EP4004370B1 - Valve device for a reciprocating-piston compressor - Google Patents

Valve device for a reciprocating-piston compressor Download PDF

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Publication number
EP4004370B1
EP4004370B1 EP20743992.8A EP20743992A EP4004370B1 EP 4004370 B1 EP4004370 B1 EP 4004370B1 EP 20743992 A EP20743992 A EP 20743992A EP 4004370 B1 EP4004370 B1 EP 4004370B1
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EP
European Patent Office
Prior art keywords
pressure
relief
stage
reciprocating
flap
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EP20743992.8A
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German (de)
French (fr)
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EP4004370A1 (en
Inventor
Marius BURKAUSKAS
Sven Hensel
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Voith Patent GmbH
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Voith Patent GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B39/08—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
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/125—Cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/16—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

Definitions

  • the invention relates to a reciprocating piston compressor for a compressed air supply system in a motor vehicle, such as a truck, bus or rail vehicle.
  • a reciprocating piston compressor essentially comprises two areas, the cylinder head area in which the valves are arranged, and the crankshaft housing with at least one cylinder that can be moved in a working chamber so that a suction stroke movement and a compression stroke movement are created.
  • the reciprocating piston compressor can be designed as a single-stage or multi-stage, in particular two-stage.
  • the valve device for controlling the air flow is usually assigned to the cylinder head and comprises automatically acting suction valves and pressure valves which are opened and closed by the pressures prevailing in the working chamber due to the stroke movement of the piston.
  • the suction stroke of the piston creates a negative pressure in the working chamber of the respective cylinder, so that the associated suction valve opens and the associated pressure valve closes. Air enters the working chamber of the cylinder or is sucked into the working chamber via the inlet chamber and the inlet channels in the valve carrier plate.
  • the compression stroke of the piston causes an overpressure in the working chamber of the respective cylinder, so that the associated suction valve closes and the associated pressure valve opens, whereby compressed air is pumped from the working chamber of the cylinder via the pressure channel into the subsequent compressed air system.
  • the suction valve is usually designed as a valve lamella, the valve tongue of which is unilaterally located between the The valve tongue is clamped between the cylinder housing and the cylinder head of the reciprocating piston compressor and is guided at its free end with at least one tab in a recess in the cylinder housing.
  • the inlet openings in the valve carrier plate, which connect an intake chamber with the working chamber of the cylinder, can be closed by means of the valve tongue.
  • valve lamella is designed in such a way that at least one outlet opening is cut out in the valve carrier plate, which is arranged between the working chamber of the cylinder and the pressure channel.
  • the pressure valve, via which the outlet opening can be closed, is usually located within the cylinder head area.
  • the reciprocating compressor continues to deliver until the pressure in the main pressure line has reached a predetermined cut-off pressure.
  • the compressor is then switched to idle mode, which reduces the power consumption in idle mode.
  • Such systems are also called relief systems or idle systems.
  • an idle valve that opens automatically as soon as the system pressure is reached and an overflow valve has opened. This eliminates the counterpressure of the compressed air system that keeps the idle valve in a closed position.
  • the open idle valve connects the working chamber with the inlet chamber so that no compression can take place during the compression stroke.
  • One advantage of such a piston compressor is that it switches off automatically when the target filling pressure in the pressure vessel is reached.
  • Another idle valve is, for example, from the EN 10 2013 001 147 A1 known.
  • an idle valve for a relief system is proposed that is held in the closed position by a spring and can optionally be switched to an open position by applying pressure.
  • Such systems are also called “externally controlled systems”.
  • a reciprocating piston compressor which comprises a pivotably mounted discharge valve which is actuated by an actuating piston.
  • a discharge opening is opened between the cylinder chamber and the expansion chamber.
  • the discharge valve is open, the cylinder chamber is enlarged by the volume of the expansion chamber, which reduces the compression pressure and thus the idling losses.
  • the US6,257,838 B1 A reciprocating piston compressor is also disclosed which comprises an expansion chamber in order to reduce the idle losses.
  • the connecting channel is realized via an actuatable sliding lamella.
  • the object of the invention is to propose a relief system by which the energy consumption of a reciprocating compressor can be further reduced.
  • the embodiment according to the invention is a reciprocating piston compressor for a compressed air supply system in a motor vehicle, with a cylinder head in which a relief system is integrated, by means of which a relief channel in a valve carrier plate of the cylinder head, which connects a working chamber of the reciprocating piston compressor with a chamber in the cylinder head, can be switched.
  • the relief system comprises a switching device and a lamella, wherein the lamella is fastened to the valve carrier plate on the working chamber side and is designed such that it can be lifted off the valve carrier plate to open the relief channel, wherein the lifting of the lamella can take place automatically and/or in a controlled manner by means of the relief system.
  • the automatic lifting of the lamella results in an enlarged effective channel cross-section, which reduces the inflow resistance of the air into the working chamber during the suction stroke of the cylinder.
  • the controlled lifting of the slats causes the compressor to be switched to idle mode, where no compression takes place.
  • a preferred embodiment can provide that the cylinder head has an inlet chamber which can be connected to the working chamber via a plurality of inlet channels in the valve carrier plate and an automatically acting inlet valve lamella designed as a reed valve, wherein the at least one relief channel is arranged within the inlet channels.
  • the at least one relief channel is surrounded by inlet channels.
  • the lamella can preferably be designed as a tongue valve, whereby a tongue valve is understood to be a lamella which is clamped on one side and closes a channel in the unactuated position and opens the passage through the channel in the actuated position.
  • the inlet chamber can be connected to the working chamber via the inlet channels and the relief channel.
  • the inlet chamber is connected to an air inlet through which ambient air in particular enters the inlet chamber.
  • the air is distributed between the inlet channels and the at least one relief channel and is sucked into the working chamber via these.
  • the enlarged cross-section facilitates the suction stroke movement of the piston, which reduces energy consumption.
  • the relief system for supporting the lamella can include a means for limiting the stroke of the lamella.
  • a means for limiting the stroke of the lamella In particular, with large volumes of air that are sucked into the working chamber during the suction stroke due to the resulting negative pressure, it may be necessary to limit the movement of the lamella, as is also necessary for the valve lamella according to the StdT.
  • a limiting lamella that protrudes into the working chamber can be used.
