EP3408536B1 - Compresseur à piston équipé d'un dispositif de dégazage - Google Patents

Compresseur à piston équipé d'un dispositif de dégazage Download PDF

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Publication number
EP3408536B1
EP3408536B1 EP17701320.8A EP17701320A EP3408536B1 EP 3408536 B1 EP3408536 B1 EP 3408536B1 EP 17701320 A EP17701320 A EP 17701320A EP 3408536 B1 EP3408536 B1 EP 3408536B1
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EP
European Patent Office
Prior art keywords
valve
compression chamber
piston compressor
pressure
inlet
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
EP17701320.8A
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German (de)
English (en)
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EP3408536A1 (fr
Inventor
Gilles Hebrard
Wolfgang Kiener
Jean-Baptiste Marescot
Jörg MELLAR
Michel Saintive
Thomas Weinhold
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Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
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Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
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Publication of EP3408536A1 publication Critical patent/EP3408536A1/fr
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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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/002—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for driven by internal combustion engines
    • 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
    • F04B49/022—Stopping, starting, unloading or idling control by means of pressure

Definitions

  • the invention relates to a piston compressor for compressing a gas, which can optionally be separated from a drive device by means of a coupling, with an inlet valve which is arranged between an inlet line for gas to be compressed and a compression chamber of the piston compressor and an outlet valve which is arranged between the compression chamber of the piston compressor and a compressed gas discharge line is arranged.
  • Such compressors are used, for example, for supplying compressed air to commercial vehicles, in particular for supplying compressed air to the brake system.
  • the compressor is driven by the drive train of the internal combustion engine.
  • Applications are known in which a coupling is arranged between the compressor and the drive connection in order to separate the compressor from the drive when the compressed air system of the commercial vehicle is filled with compressed air.
  • the outlet line of the compressor is emptied simultaneously with the opening of the clutch. When the compressor is restarted, the pressure in the then pressure-free outlet line must first be built up again before compressed air can be supplied to the compressed air system.
  • solutions are also known in which the outlet line is not switched to a pressure-free state while the piston compressor is not driven.
  • a piston compressor which can be disconnected from the drive via a clutch when a certain maximum pressure has been built up.
  • the clutch is disengaged, i.e. the drive is disconnected from the piston compressor, by means of a pressure from the compressed air reservoir filled by the piston compressor during operation.
  • the piston compressor When the piston compressor is restarted with such a high pressure in the compression chamber, the first compression stroke of the piston results in a compression of the gas in the compression chamber to about 60 bar.
  • the torque that occurs here is far too high for the clutch, which in this case slips, overheats and wears impermissibly.
  • such a high pressure in the compression chamber can also damage the compressor itself.
  • the pamphlets DE30 42 069 A1 and DE 20 2006 020 240 U1 each disclose a technical teaching which is suitable for eliminating such a problem and for venting the compression chamber during the time in which the piston is not driven by the drive.
  • the two publications each specify options for venting the pressure on the outlet side of the compressor, for which either a complicated mechanical design ( DE 30 42 069 A1 ) or a complex electrical solution ( DE 20 2006 020 240 U1 ) is applied.
  • the invention is therefore based on the object of providing an improved reciprocating compressor which avoids the aforementioned disadvantages and the undesirable effects arising therefrom.
  • a piston compressor for compressing a gas which can be separated from a drive device, with an inlet valve which is arranged between an inlet line for the gas to be compressed and a compression chamber of the piston compressor and an outlet valve which is arranged between the compression chamber of the piston compressor and an outlet line for compressed gas is arranged.
  • the piston compressor has a venting device, through which compressed gas can be discharged from the compression chamber, which gas passes back into the compression chamber from the outlet line during the separation of the piston compressor from the drive device.
  • Such a reciprocating compressor has an inlet line which is in particular part of an inlet system and through which a gas to be compressed is guided to a compression chamber of the reciprocating compressor.
