EP4004370B1 - Dispositif de soupape pour un compresseur à piston - Google Patents

Dispositif de soupape pour un compresseur à piston 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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Active
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EP20743992.8A
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German (de)
English (en)
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EP4004370A1 (fr
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)

Claims (11)

  1. Compresseur à piston alternatif (1) pour un système d'alimentation en air comprimé dans un véhicule automobile, comportant une culasse (12) comprenant une plaque de support de soupape (4) et une lamelle de soupape d'admission (18a, b) par le biais de laquelle une chambre d'admission (14a, b) peut être reliée à un espace de travail par le biais de plusieurs canaux d'admission (21a, b) dans la plaque de support de soupape (4), et comportant un système de détente (7a, b) intégré dans la culasse (12), à l'aide duquel un canal de détente (19a, b) dans la plaque de support de soupape (4), qui relie l'espace de travail à un espace dans la culasse (12), peut être commuté, le système de détente (7a, b) comprenant un dispositif de commutation (8a, b) et une lamelle (9a, b), et la lamelle (9a, b) étant fixée à la plaque de support de soupape (4) du côté de l'espace de travail et pouvant être soulevée de la plaque de support de soupape (4) pour l'ouverture du canal de détente (19a, b),
    le soulèvement de la lamelle (9a, b) pouvant s'effectuer automatiquement et/ou de manière commandée à l'aide du système de détente (7a, 7b),
    caractérisé en ce que
    le canal de détente (19a) est une liaison de guidage d'air entre la chambre d'admission (14a) et l'espace de travail.
  2. Compresseur à piston alternatif (1) selon la revendication 1,
    caractérisé en ce que
    la lamelle de soupape d'admission (18a, b) présente un évidement à l'intérieur duquel au moins un canal de détente (19a, b) et la lamelle (9a, b) sont disposés.
  3. Compresseur à piston alternatif (1) selon la revendication 2,
    caractérisé en ce que
    la lamelle (9a, b) est réalisée sous forme de soupape à languette.
  4. Compresseur à piston alternatif (1) selon la revendication 2,
    caractérisé en ce que
    le système de détente (7a, b) comprend, pour le support de la lamelle (9a, b), un moyen servant à la limitation de la course de la lamelle (9a, b).
  5. Compresseur à piston alternatif (1) selon la revendication 4,
    caractérisé en ce que
    le moyen servant à la limitation de la course de la lamelle (9a) est une lamelle de limitation (22) faisant saillie dans l'espace de travail.
  6. Compresseur à piston alternatif (1) selon la revendication 1,
    caractérisé en ce que
    le système de détente (7a, b) comprend un piston de détente (10a, b) pouvant être rappelé à l'aide d'un élément ressort, lequel piston de détente peut être actionné à l'aide d'une pression de commande.
  7. Compresseur à piston alternatif (1) selon la revendication 1,
    caractérisé en ce que
    le compresseur à piston alternatif (1) est réalisé sous forme de compresseur à deux étages comportant un étage préliminaire (2) et un étage haute pression (3), un système de détente (7a, b) et un canal de liaison (13) qui relie le canal de détente (19b) de l'étage haute pression (3) à la chambre d'admission (14a) de l'étage préliminaire (2) étant prévus dans la culasse (12) pour chaque étage.
  8. Compresseur à piston alternatif (1) selon la revendication 7,
    caractérisé en ce que
    le système de détente (7b) de l'étage haute pression (3) présente une lamelle (9b) qui est conçue de telle sorte que la lamelle (9b) demeure dans la position de fermeture lors du fonctionnement lors d'une course d'aspiration.
  9. Procédé de fonctionnement d'un compresseur à piston alternatif (1) servant à la génération d'air comprimé pour un véhicule utilitaire, selon l'une des revendications 1 à 8, le compresseur à piston alternatif (1) présentant une culasse (12) dans laquelle un système de détente (7a, b) est intégré, au moyen duquel peut être commuté un canal de détente (19a, b) dans une plaque de support de soupape (4) de la culasse (12) qui relie un espace de travail du compresseur à piston alternatif (1) à un espace dans la culasse (12),
    caractérisé en ce que,
    lors d'une course d'aspiration, lors de laquelle une dépression est générée dans l'espace de travail, une lamelle (9a) du système de détente (7a) est déplacée automatiquement ou, lors de l'actionnement du système de détente (7a), de manière forcée dans une position d'ouverture, de sorte que de l'air supplémentaire soit aspiré dans l'espace de travail par le biais de la chambre d'admission (14a) ou du canal de détente (19a) ou, lors d'une course de compression, de l'air puisse être poussé par le biais du canal de détente (19a) hors de l'espace de travail dans la chambre d'admission (14a).
  10. Procédé selon la revendication 9,
    caractérisé en ce que
    le compresseur à piston alternatif (1) est réalisé sous forme de compresseur à deux étages comportant un étage préliminaire (2) et un étage haute pression (3), un système de détente (7a, b) étant prévu dans la culasse (12) pour chaque étage (2, 3), la lamelle (9a) de l'étage préliminaire (2) étant déplacée automatiquement dans la position d'ouverture lors d'une course d'aspiration et la lamelle (9b) de l'étage haute pression (3) étant conçue de telle sorte que celle-ci demeure dans la position de fermeture lors d'une course d'aspiration.
  11. Procédé selon la revendication 10,
    caractérisé en ce que
    le compresseur (1) à deux étages dans la culasse (12) un canal de liaison (13) servant à la liaison des systèmes de détente (7a, b) est prévu, le canal de détente (19b) de l'étage haute pression (3) étant relié à la chambre d'admission (14a) de l'étage préliminaire (2) par le biais du canal de liaison (13), les pistons de détente (10a, b) des deux systèmes de détente (7a, b) étant commutés pour la détente du compresseur à piston alternatif (1), de telle sorte que les lamelles (9a, b) des deux étages (2, 3) soient déplacées dans une position d'ouverture.
EP20743992.8A 2019-07-24 2020-07-16 Dispositif de soupape pour un compresseur à piston Active EP4004370B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019119944.1A DE102019119944A1 (de) 2019-07-24 2019-07-24 Ventilvorrichtung für einen Hubkolbenverdichter
PCT/EP2020/070084 WO2021013670A1 (fr) 2019-07-24 2020-07-16 Dispositif de soupape pour un compresseur à piston

Publications (2)

Publication Number Publication Date
EP4004370A1 EP4004370A1 (fr) 2022-06-01
EP4004370B1 true EP4004370B1 (fr) 2024-09-11

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EP (1) EP4004370B1 (fr)
CN (1) CN114270037A (fr)
DE (1) DE102019119944A1 (fr)
WO (1) WO2021013670A1 (fr)

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WO2024138378A1 (fr) * 2022-12-27 2024-07-04 采埃孚商用车系统(青岛)有限公司 Compresseur d'air pour véhicule
CN115977930A (zh) * 2023-02-28 2023-04-18 采埃孚商用车系统(青岛)有限公司 卸荷装置和空气压缩机

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DE102016006358A1 (de) * 2016-05-21 2017-11-23 Wabco Gmbh Hubkolbenkompressor einer Druckluftversorgungsanlage

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DE102019119944A1 (de) 2021-01-28
EP4004370A1 (fr) 2022-06-01
CN114270037A (zh) 2022-04-01
JP2022542871A (ja) 2022-10-07
WO2021013670A1 (fr) 2021-01-28

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