  • the cylinder can have a corresponding recess for the limiting lamella. Alternatively, this recess can also be used directly as a means of limitation, so that the lamella hits the recess at least at the start of the stroke movement.
  • the relief system can comprise a relief piston that can be reset by means of a spring element and can be actuated by means of a control pressure.
  • the reciprocating piston compressor can be designed as a two-stage compressor, with a pre-stage and a high-pressure stage, whereby a relief system and a connecting channel that connects the relief channel of the high-pressure stage to the inlet chamber are provided in the cylinder head for each stage.
  • the compression stroke of all stages is relieved via a connection that connects the respective working chamber to the inlet chamber via the relief channel. In this way, when the lamella is in the relief position, ambient air can also enter the working chamber directly during the suction stroke of the high-pressure stage.
  • the lamella of the relief system of the high-pressure stage is designed in such a way that it remains in the closed position during operation during the suction stroke.
  • the lamella of the high-pressure stage or subsequent High pressure stages are designed in such a way that the slat can only be actively moved into the open position by means of the piston of the relief system.
  • the method is characterized in that during a suction stroke, in which a negative pressure is generated in the working chamber, a lamella of the relief system is moved automatically or, when the relief system is activated, forcibly into an open position, so that additional air is sucked into the working chamber via the inlet chamber and the relief channel, or when the relief system is activated, air can be pushed out of the working chamber via the relief channel.
  • This method is used in a single-stage reciprocating piston compressor or the preliminary stage or the first stage of a multi-stage reciprocating piston compressor.
  • a pre-stage and a high-pressure stage are connected in series, with a relief system provided in the cylinder head for each stage.
  • the lamella of the pre-stage is automatically moved into the open position during the suction stroke and the lamella of the high-pressure stage can be designed in such a way that it remains in the closed position during the suction stroke.
  • a connecting channel for connecting the relief systems can be provided in the cylinder head of the two-stage compressor, whereby the relief channel of the high-pressure stage is connected via the connecting channel to the inlet chamber of the pre-stage, whereby for the relief or switching to idle operation of the reciprocating piston compressor, the relief pistons of both Relief systems are switched in such a way that the slats of both stages are moved to an open position.
  • Figure 1 shows a piston-side view of the valve carrier plate 4 of a two-stage reciprocating piston compressor with the relief system assigned to the cylinder head 12.
  • the two compressor stages, the pre-stage 2 and the high-pressure stage 3 are similarly constructed but differ slightly in size and function.
  • the basic structure is the same.
  • Both compressor stages have an inlet valve 5a, b that is fixed on one side and has stop surfaces on the opposite side.
  • Recesses (not shown here) are provided in the crankshaft housing 11 for the stop surfaces, through which the opening movement of the inlet valves 5a, b is limited.
  • the outlet channels 23 are arranged within the outer contour of the inlet valves 5a, b and partially run through recesses in the inlet valves 5a, b.
  • the slats 9a, b belonging to the relief system 7a, b are arranged approximately in the middle of the intake valves 5a, b, i.e. approximately in the middle of the working chamber of the cylinders 20a, b, where the intake valves 5a, b have a recess.
  • the slats 9a, b are also clamped on one side.
  • the valves of the pre-stage 2 and the high-pressure stage 3 differ slightly. Due to the larger air volume that is sucked in during the suction stroke of the cylinder 20a of the pre-stage 2 must be opened, the lamella 9a is designed in such a way that the valve opens automatically with each suction stroke of the cylinder 20a of the preliminary stage 2. To limit the opening movement, a limiting lamella 22 is provided, which represents a stop for the lamella 9a.
  • FIG. 2 shows a cylinder head side view of the valve carrier plate 4 of a two-stage reciprocating piston compressor with relief system.
  • Both stages 2, 3 each have an inlet chamber 14a, b and an outlet chamber 15a, b.
  • the automatically acting outlet valves 6a, b are arranged in the outlet chambers, which close the outlet channels 23 in the valve carrier plate in the closed position and are moved to an open position when a definable pressure in the working chamber is exceeded.
  • the valve carrier plate 4 In the area of the inlet chamber 14a of the pre-stage 2, several channel openings are represented by the valve carrier plate 4. Part of the openings, the outer semicircle, are the inlet channels 21a, which are assigned to the inlet valve 5a with the inlet valve lamella 18a. During a suction stroke, the air is sucked into the working chamber through the inlet channels 21a, and the inlet valve lamella 18a is moved into an open position. During a compression stroke, the inlet valve lamella 18a closes the inlet channels 21a. The relief channels 19a are arranged within the semicircle of the inlet channels 21a. Their passage is switched by means of the lamella 9a of the relief system 7a.
  • the high-pressure stage is designed somewhat differently; here the relief channel 19b of the relief system 7b is arranged in a separate chamber, which is connected to the inlet chamber 14a of the pre-stage 2 via the connecting channel 13. Not shown is the separate channel connection between the outlet chamber 15a of the pre-stage 2 and the inlet chamber 14b of the high-pressure stage 3.
  • Figure 3 and 4 show the relief systems 7a, b of the pre-stage 2 and the high-pressure stage 3 in section.
  • the general layered structure of the cylinder head 12 is known from the prior art, so that only the channels and chambers essential to the invention will be considered further here.
  • the relief system 7a according to the invention for the pre-stage is shown in Figure 3 and the relief system 7b for the high pressure stage 3 is in Figure 4 shown.
  • the relief system 7a of the pre-stage can be designed as described above and in Figure 3 shown.
  • all stages following the preliminary stage receive the relief system 7b of the high-pressure stage 2, whereby in a preferred embodiment a connecting channel can be provided via which all stages can be connected to the inlet chamber of the preliminary stage.
  • each stage can also comprise a separate channel that is connected to the environment.
  • the special feature of the relief valve of the pre-stage 2 is the limiting lamella 22, which is designed as a solid component and supports the lamella 9a so that the lamella 9a does not bend too far into the working area and thus does not result in excessive bending stress.
  • the cylinder 20a has a recess on the front face into which the limiting lamella 22 dips when the cylinder is at top dead center, so that the dead space is as small as possible.
  • the recess is just large enough to accommodate the limiting slat 22 and the slat 9a lying on it in the open state.
  • the relief piston 10a can also be seen, which is guided in the cylinder head 12. In the position shown, this is in the rest position and is held in this position by a spring.
  • the relief piston 10a can be pressurized via the control pressure channel 16 shown, so that it is moved into the relief position and the lamella 9a into the open position.
  • the special feature of the Figure 4 The design of the lamella 9b shown in the relief system 8b of the high pressure stage 3 is such that it is spring-stiff that it can only be moved into the open position with the help of the relief piston 10b. A suction stroke of the piston 20b of the high-pressure stage 2 does not cause the lamella 9b to move automatically into the open position. Both relief pistons 10a, b are simultaneously pressurized with compressed air via the control pressure channel 16 shown.
  • the piston 20b also has a recess in which the lamella 9b fits in the open position.

