dead center to bottom dead center, so that, apart from flow losses, idle no energy must be expended ,
  • the larger the connection space the smaller the peak pressure that can occur at maximum. If the Zuschaltraum example, just as large as the displacement, so corresponds the peak pressure, when the piston is at the upper top point, is twice the minimum pressure when the piston is at bottom dead center.
  • this air must be passed through the engine of the truck to avoid pollution of the environment with lubricating oil-containing air.
  • lubricating oil-containing air can lead to accelerated aging of the turbocharger.
  • the invention has for its object to provide a piston air compressor, which reduces this problem.
  • the invention solves the problem by a generic piston air compressor or compressor having an air passage from the Zuschaltraum to the suction chamber.
  • An advantage of the invention is that from a pressure chamber of the piston air compressor incoming compressed air can escape during compression by the piston partially into the suction chamber, so that neither in the pressure chamber still in the Zuschaltraum can build up an excessive pressure.
  • An air flow between cylinder and piston along is significantly reduced or prevented.
  • displaced air from the Zuschaltraum can be removed for example in a suction of the engine of the truck. The air thus removed is essentially free of lubricating oil, so that a possibly existing turbocharger is spared.
  • Another advantage of the invention is its easy realizability.
  • the air duct can be easily realized by a hole of suitable size in a partition wall between suction and Zuschaltraum. It is thus advantageously also possible to modify existing piston air compressors later.
  • an air duct means any structure within the piston air compressor which allows air to pass from the connection space into the suction space. Examples are recesses, bores, channels or conduits that can either house or house valves, flaps, diaphragms or the like.
  • the suction chamber is in particular that space through which air is sucked in during a suction process of the piston air compressor.
  • the pressure chamber is in particular the space through which compressed air leaves the piston air compressor.
  • the connection space is, for example, the space through which air flows from one piston to the next piston during idling operation.
  • the suction chamber and / or the Zuschaltraum are formed in a cylinder head of the reciprocating compressor. This results in a particularly easy to manufacture piston air compressor.
  • the Zuschaltraum is separated by a wall of the suction chamber, wherein the air channel is formed in the wall.
  • the air duct can be realized in a particularly simple manner.
  • the air duct is a recess, in particular a hole in the wall.
  • a valve in particular a valve adjustable in its cross-section or its passage pressure or a throttle, can be installed in the air duct.
  • the air duct is preferably selected to be in idle mode the piston air compressor, the pressure in the Zuschaltraum does not increase in the long term. It has been found that often a cross-sectional area of less than 15 mm 2 is sufficient to achieve this requirement. It has also been found that the air duct should preferably have a cross-sectional area of over 0.5 mm 2 . It is particularly favorable when the cross-sectional area for the respective piston air compressor is individually adapted or manually and / or automatically adjustable, for example by means of adjusting screw and / or pressure relief valve.
  • Piston air compressors according to the invention are preferably single-cylinder piston air compressors.
  • the piston air compressor is a two-cylinder piston air compressor or a multi-cylinder piston air compressor.
  • the air duct is preferably provided with a check valve, in particular a ball valve. This check valve blocks an air flow from the suction chamber in the Zuschaltraum.
  • the check valve comprises a membrane, in particular a sheet-metal membrane, which at least in sections has a membrane contour which corresponds to an inner contour of the suction space.
  • the check valve membrane acts as a closing body.
  • the non-return valve membrane attaches to the inner contour of the suction chamber and thus prevents leakage of air out of the suction chamber.
  • FIG. 1 shows a pneumatic system 10 for a truck, not shown, comprising a schematically drawn piston air compressor 12, a pressure line 14, an air conditioning unit 16, a supply line 18 and an electrical control line 20.
  • the piston air compressor 12 sucks in the load operation ambient air through an intake opening 22, compresses them and releases them into the pressure line 14.
  • a predetermined pressure p max is present in the supply line 18, the air treatment unit 16 sends a signal via the electrical control line 20 to the reciprocating compressor 12, whereupon it is switched to idling. In this case, no further air is sucked in and a check valve 24 prevents compressed air from entering the piston pressure compressor 12 from the pressure line 14.
  • FIG. 2 shows a piston air compressor 12 according to the invention, which has a cylinder head 26, a cylinder 28, a piston 30 running in the cylinder 28 and a crank mechanism 32.
  • the piston 30 has piston rings 34 a, 34 b and 34 c and is reciprocated by a connecting rod 36.
  • Within a housing 38 is not shown oil lubrication, which lubricates the piston 30.
  • the housing 38 is connected via a not shown vent line in connection with a suction of an internal combustion engine of the truck.
  • FIG. 3 shows the cylinder head 26, which represents a self-contained inventive subject matter of the present application, in a perspective view.
  • the piston runs on the side facing away from the viewer of the cylinder head.
  • a suction chamber 40 is formed, which is separated by a wall 42 of a Zuschaltraum 44.
  • air flows through the inlet opening 22 (cf. FIG. 2 ) in the suction chamber 40, from the suction chamber 40 in the cylinder 28 and is compressed there by the moving to a top dead center cylinder 30.
  • An in FIG. 3 Concealed suction chamber diaphragm seal prevents the compressed air from flowing back into the suction chamber.
  • the compressed air is forced into a pressure chamber 46 and from there into the pressure line 14 (see. FIG. 1 ).
  • an air channel in the form of a recess 48 is provided in the wall 42, which separates the suction chamber 40 from the Zuschaltraum 44.
  • an air channel in the form of a bore 50 in the wall 42 is provided in the wall 42.
  • FIG. 4a shows an alternative cylinder head 26 according to the invention, which has a two-part Zuschaltraum 44a, 44b and a semi-annular suction chamber 40.
  • the air channel is arranged in the form of a recess 48 which is closed on the suction chamber side of a closing membrane 52, which thus constitutes a closing body.
  • the closing diaphragm 52 is made of spring steel sheet and has a membrane contour which corresponds to an inner contour of the suction chamber 40.
  • FIG. 4b shows the closing membrane 52 in a perspective view. It can be seen that the closing membrane 52 is formed as a bent spring steel sheet.
  • FIG. 5a shows an alternative embodiment of a cylinder head 26 for a single-cylinder piston air compressor according to the invention, in which between the Zuschaltraum 44b and the suction chamber 40, an air channel in the form of a check valve, namely a ball valve 56, is arranged.
  • a check valve namely a ball valve 56
  • FIG. 5b shows the ball valve 56 with a valve ball 58 which is biased by a spring 60 to a valve seat 62.
  • FIG. 6 shows a cylinder head 26 for a two-cylinder piston air compressor according to the invention.
  • a ball valve 56 is arranged between the suction chamber 40 and a Zuschaltraum 44.
  • air passage is formed in which a ball valve 56 is arranged.
  • air can flow from one of the two cylinders through the adjoining space 44 into the respective other cylinder when the piston air compressor is operated at idle, so that the adjoining space simultaneously acts as a connecting channel.
  • FIG. 7 shows a further alternative cylinder head 26 for a piston air compressor according to the invention, in which in the wall 42, which separates the suction chamber 40 from the Zuschaltraum 44, two air channels in the form of recesses 68a, 68b are provided. Also in FIG. 7 The piston of the reciprocating compressor in installation position in the direction behind the cylinder head 26. In the pressure chamber 46, two pressure chamber diaphragm valves 70a, 70b can be seen in this view, which allow an inflow of compressed air from the respective cylinder into the pressure chamber 46 and a return flow prevent.
  • Curve a shows the speed-dependent power consumption of a piston air compressor according to the prior art, in which the compressed air is discharged into the atmosphere at idle.
  • Curve b shows the power consumption for a system according to FIG. 1 with an ideally tight check valve 24 (see. FIG. 1 ) in Govenar mode.
  • Curve c shows the power consumption of a piston air compressor according to FIG.
  • curve d shows the case according to curve c, in which, however, a bore 50 (see. FIG. 3 ) is introduced into the wall 42. It can be seen that the power consumption in this case is significantly lower than in the case without a bore. It can also be seen that approximately the same power consumption can be achieved through the bore as for a piston air compressor with an ideally tight check valve 24.
  • FIG. 9 shows the idleness in idle mode depending on the compressor speed for in FIG. 8 mentioned cases.
  • the difference between the curves c and b shows the positive influence of the air channel in the form of the bore 50 in the wall 42 (see. FIG. 3 ).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Description