  • An inlet valve is arranged between the inlet line and the compression chamber, which is open while gas to be compressed is being sucked into the compression chamber (the pressure in the compression chamber is lower than the pressure in the inlet line).
  • the inlet valve closes the compression space off from the inlet line.
  • An outlet valve is arranged between the compression space and the outlet line, which is opened when the compressed gas is expelled from the compression space (the pressure in the compression space is higher than the pressure in the outlet line) and thus defines a connection between the compression space and the outlet line.
  • the outlet valve closes the connection between the compression space and the outlet line while the gas to be compressed is being sucked into the compression space (the pressure in the compression space is lower than the pressure in the outlet line) in order to prevent the backflow of compressed gas from the outlet line into the compression space.
  • valves with a closing body are often used which, depending on the pressure difference on both sides of the valve, is pressed onto the valve seat and thereby closes or is lifted from the valve seat, whereby the valve opens.
  • a common type of valve of this type has a valve tongue serving as a closing body.
  • the piston compressor according to the invention has a venting device, through which compressed gas can be discharged from the compression chamber in order to lower the pressure therein.
  • compressed gas can be discharged, which during a separation of the piston compressor from the drive device, in particular through an exhaust valve that does not close completely, gets back into the compression chamber from the pressurized outlet line and causes a pressure increase there.
  • the compressed gas can be discharged from the compression chamber into an area with lower pressure, in particular ambient pressure, by means of the ventilation device. This allows the compressed gas to enter an area escape, which has a lower pressure than the compression chamber into which compressed gas has penetrated from the outlet line. As a result of the discharge of the compressed gas, the pressure in the compression chamber drops.
  • the area with the ambient pressure is formed by the environment itself, a gas space connected to the inlet system or the inlet line, or the interior of the crankcase of the reciprocating compressor.
  • An area with ambient pressure in the intake system can be, for example, the intake line or a gas space connected to it, which is formed, for example, in the cylinder head of the piston compressor and thus also represents part of the intake line.
  • the area with the ambient pressure is formed by the interior of the crankcase of the piston compressor
  • the gas flowing through the ventilation device from the compression chamber of the piston compressor is guided into the crankcase, where in particular a pressure equalization in the crankcase and then via its ventilation system with the environment takes place.
  • Pressure fluctuations can occur both in a gas space connected to the intake system and in the crankcase of the reciprocating compressor: in the intake system, in particular, depending on the fresh gas intake - for example when the intake system is connected to the intake system of a correspondingly large internal combustion engine - or in particular due to previous crank drive movements in the crankcase .
  • the pressure prevailing in a gas space connected to the intake system or in the crankcase is regarded as ambient pressure in connection with this invention .
  • the inlet valve forms the venting device.
  • the inlet valve is designed so that a connection between the inlet line and the compression chamber can only be closed from a pressure in the compression chamber that is at least 0.1 bar, preferably at least 0.2 bar and in particular at least 0.5 bar higher than that Pressure in the inlet line, which essentially corresponds to the ambient pressure.
  • a pressure in the compression chamber which is below the limit value of at least 0.1 bar, preferably at least 0.2 bar and in particular at least 0.5 bar excess pressure, there is a continuous connection between the Inlet pipe and the compression chamber.
  • a compressed gas that enters the compression chamber during a separation of the piston compressor from the drive device, i.e. when the piston compressor is at a standstill, can be discharged through this opening of the inlet valve into the inlet line without pressure build-up in the compression chamber of the compressor.
  • the inlet valve in which the inlet valve can only be closed from a predetermined pressure in the compression chamber, has a concave valve seat, in particular on the valve plate, and an essentially flat valve tongue, so that the valve tongue can only be opened after a pressure
  • the elastic deformation caused in the compression chamber is in sealing contact with the valve seat.
  • the inlet valve only closes when a sufficiently high pressure acts in the compression chamber during the compression stroke, which pressure deforms the valve tongue in such a way that it rests against the concave valve seat in a sealing manner.
  • the inlet valve is open. Thus, no pressure build-up can be brought about in the compression chamber by compressed gas which returns from the outlet line to the compression chamber during the separation of the piston compressor from the drive device.