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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 Hubkolbenkompressor für ein Druckluftversorgungsystem in einem Kraftfahrzeug, wie einem LKW, Bus oder Schienenfahrzeug. Ein Hubkolbenverdichter umfasst im Wesentlichen zwei Bereiche, den Zylinderkopfbereich, in dem die Ventile angeordnet sind, und das Kurbelwellengehäuse mit zumindest einem Zylinder, der in einem Arbeitsraum bewegbar ist, so dass eine Saughubbewegung und eine Kompressionshubbewegung entsteht. Der Hubkolbenverdichter kann einstufig oder mehrstufig, insbesondere zweistufig, ausgeführt sein.The invention relates to a reciprocating piston compressor for a compressed air supply system in a motor vehicle, such as a truck, bus or rail vehicle. A reciprocating piston compressor essentially comprises two areas, the cylinder head area in which the valves are arranged, and the crankshaft housing with at least one cylinder that can be moved in a working chamber so that a suction stroke movement and a compression stroke movement are created. The reciprocating piston compressor can be designed as a single-stage or multi-stage, in particular two-stage.

Die Ventilvorrichtung zur Steuerung des Luftstroms ist üblicherweise dem Zylinderkopf zugeordnet und umfasst selbsttätig wirksame Saugventile und Druckventile, die durch die in dem Arbeitsraum durch die Hubbewegung des Kolbens herrschenden Drücke geöffnet und geschlossen werden.The valve device for controlling the air flow is usually assigned to the cylinder head and comprises automatically acting suction valves and pressure valves which are opened and closed by the pressures prevailing in the working chamber due to the stroke movement of the piston.

Der Saughub des Kolbens bewirkt einen Unterdruck im Arbeitsraum des jeweiligen Zylinders, so dass sich das zugeordnete Saugventil öffnet und das zugeordnete Druckventil geschlossen wird. Über die Einlasskammer und die Einlasskanäle in der Ventilträgerplatte gelangt Luft in den Arbeitsraum des Zylinders, bzw. wird in den Arbeitsraum gesaugt.The suction stroke of the piston creates a negative pressure in the working chamber of the respective cylinder, so that the associated suction valve opens and the associated pressure valve closes. Air enters the working chamber of the cylinder or is sucked into the working chamber via the inlet chamber and the inlet channels in the valve carrier plate.

Der Verdichtungshub des Kolbens bewirkt einen Überdruck im Arbeitsraum des jeweiligen Zylinders, so dass sich das zugeordnete Saugventil schließt und das zugeordnete Druckventil geöffnet wird, wodurch komprimierte Luft aus dem Arbeitsraum des Zylinders über den Druckkanal in das nachfolgende Druckluftsystem gefördert wird.The compression stroke of the piston causes an overpressure in the working chamber of the respective cylinder, so that the associated suction valve closes and the associated pressure valve opens, whereby compressed air is pumped from the working chamber of the cylinder via the pressure channel into the subsequent compressed air system.

Wie auch aus der DE 10 2016 006 358 A1 bekannt, ist das Saugventil meistens als Ventillamelle ausgebildet, dessen Ventilzunge einseitig zwischen dem Zylindergehäuse und dem Zylinderkopf des Hubkolbenkompressors eingespannt ist und an ihrem freien Ende mit mindestens einer Lasche in einer Aussparung des Zylindergehäuses geführt ist. Mittels der Ventilzunge sind die Eintrittsöffnungen in der Ventilträgerplatte, die eine Ansaugkammer mit dem Arbeitsraum des Zylinders verbinden, verschließbar.As also from the EN 10 2016 006 358 A1 As is known, the suction valve is usually designed as a valve lamella, the valve tongue of which is unilaterally located between the The valve tongue is clamped between the cylinder housing and the cylinder head of the reciprocating piston compressor and is guided at its free end with at least one tab in a recess in the cylinder housing. The inlet openings in the valve carrier plate, which connect an intake chamber with the working chamber of the cylinder, can be closed by means of the valve tongue.

Weiterhin ist die Ventillamelle derart gestaltet, dass zumindest eine Austrittsöffnung in der Ventilträgerplatte ausgespart wird, die zwischen dem Arbeitsraum des Zylinders und dem Druckkanal angeordnet ist. Das Druckventil, über das die Austrittsöffnung verschließbar ist, befindet sich üblicherweise innerhalb des Zylinderkopfbereichs.Furthermore, the valve lamella is designed in such a way that at least one outlet opening is cut out in the valve carrier plate, which is arranged between the working chamber of the cylinder and the pressure channel. The pressure valve, via which the outlet opening can be closed, is usually located within the cylinder head area.

Der Förderbetrieb des Hubkolbenkompressors erfolgt so lange, bis der Druck in der Hauptdruckleitung einen vorgegebenen Abschaltdruck erreicht hat. Dann wird der Kompressor in den Leerlaufbetrieb geschaltet, durch den die Leistungsaufnahme im Leerlaufbetrieb reduziert wird. Derartige Systeme nennt man auch Entlastungssysteme oder Leerlaufsysteme.The reciprocating compressor continues to deliver until the pressure in the main pressure line has reached a predetermined cut-off pressure. The compressor is then switched to idle mode, which reduces the power consumption in idle mode. Such systems are also called relief systems or idle systems.

Aus der EP 1 650 434 A2 ist beispielsweise ein Leerlaufventil bekannt, dass sich automatisch öffnet, sobald der Systemdruck erreicht ist und sich ein Überströmventil geöffnet hat. Dadurch entfällt der Gegendruck des Druckluftsystems, der das Leerlaufventil in einer Schließstellung hält. Das geöffnete Leerlaufventil verbindet den Arbeitsraum mit der Einlasskammer, so dass keine Verdichtung während des Verdichtungshubs stattfinden kann. Ein Vorteil eines solchen Kolbenverdichters besteht darin, dass das Abschalten bei Erreichen des Soll-Fülldruckes im Druckbehälter automatisch erfolgt.From the EP 1 650 434 A2 For example, an idle valve is known that opens automatically as soon as the system pressure is reached and an overflow valve has opened. This eliminates the counterpressure of the compressed air system that keeps the idle valve in a closed position. The open idle valve connects the working chamber with the inlet chamber so that no compression can take place during the compression stroke. One advantage of such a piston compressor is that it switches off automatically when the target filling pressure in the pressure vessel is reached.