Die Erfindung betrifft einen Kolbenverdichter, der einen Saugraum und einen von dem Saugraum getrennten Zuschaltraum umfasst. Derartige Kolbenluftverdichter werden beispielsweise in Form von Ein-Zylinder-Kolbenverdichtern in Pneumatiksystemen von Lastkraftwagen eingesetzt. Ein derartiger Kolbenluftverdichter besitzt einen in einem Zylinder laufenden Kolben, der auf seinem Weg von einem unteren Totpunkt zu einem oberen Totpunkt Luft verdichtet, die dann als Druckluft durch ein Membranventil, das als Rückschlagventil fungiert, aus dem Kolbenluftverdichter austritt. Die Druckluft wird über eine Druckleitung in eine Luftaufbereitungsanlage geleitet, die die Druckluft trocknet und sie über ein Steuerventil an Verbraucher, wie beispielsweise einen Druckluftbehälter, weiterleitet.The invention relates to a reciprocating compressor comprising a suction chamber and a separate from the suction chamber Zuschaltraum. Such piston air compressors are used for example in the form of one-cylinder reciprocating compressors in pneumatic systems of trucks. Such a piston air compressor has a piston running in a cylinder, which compresses air on its way from a bottom dead center to a top dead center, which then exits the piston air compressor as compressed air through a diaphragm valve, which acts as a check valve. The compressed air is passed via a pressure line in an air treatment plant, which dries the compressed air and forwards them via a control valve to consumers, such as a compressed air tank.

Aus der AT 265498B ist ein Kolbenverdichter mit einem Saugraum und einem Zuschaltraum bekannt. Ein Luftaustausch zwischen Zuschaltraum und Saugraum wird hier jedoch durch ein Rückschlagventil verhindert.From the AT 265498B is a reciprocating compressor with a suction chamber and a Zuschaltraum known. However, air exchange between the connection chamber and the suction chamber is prevented here by a check valve.

Aus der DE 4321013A1 ist ein Gasverdichter mit einem Ansaugraum und einem Zusatzraum bekannt. Hierbei besteht allerdings keine direkte Verbindung zwischen dem Ansaugraum und dem Zuschaltraum.From the DE 4321013A1 is a gas compressor with a suction and an additional space known. However, there is no direct connection between the intake and the Zuschaltraum.

Ist der Druckluftbehälter voll befüllt, so wird der Kolbenluftverdichter in einen Leerlauf geschaltet. Dabei bleibt die Druckleitung unter Druck. Gleichzeitig wird ein Zuschaltraum in den Ein-Zylinder-Kolbenluftverdichter zugeschaltet. Bei seinem Weg vom unteren Totpunkt zum oberen Totpunkt komprimiert der Kolben die Luft in dem Zuschaltraum und die komprimierte Luft drückt den Kolben bei seinem Weg vom oberen Totpunkt zum unteren Totpunkt wieder zurück, so dass, von Strömungsverlusten abgesehen, im Leerlauf keine Energie aufgewendet werden muss. Je größer der Zuschaltraum ist, desto kleiner ist der Spitzendruck, der maximal auftreten kann. Ist der Zuschaltraum beispielsweise genau so groß wie der Hubraum, so entspricht der Spitzendruck, wenn der Kolben am oberen Topunkt ist, dem Doppelten des minimalen Drucks, wenn der Kolben am unteren Totpunkt ist.If the compressed air tank is fully filled, the piston air compressor is switched to idle. The pressure line remains under pressure. At the same time a Zuschaltraum is switched into the one-cylinder piston air compressor. On its way from bottom dead center to top dead center, the piston compresses the air in the Zuschaltraum and the compressed air pushes back the piston on its way from top dead center to bottom dead center, so that, apart from flow losses, idle no energy must be expended , The larger the connection space, the smaller the peak pressure that can occur at maximum. If the Zuschaltraum example, just as large as the displacement, so corresponds the peak pressure, when the piston is at the upper top point, is twice the minimum pressure when the piston is at bottom dead center.

Bei Zwei- oder Mehrkolbenverdichtern werden im Leerlauf einzelne Zylinder über einen Zuschaltraum miteinander verbunden, so dass ebenfalls im Wesentlichen keine Energie benötigt wird. Nachteilig an derartigen Kolbenluftverdichtern ist, dass das Membranventil, das als Rückschlagventil einen gewissen Leckagestrom aufweist, der in Litern pro Minute angegeben und auch als Lässigkeit bezeichnet wird. Aufgrund der Lässigkeit kann Druckluft aus der Druckleitung in den Zylinder des Kolbenluftverdichters einströmen. Beim Komprimieren werden so hohe Drücke erreicht. Aufgrund dieser hohen Drücke strömt Druckluft zwischen Zylinder und Kolben vorbei und gelangt so in das Verdichtergehäuse, in dem sich auch die Ölschmierung des Kolbenverdichters befindet. Aus Umweltschutzgründen muss diese Luft durch den Verbrennungsmotor des Lastkraftwagens geführt werden, um eine Belastung der Umwelt mit schmierölhaltiger Luft zu vermeiden. Sofern der Verbrennungsmotor des Lastkraftwagens einen Turbolader besitzt, kann schmierölhaltige Luft jedoch zu einer beschleunigten Alterung des Turboladers führen.In two-piston or multi-piston compressors, individual cylinders are connected to each other via an additional space during idling, so that essentially no energy is required. A disadvantage of such piston air compressors is that the Diaphragm valve, which has a certain leakage flow as a check valve, which is given in liters per minute and also referred to as permeability. Due to the permeability, compressed air from the pressure line can flow into the cylinder of the piston air compressor. When compressing such high pressures are achieved. Due to these high pressures, compressed air flows between cylinder and piston and thus enters the compressor housing, which also houses the oil lubrication of the piston compressor. For environmental reasons, this air must be passed through the engine of the truck to avoid pollution of the environment with lubricating oil-containing air. However, if the engine of the truck has a turbocharger, lubricating oil-containing air can lead to accelerated aging of the turbocharger.

Der Erfindung liegt die Aufgabe zugrunde, einen Kolbenluftverdichter bereitzustellen, der dieses Problem vermindert.The invention has for its object to provide a piston air compressor, which reduces this problem.

Die Erfindung löst das Problem durch einen gattungsgemäßen Kolbenluftverdichter bzw. Kompressor, der einen Luftkanal von dem Zuschaltraum zum Saugraum besitzt.The invention solves the problem by a generic piston air compressor or compressor having an air passage from the Zuschaltraum to the suction chamber.

Vorteilhaft an der Erfindung ist, dass aus einem Druckraum des Kolbenluftverdichters einströmende Druckluft beim Komprimieren durch den Kolben teilweise in den Saugraum entweichen kann, so dass sich weder im Druckraum noch im Zuschaltraum ein übermäßiger Druck aufbauen kann. Ein Luftstrom zwischen Zylinder und Kolben entlang wird dadurch deutlich vermindert oder unterbunden. In den Saugraum verdrängte Luft aus dem Zuschaltraum kann beispielsweise in einen Ansaugbereich des Verbrennungsmotors des Lastkraftwagens abgeführt werden. Die so abgeführte Luft ist im Wesentlichen schmierölfrei, so dass ein möglicherweise vorhandener Turbolader geschont wird.An advantage of the invention is that from a pressure chamber of the piston air compressor incoming compressed air can escape during compression by the piston partially into the suction chamber, so that neither in the pressure chamber still in the Zuschaltraum can build up an excessive pressure. An air flow between cylinder and piston along is significantly reduced or prevented. In the suction chamber displaced air from the Zuschaltraum can be removed for example in a suction of the engine of the truck. The air thus removed is essentially free of lubricating oil, so that a possibly existing turbocharger is spared.

Vorteilhaft an der Erfindung ist zudem deren leichte Realisierbarkeit. So kann der Luftkanal beispielsweise einfach durch eine Bohrung geeigneter Größe in einer Trennwand zwischen Saug- und Zuschaltraum realisiert werden. Es ist dadurch vorteilhafterweise auch möglich, bereits existierende Kolbenluftverdichter nachträglich zu modifizieren.Another advantage of the invention is its easy realizability. For example, the air duct can be easily realized by a hole of suitable size in a partition wall between suction and Zuschaltraum. It is thus advantageously also possible to modify existing piston air compressors later.