Ein weiteres Leerlaufventil ist beispielsweise aus der DE 10 2013 001 147 A1 bekannt. Hier wird ein Leerlaufventil für ein Entlastungssystem vorgeschlagen, dass mittels einer Feder in der Schließstellung gehalten wird und wahlweise durch Aufbringen eines Druckes in eine Offenstellung geschaltet werden kann. Derartige Systeme werden auch "fremdgesteuerte-Systeme" genannt.Another idle valve is, for example, from the EN 10 2013 001 147 A1 known. Here, an idle valve for a relief system is proposed that is held in the closed position by a spring and can optionally be switched to an open position by applying pressure. Such systems are also called "externally controlled systems".

Aus der EP 0091 994 ist eine Leerlauf-Ventileinrichtung bekannt. Diese ist derart angeordnet, dass sie nicht in den Kolben des Verdichters überfahrenden Bereich ragt.From the EP0091994 An idle valve device is known. This is arranged in such a way that it does not protrude into the area where the piston of the compressor travels.

Alle Leerlaufsysteme haben gemeinsam, dass im Leerlaufbetrieb der Arbeitsraum über einen Entlastungskanal mit einem weiteren Raum verbunden wird, so dass keine oder eine verringerte Kompression stattfindet.What all idle systems have in common is that during idle operation the working chamber is connected to another chamber via a relief channel, so that no or reduced compression takes place.

Aus der WO 95/11384 A1 ist ein Hubkolbenverdichter offenbart, der ein schwenkbar gelagertes Entladeventil umfasst, das von einem Betätigungskolben betätigt wird. Bei geöffnetem Entladeventil wird eine Entladeöffnung zwischen dem Zylinderraum und der Expansionskammer freigegeben. Bei geöffnetem Entladeventil wird der Zylinderraum um das Volumen der Expansionskammer vergrößert, was den Kompressionsdruck und damit die Leerlaufverluste verringert.From the WO95/11384 A1 discloses a reciprocating piston compressor which comprises a pivotably mounted discharge valve which is actuated by an actuating piston. When the discharge valve is open, a discharge opening is opened between the cylinder chamber and the expansion chamber. When the discharge valve is open, the cylinder chamber is enlarged by the volume of the expansion chamber, which reduces the compression pressure and thus the idling losses.

Die US 6,257,838 B1 ist auch ein Hubkolbenverdichter offenbart, der eine Expansionskammer umfasst, um die Leerlaufverluste zu reduzieren. Der Verbindungskanal wird über eine betätigbare Schiebelamelle realisiert.The US6,257,838 B1 A reciprocating piston compressor is also disclosed which comprises an expansion chamber in order to reduce the idle losses. The connecting channel is realized via an actuatable sliding lamella.

Die Aufgabe der Erfindung ist es, ein Entlastungssystem vorzuschlagen, durch das sich der Energieverbrauch eines Hubkolbenverdichters weiter reduzieren lässt.The object of the invention is to propose a relief system by which the energy consumption of a reciprocating compressor can be further reduced.

Die Aufgabe wird erfindungsgemäß durch eine Ausführung entsprechend Anspruch 1 gelöst. Weitere vorteilhafte Merkmale der erfindungsgemäßen Ausführung finden sich in den Unteransprüchen.The object is achieved according to the invention by an embodiment according to claim 1. Further advantageous features of the embodiment according to the invention can be found in the subclaims.

Bei der erfindungsgemäßen Ausführung handelt es sich um einen Hubkolbenkompressor für ein Druckluftversorgungsystem in einem Kraftfahrzeug, mit einem Zylinderkopf in dem ein Entlastungssystem integriert ist, mittels dem ein Entlastungskanal in einer Ventilträgerplatte des Zylinderkopfes, der einen Arbeitsraum des Hubkolbenkompressors mit einem Raum im Zylinderkopf verbindet, schaltbar ist.The embodiment according to the invention is a reciprocating piston compressor for a compressed air supply system in a motor vehicle, with a cylinder head in which a relief system is integrated, by means of which a relief channel in a valve carrier plate of the cylinder head, which connects a working chamber of the reciprocating piston compressor with a chamber in the cylinder head, can be switched.

Zur Verbesserung der Effizienz des Hubkolbenkompressors wird vorgeschlagen, dass das Entlastungssystem eine Schaltvorrichtung und eine Lamelle umfasst, wobei die Lamelle arbeitsraumseitig an der Ventilträgerplatte befestigt ist und derart ausgelegt ist, das diese zum Öffnen des Entlastungskanals von der Ventilträgerplatte abhebbar ist, wobei das Abheben des Lamelle selbsttätig und/oder gesteuert mittels des Entlastungssystems erfolgen kann.In order to improve the efficiency of the reciprocating piston compressor, it is proposed that the relief system comprises a switching device and a lamella, wherein the lamella is fastened to the valve carrier plate on the working chamber side and is designed such that it can be lifted off the valve carrier plate to open the relief channel, wherein the lifting of the lamella can take place automatically and/or in a controlled manner by means of the relief system.

Durch das selbsttätige Abheben der Lamelle wird erreicht, dass ein vergrößerter wirksamer Kanalquerschnitt entsteht, durch den der Einströmwiderstand der Luft in den Arbeitsraum beim Saughub des Zylinders reduziert wird.The automatic lifting of the lamella results in an enlarged effective channel cross-section, which reduces the inflow resistance of the air into the working chamber during the suction stroke of the cylinder.

Durch das gesteuerte Abheben der Lamelle wird erreicht, dass der Kompressor in den Leerlaufbetrieb geschaltet wird, bei der keine Kompression stattfindet.The controlled lifting of the slats causes the compressor to be switched to idle mode, where no compression takes place.

Eine bevorzugte Ausführungsform kann vorsehen, dass der Zylinderkopf eine Einlasskammer aufweist, welche über mehrere Einlasskanäle in der Ventilträgerplatte und einer selbsttätig wirksamen als Zungenventil ausgebildete, Einlassventillamelle mit dem Arbeitsraum verbindbar ist, wobei der mindestens eine Entlastungskanal innerhalb der Einlasskanäle angeordnet ist. Mit anderen Worten, dass der mindestens eine Entlastungskanal von Einlasskanälen umgeben ist.A preferred embodiment can provide that the cylinder head has an inlet chamber which can be connected to the working chamber via a plurality of inlet channels in the valve carrier plate and an automatically acting inlet valve lamella designed as a reed valve, wherein the at least one relief channel is arranged within the inlet channels. In other words, the at least one relief channel is surrounded by inlet channels.