Im Rahmen der vorliegenden Beschreibung wird unter einem Luftkanal jede Struktur innerhalb des Kolbenluftverdichters verstanden, die es Luft gestattet, von dem Zuschaltraum in den Saugraum zu gelangen. Beispiele sind Ausnehmungen, Bohrungen, Kanäle oder Leitungen, die alle Ventile, Klappen, Membranen oder ähnliches umfassen oder beherbergen können.In the context of the present description, an air duct means any structure within the piston air compressor which allows air to pass from the connection space into the suction space. Examples are recesses, bores, channels or conduits that can either house or house valves, flaps, diaphragms or the like.

Unter einem Zuschaltraum wird ein schädlicher Raum verstanden, der nicht zum Saugraum oder zum Druckraum gehört. Der Saugraum ist insbesondere derjenige Raum, durch den Luft bei einem Ansaugvorgang des Kolbenluftverdichters eingesaugt wird. Der Druckraum ist insbesondere der Raum, durch den komprimierte Luft den Kolbenluftverdichter verlässt. Bei einem Kolbenluftverdichter mit zwei oder mehr Kolben ist der Zuschaltraum beispielsweise derjenige Raum, durch den Luft im Leer-laufbetrieb von einem Kolben zum nächsten Kolben strömt.Under a Zuschaltraum is a harmful room understood that does not belong to the suction chamber or the pressure chamber. The suction chamber is in particular that space through which air is sucked in during a suction process of the piston air compressor. The pressure chamber is in particular the space through which compressed air leaves the piston air compressor. In a piston-type air compressor with two or more pistons, the connection space is, for example, the space through which air flows from one piston to the next piston during idling operation.

In einer bevorzugten Ausführungsform sind der Saugraum und/oder der Zuschaltraum in einem Zylinderkopf des Kolbenverdichters ausgebildet. Es ergibt sich so ein besonders leicht zu fertigender Kolbenluftverdichter.In a preferred embodiment, the suction chamber and / or the Zuschaltraum are formed in a cylinder head of the reciprocating compressor. This results in a particularly easy to manufacture piston air compressor.

Bevorzugt ist der Zuschaltraum durch eine Wandung von dem Saugraum getrennt, wobei der Luftkanal in der Wandung ausgebildet ist. Auf diese Weise lässt sich der Luftkanal auf besonders einfache Weise realisieren. Besonders bevorzugt ist der Luftkanal eine Ausnehmung, insbesondere eine Bohrung in der Wandung.Preferably, the Zuschaltraum is separated by a wall of the suction chamber, wherein the air channel is formed in the wall. In this way, the air duct can be realized in a particularly simple manner. Particularly preferably, the air duct is a recess, in particular a hole in the wall.

In dem Luftkanal kann zudem ein Ventil, insbesondere ein in seinem Querschnitt oder seinem Durchlassdruck einstellbares Ventil oder eine Drossel eingebaut sein.In addition, a valve, in particular a valve adjustable in its cross-section or its passage pressure or a throttle, can be installed in the air duct.

Für einen gegebenen Kolbenluftverdichter mit einem Rückschlagventil zwischen Zylinder und abgehender Druckleitung, das eine vorgegebene Rückschlagventil-Lässigkeit aufweist, wird der Luftkanal bevorzugt so gewählt, dass im Leerlaufbetrieb des Kolbenluftverdichters der Druck im Zuschaltraum langfristig nicht ansteigt. Es hat sich herausgestellt, dass oft eine Querschnittsfläche von unter 15 mm2 ausreichend ist, um diese Forderung zu erreichen. Es hat sich zudem herausgestellt, dass der Luftkanal bevorzugt eine Querschnittsfläche von über 0,5 mm2 besitzen sollte. Besonders günstig ist, wenn die Querschnittsfläche für den jeweiligen Kolbenluftverdichter individuell angepasst ist oder manuell und/oder automatisch einstellbar ist, beispielsweise mittels Verstellschraube und/oder Druckbegrenzungsventil.For a given piston air compressor with a check valve between cylinder and outgoing pressure line, which has a predetermined non-return valve permeability, the air duct is preferably selected to be in idle mode the piston air compressor, the pressure in the Zuschaltraum does not increase in the long term. It has been found that often a cross-sectional area of less than 15 mm 2 is sufficient to achieve this requirement. It has also been found that the air duct should preferably have a cross-sectional area of over 0.5 mm 2 . It is particularly favorable when the cross-sectional area for the respective piston air compressor is individually adapted or manually and / or automatically adjustable, for example by means of adjusting screw and / or pressure relief valve.

Erfindungsgemäße Kolbenluftverdichter sind bevorzugt Ein-Zylinder-Kolbenluftverdichter. Alternativ ist der Kolbenluftverdichter ein Zwei-Zylinder-Kolbenluftverdichter oder ein Mehr-Zylinder-Kolbenluftverdichter.Piston air compressors according to the invention are preferably single-cylinder piston air compressors. Alternatively, the piston air compressor is a two-cylinder piston air compressor or a multi-cylinder piston air compressor.

Um ein Rückströmen von Luft von dem Saugraum in den Zuschaltraum zu unterbinden, ist der Luftkanal bevorzugt mit einem Rückschlagventil, insbesondere einem Kugelventil, versehen. Dieses Rückschlagventil sperrt einen Luftstrom von dem Saugraum in den Zuschaltraum.In order to prevent a backflow of air from the suction chamber in the Zuschaltraum, the air duct is preferably provided with a check valve, in particular a ball valve. This check valve blocks an air flow from the suction chamber in the Zuschaltraum.

Alternativ oder additiv umfasst das Rückschlagventil eine Membran, insbesondere eine Blechmembran, die zumindest abschnittsweise eine Membrankontur besitzt, die einer Innenkontur des Saugraums entspricht. In diesem Fall fungiert die Rückschlagventil-Membran als Schließkörper. Bei einem Überdruck im Saugraum legt sich die Rückschlagventil-Membran an die Innenkontur des Saugraums und verhindert so ein Ausströmen von Luft aus dem Saugraum hinaus.Alternatively or additionally, the check valve comprises a membrane, in particular a sheet-metal membrane, which at least in sections has a membrane contour which corresponds to an inner contour of the suction space. In this case, the check valve membrane acts as a closing body. At an overpressure in the suction chamber, the non-return valve membrane attaches to the inner contour of the suction chamber and thus prevents leakage of air out of the suction chamber.

Im Folgenden werden Ausführungsformen der Erfindung anhand der beigefügten Zeichnungen näher erläutert. Dabei zeigt

Figur 1
ein erfindungsgemäßes Pneumatiksystem,
Figur 2
einen erfindungsgemäßen Ein-Zylinder-Kolbenluftverdichter in einer Querschnittsansicht,
Figur 3
einen Zylinderkopf des Ein-Zylinder-Kolbenluftverdichters gemäß Figur 2 in einer perspektivischen Ansicht,
Figur 4a
eine alternative Ausführungsform eines Zylinderkopfes eines erfindungsgemäßen Kolbenluftverdichters,
Figur 4b
einen Schließkörper aus dem Zylinderkopf nach Figur 4a,
Figur 5a
eine weitere alternative Ausführungsform eines Zylinderkopfes für einen erfindungsgemäßen Kolbenluftverdichter,
Figur 5b
ein Rückschlagventil des Zylinderkopfes nach Figur 5a,
Figur 6
eine Draufsicht auf einen Zylinderkopf eines erfindungsgemäßen ZweiZylinder-Kolbenluftverdichters und
Figur 7
eine perspektivische Ansicht einer weiteren alternativen Ausführungsform eines Zylinderkopfes eines erfindungsgemäßen Zwei-Zylinder-Kolbenluftverdichters.
Figur 8
zeigt ein Diagramm, das die Leistungsaufnahme verschiedener Kolbenluftverdichter gegen die Kompressordrehzahl aufträgt und
Figur 9
zeigt ein Diagramm, das die Lässigkeit im Leerlaufbetrieb für verschiedene Kolbenluftverdichter, die ihm die Kompressordrehzahl aufträgt.
Embodiments of the invention will be explained in more detail below with reference to the accompanying drawings. It shows
FIG. 1
a pneumatic system according to the invention,
FIG. 2
a single-cylinder piston air compressor according to the invention in a cross-sectional view,
FIG. 3
a cylinder head of the one-cylinder piston air compressor according to FIG. 2 in a perspective view,
FIG. 4a
an alternative embodiment of a cylinder head of a piston air compressor according to the invention,
FIG. 4b
a closing body from the cylinder head to FIG. 4a .
FIG. 5a
a further alternative embodiment of a cylinder head for a piston air compressor according to the invention,
FIG. 5b
a check valve of the cylinder head after FIG. 5a .
FIG. 6
a plan view of a cylinder head of a two-cylinder piston air compressor according to the invention and
FIG. 7
a perspective view of another alternative embodiment of a cylinder head of a two-cylinder piston air compressor according to the invention.
FIG. 8
shows a diagram that plots the power consumption of different piston air compressor against the compressor speed and
FIG. 9
Figure 12 is a graph showing the idling-free operation for various piston air compressors, which plots compressor speed.

Figur 1 zeigt ein pneumatisches System 10 für einen nicht eingezeichneten Lastkraftwagen, das einen schematisch eingezeichneten Kolbenluftverdichter 12, eine Druckleitung 14, eine Luftaufbereitungseinheit 16, eine Versorgungsleitung 18 und eine elektrische Steuerleitung 20 umfasst. FIG. 1 shows a pneumatic system 10 for a truck, not shown, comprising a schematically drawn piston air compressor 12, a pressure line 14, an air conditioning unit 16, a supply line 18 and an electrical control line 20.

Der Kolbenluftverdichter 12 saugt im Lastbetrieb Umgebungsluft durch eine Einsaugöffnung 22 an, komprimiert diese und gibt sie in die Druckleitung 14 ab. Wenn in der Versorgungsleitung 18 ein vorgegebener Druck pmax anliegt, sendet die Luftaufbereitungseinheit 16 über die elektrische Steuerleitung 20 ein Signal an den Kolbenverdichter 12, woraufhin dieser in den Leerlauf geschaltet wird. In diesem Fall wird keine weitere Luft mehr angesaugt und ein Rückschlagventil 24 verhindert, dass Druckluft aus der Druckleitung 14 in den Kolbendruckverdichter 12 gelangt.The piston air compressor 12 sucks in the load operation ambient air through an intake opening 22, compresses them and releases them into the pressure line 14. When a predetermined pressure p max is present in the supply line 18, the air treatment unit 16 sends a signal via the electrical control line 20 to the reciprocating compressor 12, whereupon it is switched to idling. In this case, no further air is sucked in and a check valve 24 prevents compressed air from entering the piston pressure compressor 12 from the pressure line 14.