Die Lamelle kann dabei vorzugsweise als Zungenventil ausgeführt sein, wobei man unter einem Zungenventil eine Lamelle versteht, die einseitig eingespannt ist und in der unbetätigten Stellung einen Kanal verschließt und in der betätigten Stellung den Durchgang durch den Kanal öffnet.The lamella can preferably be designed as a tongue valve, whereby a tongue valve is understood to be a lamella which is clamped on one side and closes a channel in the unactuated position and opens the passage through the channel in the actuated position.

Die Einlasskammer ist über die Einlasskanäle und den Entlastungskanal mit dem Arbeitsraum verbindbar. Die Einlasskammer ist mit einem Lufteinlass verbunden, durch den insbesondere Umgebungsluft in die Einlasskammer gelangt. In der Einlasskammer verteilt sich die Luft auf die Einlasskanäle und den mindestens einen Entlastungskanal und wird über diese in den Arbeitsraum gesaugt. Durch den vergrößerten Querschnitt wird die Saughubbewegung des Kolbens erleichtert, was den Energieverbrauch reduziert.The inlet chamber can be connected to the working chamber via the inlet channels and the relief channel. The inlet chamber is connected to an air inlet through which ambient air in particular enters the inlet chamber. In the inlet chamber, the air is distributed between the inlet channels and the at least one relief channel and is sucked into the working chamber via these. The enlarged cross-section facilitates the suction stroke movement of the piston, which reduces energy consumption.

Weiterhin kann das Entlastungssystem zur Stützung der Lamelle ein Mittel zur Hubbegrenzung der Lamelle umfassen. Insbesondere bei großen Luftvolumen, die beim Saughub in den Arbeitsraum durch den entstehenden Unterduck gesaugt werden, kann es erforderlich sein, dass die Lamellenbewegung begrenzt werden muss, wie dies auch bei der Ventillamelle entsprechend dem StdT notwendig ist. Zur Hubbegrenzung der Lamelle kann beispielsweise eine in den Arbeitsraum ragende Begrenzungslamelle verwendet werden. Damit der Totraum trotzdem relativ klein bleibt, kann der Zylinder, für die Begrenzungslamelle, eine entsprechende Aussparung aufweisen. Alternativ kann diese Aussparung auch direkt als Mittel zur Begrenzung verwendet werden, so dass die Lamelle zumindest beim Start der Hubbewegung in die Aussparung schlägt.Furthermore, the relief system for supporting the lamella can include a means for limiting the stroke of the lamella. In particular, with large volumes of air that are sucked into the working chamber during the suction stroke due to the resulting negative pressure, it may be necessary to limit the movement of the lamella, as is also necessary for the valve lamella according to the StdT. To limit the stroke of the lamella, for example, a limiting lamella that protrudes into the working chamber can be used. To ensure that the dead space remains relatively small, the cylinder can have a corresponding recess for the limiting lamella. Alternatively, this recess can also be used directly as a means of limitation, so that the lamella hits the recess at least at the start of the stroke movement.

Weiterhin kann das Entlastungssystem einen mittels einem Federelement rückstellbaren Entlastungskolben umfassen, der mittels eines Steuerdrucks betätigbar ist.Furthermore, the relief system can comprise a relief piston that can be reset by means of a spring element and can be actuated by means of a control pressure.

In einer weiteren Ausführung kann der Hubkolbenverdichter als zweistufiger Verdichter, mit einer Vorstufe und einer Hochdruckstufe, ausgeführt sein, wobei im Zylinderkopf für jede Stufe ein Entlastungssystem und ein Verbindungskanal, der den Entlastungskanal der Hochdruckstufe mit der Einlasskammer verbindet, vorgesehen sind. Bei mehrstufigen Verdichtern erfolgt die Entlastung des Kompressionshubs aller Stufen über eine Verbindung die den jeweiligen Arbeitsraum über den Entlastungskanal gesteuert mit der Einlasskammer verbindet. So kann in der Entlastungsstellung der Lamelle auch beim Saughub der Hochdruckstufe Umgebungsluft direkt in den Arbeitsraum gelangen.In another version, the reciprocating piston compressor can be designed as a two-stage compressor, with a pre-stage and a high-pressure stage, whereby a relief system and a connecting channel that connects the relief channel of the high-pressure stage to the inlet chamber are provided in the cylinder head for each stage. In multi-stage compressors, the compression stroke of all stages is relieved via a connection that connects the respective working chamber to the inlet chamber via the relief channel. In this way, when the lamella is in the relief position, ambient air can also enter the working chamber directly during the suction stroke of the high-pressure stage.

Im Gegensatz zur Lamelle der Vorstufe, ist die Lamelle des Entlastungssystems der Hochdruckstufe derart ausgelegt, dass diese im Betrieb beim Saughub in der Schließstellung verbleibt. Die Lamelle der Hochdruckstufe bzw. nachfolgender Hochdruckstufen ist somit so ausgelegt, dass die Lamelle nur aktiv, mittels des Kolbens des Entlastungssystems in die Offenstellung, bewegbar ist.In contrast to the lamella of the pre-stage, the lamella of the relief system of the high-pressure stage is designed in such a way that it remains in the closed position during operation during the suction stroke. The lamella of the high-pressure stage or subsequent High pressure stages are designed in such a way that the slat can only be actively moved into the open position by means of the piston of the relief system.

Weiterhin wird ein Verfahren zum Betreiben eines Hubkolbenkompressors nach dem Anspruch 1.Furthermore, a method for operating a reciprocating piston compressor according to claim 1 is provided.

Das Verfahren ist dadurch gekennzeichnet, dass bei einem Saughub, bei dem ein Unterdruck im Arbeitsraum erzeugt wird, eine Lamelle des Entlastungssystems, selbsttätig oder, bei Betätigung des Entlastungssystems, zwangsweise in eine Offenstellung bewegt wird, so dass zusätzliche Luft über die Einlasskammer und den Entlastungskanal in den Arbeitsraum gesaugt wird, oder bei Betätigung des Entlastungssystems Luft über den Entlastungskanal aus dem Arbeitsraum herausgedrückt werden kann. Dieses Verfahren kommt bei einem einstufigen Hubkolbenverdichter oder der Vorstufe bzw. der ersten Stufe eines mehrstufigen Hubkolbenverdichters zum Einsatz.The method is characterized in that during a suction stroke, in which a negative pressure is generated in the working chamber, a lamella of the relief system is moved automatically or, when the relief system is activated, forcibly into an open position, so that additional air is sucked into the working chamber via the inlet chamber and the relief channel, or when the relief system is activated, air can be pushed out of the working chamber via the relief channel. This method is used in a single-stage reciprocating piston compressor or the preliminary stage or the first stage of a multi-stage reciprocating piston compressor.