Figur 2 zeigt einen erfindungsgemäßen Kolbenluftverdichter 12, der einen Zylinderkopf 26, einen Zylinder 28, einen in dem Zylinder 28 laufenden Kolben 30 und einen Kurbeltrieb 32 aufweist. Der Kolben 30 besitzt Kolbenringe 34a, 34b und 34 c und wird von einem Pleuel 36 hin- und herbewegt. Innerhalb eines Gehäuses 38 befindet sich eine nicht eingezeichnete Ölschmierung, die den Kolben 30 schmiert. Das Gehäuse 38 steht über eine nicht eingezeichnete Entlüftungsleitung in Verbindung mit einem Ansaugbereich eines Verbrennungsmotors des Lastkraftwagens. FIG. 2 shows a piston air compressor 12 according to the invention, which has a cylinder head 26, a cylinder 28, a piston 30 running in the cylinder 28 and a crank mechanism 32. The piston 30 has piston rings 34 a, 34 b and 34 c and is reciprocated by a connecting rod 36. Within a housing 38 is not shown oil lubrication, which lubricates the piston 30. The housing 38 is connected via a not shown vent line in connection with a suction of an internal combustion engine of the truck.

Figur 3 zeigt den Zylinderkopf 26, der einen selbständigen erfinderischen Gegenstand der vorliegenden Anmeldung darstellt, in einer perspektivischen Ansicht. Der Kolben läuft auf der dem Betrachter abgewandten Seite des Zylinderkopfes. Im Zylinderkopf 26 ist ein Saugraum 40 ausgebildet, der durch eine Wandung 42 von einem Zuschaltraum 44 getrennt ist. Beim Betrieb des Kolbenluftverdichters strömt Luft durch die Eingangsöffnung 22 (vgl. Figur 2) in den Saugraum 40, vom Saugraum 40 in den Zylinder 28 und wird dort von dem sich auf einen oberen Totpunkt zu bewegenden Zylinder 30 komprimiert. Eine in Figur 3 verdeckte Saugraum-Membrandichtung verhindert, dass die komprimierte Luft in den Saugraum zurückströmen kann. Im Lastbetrieb wird die komprimierte Luft in einen Druckraum 46 gedrückt und gelangt von dort in die Druckleitung 14 (vgl. Figur 1). FIG. 3 shows the cylinder head 26, which represents a self-contained inventive subject matter of the present application, in a perspective view. The piston runs on the side facing away from the viewer of the cylinder head. In the cylinder head 26, a suction chamber 40 is formed, which is separated by a wall 42 of a Zuschaltraum 44. During operation of the piston air compressor, air flows through the inlet opening 22 (cf. FIG. 2 ) in the suction chamber 40, from the suction chamber 40 in the cylinder 28 and is compressed there by the moving to a top dead center cylinder 30. An in FIG. 3 Concealed suction chamber diaphragm seal prevents the compressed air from flowing back into the suction chamber. In load operation, the compressed air is forced into a pressure chamber 46 and from there into the pressure line 14 (see. FIG. 1 ).

Im Leerlauf wird die angesaugte Luft in den Zuschaltraum 44 (Figur 3) gedrückt und strömt von dort in den Zylinder zurück, wenn sich der Kolben vom oberen Totpunkt auf einen unteren Totpunkt zu bewegt. Es liegt eine Governor-Schaltung vor.At idle, the intake air is in the Zuschaltraum 44 ( FIG. 3 ) and flows back into the cylinder from there as the piston moves from top dead center to bottom dead center. There is a governor circuit.

In der Wandung 42, die den Saugraum 40 von dem Zuschaltraum 44 trennt, ist ein Luftkanal in Form einer Ausnehmung 48 vorgesehen. Alternativ oder additiv ist ein Luftkanal in Form einer Bohrung 50 in der Wandung 42 vorgesehen.In the wall 42, which separates the suction chamber 40 from the Zuschaltraum 44, an air channel in the form of a recess 48 is provided. Alternatively or additionally, an air channel in the form of a bore 50 in the wall 42 is provided.

Ist das Rückschlagventil 24 (Figur 1) undicht, so strömt Druckluft aus der Druckleitung 14 in den Druckraum 46 (Figur 3) ein, gelangt dort in den Zylinder 28 (Figur 2) und von dort in den Zuschaltraum 44. Ein Teil dieser überschüssigen Luft wird durch die Ausnehmung 48 bzw. die Bohrung 50 in den Saugraum 40 geleitet und verlässt den Kolbenluftverdichter durch die Eingangsöffnung 22 (Figur 1).Is the check valve 24 ( FIG. 1 ), compressed air flows from the pressure line 14 into the pressure chamber 46 (FIG. FIG. 3 ), enters the cylinder 28 (FIG. FIG. 2 A portion of this excess air is passed through the recess 48 and the bore 50 into the suction chamber 40 and leaves the piston air compressor through the inlet opening 22 (FIG. FIG. 1 ).

Figur 4a zeigt einen alternativen erfindungsgemäßen Zylinderkopf 26, der einen zweiteiligen Zuschaltraum 44a, 44b und einen teilringförmigen Saugraum 40 besitzt. In der Wandung 42 zwischen dem Saugraum 40 und dem Zuschaltraum 44b ist der Luftkanal in Form einer Ausnehmung 48 angeordnet, die saugraumseitig von einer Schließmembran 52 abgeschlossen wird, die damit einen Schließkörper darstellt. Die Schließmembran 52 ist aus Federstahlblech gefertigt und besitzt eine Membrankontur, die einer Innenkontur des Saugraums 40 entspricht. Überschreitet ein Luftdruck p im Zuschaltraum 44b einen vorgegebenen Wert, so überwindet dieser Luftdruck den Widerstand der Schließmembran 52 und Druckluft 54 strömt in den Saugraum 40 ein. FIG. 4a shows an alternative cylinder head 26 according to the invention, which has a two-part Zuschaltraum 44a, 44b and a semi-annular suction chamber 40. In the wall 42 between the suction chamber 40 and the Zuschaltraum 44b, the air channel is arranged in the form of a recess 48 which is closed on the suction chamber side of a closing membrane 52, which thus constitutes a closing body. The closing diaphragm 52 is made of spring steel sheet and has a membrane contour which corresponds to an inner contour of the suction chamber 40. Exceeds an air pressure p in the Zuschaltraum 44 b a predetermined value, so this air pressure overcomes the resistance of the closing membrane 52 and compressed air 54 flows into the suction chamber 40 a.

Figur 4b zeigt die Schließmembran 52 in einer perspektivischen Ansicht. Es ist zu sehen, dass die Schließmembran 52 als ein gebogenes Federstahlblech ausgebildet ist. FIG. 4b shows the closing membrane 52 in a perspective view. It can be seen that the closing membrane 52 is formed as a bent spring steel sheet.

Figur 5a zeigt eine alternative Ausführungsform eines Zylinderkopfes 26 für einen erfindungsgemäßen Ein-Zylinder-Kolbenluftverdichter, bei dem zwischen dem Zuschaltraum 44b und dem Saugraum 40 ein Luftkanal in Form eines Rückschlagventils, nämlich eines Kugelventils 56, angeordnet ist. FIG. 5a shows an alternative embodiment of a cylinder head 26 for a single-cylinder piston air compressor according to the invention, in which between the Zuschaltraum 44b and the suction chamber 40, an air channel in the form of a check valve, namely a ball valve 56, is arranged.

Figur 5b zeigt das Kugelventil 56 mit einer Ventilkugel 58, die über eine Feder 60 auf einen Ventilsitz 62 vorgespannt ist. FIG. 5b shows the ball valve 56 with a valve ball 58 which is biased by a spring 60 to a valve seat 62.

Figur 6 zeigt einen Zylinderkopf 26 für einen erfindungsgemäßen Zwei-Zylinder-Kolbenluftverdichter. Zwischen dem Saugraum 40 und einem Zuschaltraum 44 ist wiederum ein Luftkanal ausgebildet, in dem ein Kugelventil 56 angeordnet ist. Über jeweils zwei Einströmöffnungen 64 bzw. 66 kann Luft aus jeweils einem der beiden Zylinder durch den Zuschaltraum 44 in den jeweils anderen Zylinder strömen, wenn der Kolbenluftverdichter im Leerlauf betrieben wird, so dass der Zuschaltraum gleichzeitig als Verbindungskanal fungiert. FIG. 6 shows a cylinder head 26 for a two-cylinder piston air compressor according to the invention. Between the suction chamber 40 and a Zuschaltraum 44, in turn, an air passage is formed in which a ball valve 56 is arranged. Via two inflow openings 64 and 66, air can flow from one of the two cylinders through the adjoining space 44 into the respective other cylinder when the piston air compressor is operated at idle, so that the adjoining space simultaneously acts as a connecting channel.

Figur 7 zeigt einen weiteren alternativen Zylinderkopf 26 für einen erfindungsgemäßen Kolbenluftverdichter, bei dem in der Wandung 42, die den Saugraum 40 von dem Zuschaltraum 44 trennt, zwei Luftkanäle in Form von Ausnehmungen 68a, 68b vorgesehen sind. Auch in Figur 7 befinden sich die Kolben des Kolbenverdichters in Einbaulage in Blickrichtung hinter dem Zylinderkopf 26. Im Druckraum 46 sind in dieser Ansicht zwei Druckraum-Membranventile 70a, 70b zu erkennen, die ein Einströmen von komprimierter Luft aus dem jeweiligen Zylinder in den Druckraum 46 gestatten und ein Rückströmen verhindern. FIG. 7 shows a further alternative cylinder head 26 for a piston air compressor according to the invention, in which in the wall 42, which separates the suction chamber 40 from the Zuschaltraum 44, two air channels in the form of recesses 68a, 68b are provided. Also in FIG. 7 The piston of the reciprocating compressor in installation position in the direction behind the cylinder head 26. In the pressure chamber 46, two pressure chamber diaphragm valves 70a, 70b can be seen in this view, which allow an inflow of compressed air from the respective cylinder into the pressure chamber 46 and a return flow prevent.