In einer Ausführung des Hubkolbenkompressors als zweistufiger Verdichter sind eine Vorstufe und eine Hochdruckstufe in Reihe hintereinandergeschaltet, wobei im Zylinderkopf für jede Stufe ein Entlastungssystem vorgesehen ist. Bei einem derartigen Aufbau wird die Lamelle der Vorstufe beim Saughub selbsttätig in die Offenstellung bewegt und die Lamelle der Hochdruckstufe kann derart ausgelegt sein, dass diese beim Saughub in der Schließstellung verbleibt.In a design of the reciprocating piston compressor as a two-stage compressor, a pre-stage and a high-pressure stage are connected in series, with a relief system provided in the cylinder head for each stage. With such a design, the lamella of the pre-stage is automatically moved into the open position during the suction stroke and the lamella of the high-pressure stage can be designed in such a way that it remains in the closed position during the suction stroke.

Weiterhin kann im Zylinderkopf des zweistufigen Verdichters ein Verbindungskanal zur Verbindung der Entlastungssysteme vorgesehen sein, wobei der Entlastungskanal der Hochdruckstufe über den Verbindungskanal mit der Einlasskammer der Vorstufe verbunden ist, wobei zur Entlastung bzw. Schaltung in den Leerlaufbetrieb des Hubkolbenkompressors die Entlastungskolben beider Entlastungssysteme derart geschaltet werden, dass die Lamellen beider Stufen in eine Offenstellung bewegt werden.Furthermore, a connecting channel for connecting the relief systems can be provided in the cylinder head of the two-stage compressor, whereby the relief channel of the high-pressure stage is connected via the connecting channel to the inlet chamber of the pre-stage, whereby for the relief or switching to idle operation of the reciprocating piston compressor, the relief pistons of both Relief systems are switched in such a way that the slats of both stages are moved to an open position.

Nachfolgend wird die Erfindung anhand eines Ausführungsbeispiels näher erläutert. Die Figuren zeigen im Einzelnen:

Fig.1
Kolbenseitige Ansicht auf die Ventilplatte eines zweistufigen Hubkolbenverdichters mit Entlastungssystem
Fig.2
Zylinderkopfseitige Ansicht auf die Ventilplatte eines zweistufigen Hubkolbenverdichters mit Entlastungssystem
Fig.3
Entlastungssystem der ersten Verdichterstufe im Schnitt
Fig.4
Entlastungssystem der zweiten Verdichterstufe im Schnitt
The invention is explained in more detail below using an exemplary embodiment. The figures show in detail:
Fig.1
Piston side view of the valve plate of a two-stage reciprocating compressor with relief system
Fig.2
Cylinder head side view of the valve plate of a two-stage reciprocating compressor with relief system
Fig.3
Relief system of the first compressor stage in section
Fig.4
Relief system of the second compressor stage in section

Figur 1 zeigt eine kolbenseitige Ansicht auf die Ventilträgerplatte 4 eines zweistufigen Hubkolbenverdichters mit dem Entlastungssystem die dem Zylinderkopf 12 zugeordnet ist. Die beiden Verdichterstufen, die Vorstufe 2 und die Hochdruckstufe 3, sind ähnlich aufgebaut und unterscheiden sich aber in der Größe und der Funktion etwas voneinander. Gleich ist der grundsätzliche Aufbau. Beide Verdichterstufen haben ein Einlassventil 5a, b, das einseitig fixiert ist und auf der gegenüberliegenden Seite Anschlagflächen aufweist. Für die Anschlagflächen sind in dem Kurbelwellengehäuse 11 hier nicht dargestellte Aussparungen vorgesehen, durch die die Öffnungsbewegung der Einlassventile 5a, b begrenzt wird. Die Auslasskanäle 23 sind innerhalb der Außenkontur der Einlassventile 5a, b angeordnet und verlaufen teilweise durch Aussparungen in den Einlassventilen 5a, b. Etwa in der Mitte der Einlassventile 5a, b, also etwa in der Mitte des Arbeitsraums der Zylinder 20 a, b, an der die Einlassventile 5a, b eine Aussparung aufweisen, sind die zum Entlastungssystem 7a, b gehörenden Lamellen 9a, b angeordnet. Auch die Lamellen 9a, b sind einseitig eingespannt. Figure 1 shows a piston-side view of the valve carrier plate 4 of a two-stage reciprocating piston compressor with the relief system assigned to the cylinder head 12. The two compressor stages, the pre-stage 2 and the high-pressure stage 3, are similarly constructed but differ slightly in size and function. The basic structure is the same. Both compressor stages have an inlet valve 5a, b that is fixed on one side and has stop surfaces on the opposite side. Recesses (not shown here) are provided in the crankshaft housing 11 for the stop surfaces, through which the opening movement of the inlet valves 5a, b is limited. The outlet channels 23 are arranged within the outer contour of the inlet valves 5a, b and partially run through recesses in the inlet valves 5a, b. The slats 9a, b belonging to the relief system 7a, b are arranged approximately in the middle of the intake valves 5a, b, i.e. approximately in the middle of the working chamber of the cylinders 20a, b, where the intake valves 5a, b have a recess. The slats 9a, b are also clamped on one side.

Durch die unterschiedliche Funktion der Entlastungssysteme 7a, b unterscheiden sich die Ventile der Vorstufe 2 und der Hochdruckstufe 3 etwas. Durch das größere Luftvolumen, dass beim Saughub des Zylinders 20a der Vorstufe 2 angesaugt werden muss, ist die Lamelle 9a derart ausgelegt, dass sich das Ventil bei jedem Saughub des Zylinders 20a der Vorstufe 2 selbststätig öffnet. Zu Begrenzung der Öffnungsbewegung ist eine Begrenzungslamelle 22 vorgesehen, die einen Anschlag für die Lamelle 9a darstellt.Due to the different function of the relief systems 7a, b, the valves of the pre-stage 2 and the high-pressure stage 3 differ slightly. Due to the larger air volume that is sucked in during the suction stroke of the cylinder 20a of the pre-stage 2 must be opened, the lamella 9a is designed in such a way that the valve opens automatically with each suction stroke of the cylinder 20a of the preliminary stage 2. To limit the opening movement, a limiting lamella 22 is provided, which represents a stop for the lamella 9a.