Figur 8 zeigt ein Diagramm, das die Leistungsaufnahme verschiedener Kolbenluftverdichter gegen eine Drehzahl der Kolbenluftverdichter im Leerlauf aufträgt. Es handelt sich in jedem Fall um Ein-Zylinder-Kolbenluftverdichter mit einem Hubraum von Vh = 318 m3. Kurve a zeigt die drehzahlabhängige Leistungsaufnahme eines Kolbenluftverdichters nach dem Stand der Technik, bei dem im Leerlauf die komprimierte Luft in die Atmosphäre abgegeben wird. Kurve b zeigt die Leistungsaufnahme für ein System gemäß Figur 1 mit einem ideal dichten Rückschlagventil 24 (vgl. Figur 1) im Govenar-Modus. Kurve c zeigt die Leistungsaufnahme eines Kolbenluftverdichters gemäß Figur 1, wenn das Rückschlagventil 24 eine Lässigkeit (Leckstromrate) von 25 l/min aufweist und Kurve d zeigt den Fall gemäß Kurve c, bei dem jedoch eine Bohrung 50 (vgl. Figur 3) in die Wandung 42 eingebracht ist. Es ist zu erkennen, dass die Leistungsaufnahme in diesem Fall deutlich geringer ist als im Fall ohne Bohrung. Es ist zudem zu erkennen, dass durch die Bohrung annähernd die gleiche Leistungsaufnahme erreichbar ist wie für einen Kolbenluftverdichter mit einem ideal dichten Rückschlagventil 24. FIG. 8 shows a diagram that plots the power consumption of different piston air compressor against a speed of the piston air compressor at idle. It is in any case a one-cylinder piston air compressor with a displacement of V h = 318 m 3 . Curve a shows the speed-dependent power consumption of a piston air compressor according to the prior art, in which the compressed air is discharged into the atmosphere at idle. Curve b shows the power consumption for a system according to FIG. 1 with an ideally tight check valve 24 (see. FIG. 1 ) in Govenar mode. Curve c shows the power consumption of a piston air compressor according to FIG. 1 when the check valve 24 has a non-permeability (leakage flow rate) of 25 l / min and curve d shows the case according to curve c, in which, however, a bore 50 (see. FIG. 3 ) is introduced into the wall 42. It can be seen that the power consumption in this case is significantly lower than in the case without a bore. It can also be seen that approximately the same power consumption can be achieved through the bore as for a piston air compressor with an ideally tight check valve 24.

Figur 9 zeigt die Lässigkeit im Leerlaufbetrieb in Abhängigkeit von der Kompressordrehzahl für die in Figur 8 genannten Fälle. Der Unterschied zwischen den Kurven c und b zeigt den positiven Einfluss des Luftkanals in Form der Bohrung 50 in der Wandung 42 (vgl. Figur 3). FIG. 9 shows the idleness in idle mode depending on the compressor speed for in FIG. 8 mentioned cases. The difference between the curves c and b shows the positive influence of the air channel in the form of the bore 50 in the wall 42 (see. FIG. 3 ).

Claims (10)

  1. Piston compressor (12) which comprises
    (a) a suction space (40) and
    (b) a connection space (44) which is separate from the suction space (40),
    and has an air channel (48, 50, 56, 68) from the connection space (44) to the suction space (40), characterized in that the connection space (44) is separated from the suction space (40) by a wall (42) and the air channel (48, 50, 56, 68) is formed in the wall (42), and the air channel (48, 50, 56, 68) permitting air to flow from the connection space (44) into the suction space (40).
  2. Piston compressor according to Claim 1, characterized in that the suction space (40) and/or the connection space (44) are/is formed in a cylinder head (26) of the piston compressor.
  3. Piston compressor according to Claim 1 or 2, characterized in that the air channel is a recess (48), in particular a bore (50), in the wall (42).
  4. Piston compressor according to one of the preceding claims, characterized in that the air channel has a cross-sectional area of below 5 mm2.
  5. Piston compressor according to one of the preceding claims, characterized in that the air channel has an adjustable cross-sectional area.
  6. Piston compressor according to one of the preceding claims, characterized in that it is a single-cylinder piston compressor.
  7. Piston compressor according to one of Claims 1 to 6, characterized in that it is a two-cylinder piston compressor.
  8. Piston compressor according to one of the preceding claims, characterized in that the air channel (48, 50, 56, 68) is provided with a non-return valve (24), in particular a ball valve (56).
  9. Piston compressor according to Claim 8, characterized in that the non-return valve (24) comprises a closing diaphragm (52), in particular a sheet-metal closing diaphragm, which has, at least in sections, a diaphragm contour which corresponds at least in sections to an inner contour of the suction space (40).
  10. Commercial vehicle having a pneumatic system (10) which comprises a piston compressor (12) according to one of the preceding claims.
EP20080773797 2007-08-21 2008-07-01 Piston air compressor Active EP2191136B1 (en)

Applications Claiming Priority (2)

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DE200710039476 DE102007039476A1 (en) 2007-08-21 2007-08-21 piston compressor
PCT/EP2008/005372 WO2009024210A1 (en) 2007-08-21 2008-07-01 Piston air compressor

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EP2191136B1 true EP2191136B1 (en) 2013-08-14

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JP2002174471A (en) * 2000-12-07 2002-06-21 Zexel Valeo Climate Control Corp Freezing cycle
US7270145B2 (en) * 2002-08-30 2007-09-18 Haldex Brake Corporation unloading/venting valve having integrated therewith a high-pressure protection valve
WO2004094822A2 (en) * 2003-04-22 2004-11-04 R. Conrader Company Air compressor with inlet control mechanism and automatic inlet control mechanism
US6898934B1 (en) * 2003-11-18 2005-05-31 Daimlerchrysler Corporation External blow off conversion of compressor recirculation valve
JP4787937B2 (en) * 2006-03-01 2011-10-05 株式会社テージーケー Control valve for compressor

Also Published As

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DE102007039476A1 (en) 2009-02-26
CN101680446B (en) 2015-04-01
US9046096B2 (en) 2015-06-02
JP2010537107A (en) 2010-12-02
US20110277625A1 (en) 2011-11-17
WO2009024210A1 (en) 2009-02-26
EP2191136A1 (en) 2010-06-02
CN101680446A (en) 2010-03-24

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