Figur 2 zeigt eine zylinderkopfseitige Ansicht auf die Ventilträgerplatte 4 eines zweistufigen Hubkolbenverdichters mit Entlastungssystem. In dieser Ansicht sind die Kanäle und Kammern der Verdichterstufen gut zu erkennen. Beide Stufen 2, 3 weisen jeweils eine Einlasskammer 14a, b und eine Auslasskammer 15 a, b auf. In den Auslasskammern sind die selbsttätig wirksamen Auslassventile 6a, b angeordnet, die in der Schließstellung die Auslasskanäle 23 in der Ventilträgerplatte verschließen und in eine Offenstellung bewegt werden, wenn ein festlegbarer Druck im Arbeitsraum überschritten wird. Figure 2 shows a cylinder head side view of the valve carrier plate 4 of a two-stage reciprocating piston compressor with relief system. In this view, the channels and chambers of the compressor stages can be clearly seen. Both stages 2, 3 each have an inlet chamber 14a, b and an outlet chamber 15a, b. The automatically acting outlet valves 6a, b are arranged in the outlet chambers, which close the outlet channels 23 in the valve carrier plate in the closed position and are moved to an open position when a definable pressure in the working chamber is exceeded.

Im Bereich der Einlasskammer 14a der Vorstufe 2 sind mehrere Kanalöffnungen durch die Ventilträgerplatte 4 dargestellt. Ein Teil der Öffnungen, der äußere Halbkreis, sind die Einlasskanäle 21a, die dem Einlassventil 5a mit der Einlassventillamelle 18a zugeordnet sind. Bei einem Saughub wird die Luft durch die Einlasskanäle 21a in den Arbeitsraum gesaugt, die Einlassventillamelle 18a in eine Offenstellung bewegt. Bei einem Kompressionshub verschließt die Einlassventillamelle 18a die Einlasskanäle 21a. Innerhalb des Halbkreises der Einlasskanäle 21a sind die Entlastungskanäle 19a angeordnet. Deren Durchgang wird mittels der Lamelle 9a des Entlastungssystems 7a geschaltet.In the area of the inlet chamber 14a of the pre-stage 2, several channel openings are represented by the valve carrier plate 4. Part of the openings, the outer semicircle, are the inlet channels 21a, which are assigned to the inlet valve 5a with the inlet valve lamella 18a. During a suction stroke, the air is sucked into the working chamber through the inlet channels 21a, and the inlet valve lamella 18a is moved into an open position. During a compression stroke, the inlet valve lamella 18a closes the inlet channels 21a. The relief channels 19a are arranged within the semicircle of the inlet channels 21a. Their passage is switched by means of the lamella 9a of the relief system 7a.

Die Hochdruckstufe ist etwas anders ausgelegt, hier ist der Entlastungskanal 19b des Entlastungssystems 7b in einer separaten Kammer angeordnet, die über den Verbindungskanal 13 mit der Einlasskammer 14a der Vorstufe 2 verbunden ist. Nicht dargestellt ist die separate Kanalverbindung zwischen Auslasskammer 15a der Vorstufe 2 und Einlasskammer 14b der Hochdruckstufe 3.The high-pressure stage is designed somewhat differently; here the relief channel 19b of the relief system 7b is arranged in a separate chamber, which is connected to the inlet chamber 14a of the pre-stage 2 via the connecting channel 13. Not shown is the separate channel connection between the outlet chamber 15a of the pre-stage 2 and the inlet chamber 14b of the high-pressure stage 3.

Figur 3 und 4 zeigen die Entlastungssysteme 7a, b der Vorstufe 2 und der Hochdruckstufe 3 im Schnitt. Der generelle schichtweise Aufbau des Zylinderkopfes 12 ist aus dem Stand der Technik bekannt, so dass hier nur die erfindungswesentlichen Kanäle und Kammern weiter betrachtet werden. Das erfindungsgemäße Entlastungssystem 7a für die Vorstufe ist in Figur 3 und das Entlastungssystem 7b für die Hochdruckstufe 3 ist in Figur 4 dargestellt. Figure 3 and 4 show the relief systems 7a, b of the pre-stage 2 and the high-pressure stage 3 in section. The general layered structure of the cylinder head 12 is known from the prior art, so that only the channels and chambers essential to the invention will be considered further here. The relief system 7a according to the invention for the pre-stage is shown in Figure 3 and the relief system 7b for the high pressure stage 3 is in Figure 4 shown.

Bei einem einstufigen Verdichter kann das Entlastungssystem 7a der Vorstufe wie oben beschrieben und in Figur 3 dargestellt verwendet werden. Bei einem Mehrstufigen, also mehr als zwei Stufen, erhalten alle der Vorstufe folgenden Stufen das Entlastungssystem 7b der Hochdruckstufe 2, wobei in einer bevorzugten Ausführung ein Verbindungskanal vorgesehen sein kann, über den alle Stufen mit der Einlasskammer der Vorstufe verbindbar sind. Alternativ kann auch jede Stufe einen separaten Kanal umfassen der mit der Umgebung verbunden istIn a single-stage compressor, the relief system 7a of the pre-stage can be designed as described above and in Figure 3 shown. In a multi-stage system, i.e. more than two stages, all stages following the preliminary stage receive the relief system 7b of the high-pressure stage 2, whereby in a preferred embodiment a connecting channel can be provided via which all stages can be connected to the inlet chamber of the preliminary stage. Alternatively, each stage can also comprise a separate channel that is connected to the environment.

Das Besondere am Entlastungsventil der Vorstufe 2 ist die Begrenzungslamelle 22, die als massives Bauteil ausgeführt ist und die Lamelle 9a abstützt so dass die Lamelle 9a sich nicht zu weit in den Arbeitsraum verbiegt und es so zu einer zu großen Biegebeanspruchung kommt. Der Zylinder 20a hat eine Aussparung an der Stirnfläche, in die die Begrenzungslamelle 22 eintaucht, wenn der Zylinder sich am oberen Totpunkt befindet, so dass der Schadraum möglichst klein wird.The special feature of the relief valve of the pre-stage 2 is the limiting lamella 22, which is designed as a solid component and supports the lamella 9a so that the lamella 9a does not bend too far into the working area and thus does not result in excessive bending stress. The cylinder 20a has a recess on the front face into which the limiting lamella 22 dips when the cylinder is at top dead center, so that the dead space is as small as possible.

Die Aussparung ist gerade so groß, dass die Begrenzungslamelle 22 und die im geöffneten Zustand darauf liegende Lamelle 9a darin Platz finden.The recess is just large enough to accommodate the limiting slat 22 and the slat 9a lying on it in the open state.

Weiterhin ist der Entlastungskolben 10a zu erkennen der im Zylinderkopf 12 geführt ist. In der dargestellten Position befindet sich dieser in der Ruhestellung, und wird von einer Feder in dieser Stellung gehalten. Über den dargestellten Steuerdruckkanal 16 kann der Entlastungskolben 10a druckbeaufschlagt werden, so dass dieser in die Entlastungsstellung und die Lamelle 9a in die Offenstellung bewegt werden.The relief piston 10a can also be seen, which is guided in the cylinder head 12. In the position shown, this is in the rest position and is held in this position by a spring. The relief piston 10a can be pressurized via the control pressure channel 16 shown, so that it is moved into the relief position and the lamella 9a into the open position.

Die Besonderheit des in Figur 4 dargestellten Entlastungssystem 8b der Hochdruckstufe 3 ist die Auslegung der Lamelle 9b die derart federsteif ausgelegt ist, dass sie nur mit Hilfe des Entlastungskolbens 10b in die Offenstellung bewegt werden kann. Ein Saughub des Kolbens 20b der Hochdruckstufe 2 bewirkt keine selbsttätige Bewegung der Lamelle 9b in die Offenstellung. Beide Entlastungskolben 10a, b werden über den dargestellten Steuerdruckkanal 16 gleichzeitig mit Druckluft beaufschlagt.The special feature of the Figure 4 The design of the lamella 9b shown in the relief system 8b of the high pressure stage 3 is such that it is spring-stiff that it can only be moved into the open position with the help of the relief piston 10b. A suction stroke of the piston 20b of the high-pressure stage 2 does not cause the lamella 9b to move automatically into the open position. Both relief pistons 10a, b are simultaneously pressurized with compressed air via the control pressure channel 16 shown.

Der Kolben 20b weist ebenfalls eine Vertiefung auf, in der die Lamelle 9b in der Offenstellung Platz hat.The piston 20b also has a recess in which the lamella 9b fits in the open position.

Claims (11)

  1. Reciprocating-piston compressor (1) for a compressed-air supply system in a motor vehicle, with a cylinder head (12) comprising a valve carrier plate (4) and an inlet valve flap (18a, b) via which the one inlet chamber (14a, b) can be connected to a working space via multiple inlet channels (21a, b) in the valve carrier plate (4), and with a pressure-relief system (7a, b) which is integrated in the cylinder head (12) and able to switch a pressure-relief channel (19a, b) in the valve carrier plate (4) which connects the working space to a space in the cylinder head (12), wherein the pressure-relief system (7a, b) comprises a switch device (8a, b) and a flap (9a, b), and wherein the flap (9a, b) is attached to the valve carrier plate (4) on the working space side and can be lifted from the valve carrier plate (4) in order to open the pressure-relief channel (19a, b), wherein the flap (9a, b) can be lifted autonomously and/or controlled by the pressure-relief system (7a, b), characterized in that the pressure-relief channel (19a) is an air-conductive connection between the inlet chamber (14a) and the working space.
  2. Reciprocating-piston compressor (1) according to Claim 1, characterized in that the inlet valve flap (18a, b) has a recess within which the at least one pressure-relief channel (19a, b) and the flap (9a, b) are arranged.
  3. Reciprocating-piston compressor (1) according to Claim 2, characterized in that the flap (9a, b) is configured as a reed valve.
  4. Reciprocating-piston compressor (1) according to Claim 2, characterized in that to support the flap (9a, b), the pressure-relief system (7a, b) comprises means for limiting the lift of the flap (9a, b).
  5. Reciprocating-piston compressor (1) according to Claim 4, characterized in that the means for limiting the lift of the flap (9a) is a limiting flap (22) protruding into the working space.
  6. Reciprocating-piston compressor (1) according to Claim 1, characterized in that the pressure-relief system (7a, b) comprises a pressure-relief piston (10a, b) which can be reset by means of a spring element and actuated by means of a control pressure.
  7. Reciprocating-piston compressor (1) according to Claim 1, characterized in that the reciprocating-piston compressor (1) is configured as a two-stage compressor with a pre-stage (2) and a high-pressure stage (3), wherein for each stage, the cylinder head (12) comprises a pressure-relief system (7a, b) and a connecting channel (13) which connects the pressure-relief channel (19b) of the high-pressure stage (3) to the inlet chamber (14a) of the pre-stage (2).
  8. Reciprocating-piston compressor (1) according to Claim 7, characterized in that the pressure-relief system (7b) of the high-pressure stage (3) has a flap (9b) which is configured such that during operation, the flap (9b) remains in the closed position during a suction stroke.
  9. Method for operating a reciprocating-piston compressor (1) according to any of Claims 1 to 8 to generate compressed air for a utility vehicle, wherein the reciprocating-piston compressor (1) has a cylinder head (12) in which a pressure-relief system (7a, b) is integrated which is able to switch a pressure-relief channel (19a, b) in a valve carrier plate (4) of the cylinder head (12), which channel connects a working space of the reciprocating-piston compressor (1) to a space in the cylinder head (12), characterized in that on a suction stroke in which a vacuum is created in the working space, a flap (9a) of the pressure-relief system (7a) is moved into an open position, either autonomously or by force on actuation of the pressure-relief system (7a), so that additional air is drawn into the working space via the inlet chamber (14a) and the pressure-relief channel (19a), or on a compression stroke, air can be pushed out of the working space into the inlet chamber (14a) via the pressure-relief channel (19a).
  10. Method according to Claim 9, characterized in that the reciprocating-piston compressor (1) is configured as a two-stage compressor with a pre-stage (2) and a high-pressure stage (3), wherein a pressure-relief system (7a, b) is provided in the cylinder head (12) for each stage, wherein the flap (9a) of the pre-stage moves autonomously into the open position on a suction stroke, and the flap (9b) of the high-pressure stage (3) is configured such that it remains in the closed position on a suction stroke.
  11. Method according to Claim 10, characterized in that in the cylinder head (12), the two-stage compressor (1) a connecting channel (13) for connecting the pressure-relief systems (7a, b) is provided, wherein the pressure-relief channel (19b) of the high-pressure stage (3) can be connected to the inlet chamber (14a) of the pre-stage (2) via the connecting channel (13), wherein for pressure-relief of the reciprocating-piston compressor (1), the pressure-relief pistons (10a, b) of both pressure-relief systems (7a, b) are switched such that the flaps (9a, b) of both stages (2, 3) are moved into an open position.
EP20743992.8A 2019-07-24 2020-07-16 Valve device for a reciprocating-piston compressor Active EP4004370B1 (en)

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CN (1) CN114270037A (en)
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CN115977930A (en) * 2023-02-28 2023-04-18 采埃孚商用车系统(青岛)有限公司 Unloading device and air compressor

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WO2021013670A1 (en) 2021-01-28
CN114270037A (en) 2022-04-01
DE102019119944A1 (en) 2021-01-28
EP4004370A1 (en) 2022-06-01

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