  • the inlet valve in which the inlet valve can only be closed from a predetermined pressure in the compression chamber, has a flat valve seat and a curved valve tongue.
  • the valve tongue consequently only lies against the valve seat in a sealing manner after an elastic deformation caused by the pressure in the compression chamber.
  • the inlet valve only closes when a sufficiently high pressure acts in the compression chamber during a compression stroke, which deforms the bent valve tongue in such a way that it rests sealingly on the valve seat that is just formed.
  • the inlet valve remains open as long as the pressure in the compression chamber has a lower value than the pressure which leads to the inlet valve closing, in particular during a compression stroke.
  • a compressed gas which returns from the outlet line to the compression chamber during the separation of the piston compressor from the drive device cannot lead to a pressure build-up in the compression chamber.
  • a ventilation channel forms the ventilation device.
  • a ventilation channel which in particular creates a permanent connection to an area with a lower pressure than the compression chamber, in particular ambient pressure, allows gas to flow from one end of the ventilation channel in the compression chamber, which is under a higher pressure, through the ventilation channel into an area with a lower pressure Pressure, in particular ambient pressure, can be dissipated at the other end of the ventilation duct. This results in a pressure equalization with the compression chamber. So if gas from the pressurized outlet line returns to the compression chamber during a separation of the piston compressor from the drive device, no increased pressure can build up there because the gas is discharged through the ventilation duct.
  • At least one end of the ventilation duct is arranged in the valve plate and in particular establishes a connection between the compression chamber and the surroundings of the reciprocating compressor or its inlet system.
  • a disadvantage of a permanently open ventilation duct is that it allows the gas to escape from the compression chamber even during a compression stroke, which reduces the efficiency of the compressor.
  • the vent channel has such a small cross section that pressure equalization through the vent channel is possible, but the throttling effect of the small cross section of the vent channel prevents the pressure flow of a larger volume flow during a compression stroke.
  • An alternative design which restricts the gas from escaping from the compression chamber during a compression stroke, has a suitable shut-off valve in the venting channel, which closes it once a predetermined excess pressure has been reached.
  • a check valve suitable for this is, for example, a gravity ball valve.
  • Such a shut-off valve is advantageously designed to be robust against contamination by lubricating oil impurities.
  • At least one end of the ventilation duct is arranged in the cylinder wall, which for example establishes a connection with the surroundings of the piston compressor.
  • the ventilation channel can have a connecting device in the form of a line, which serves as an extension of the ventilation channel and this in particular with or with the inlet system connects to the interior of the crankcase of the reciprocating compressor.
  • a ventilation duct also forms an opening in the compression chamber through which gas can escape from the compression chamber even during the compression stroke, which reduces the efficiency of the piston compressor.
  • the ventilation duct is therefore designed to be large enough to ensure pressure equalization so that the gas volume flow, which can thereby be removed from the compression chamber during a separation of the compressor from the drive device, is at least as large as that from the outlet line back in this time segment The gas volume flow of compressed gas from the outlet line reached the compression chamber.
  • a check valve or a check valve is arranged in the ventilation channel or in a connecting device connected to it.
  • a check or shut-off valve can on the one hand prevent gas from escaping from the compression chamber during a compression stroke of the reciprocating compressor, on the other hand such a check or shut-off valve can also serve to prevent possibly contaminated gas, especially from the crankcase, from being sucked into the compression chamber.
  • piston, cylinder, cylinder head, etc. is addressed above in connection with the components of the piston compressor, the properties described here also apply to a piston compressor with two or more of these elements, since the present invention is not only for single-stage piston compressors but can also be used for multi-stage piston compressors.
  • Fig. 1 shows a schematic representation of an exemplary reciprocating compressor 10 as it is known as the prior art.
  • the crankshaft 11 of the piston compressor 10 is connected to a drive device (not shown, here an internal combustion engine) via a clutch 3 and can optionally be separated from this drive device by means of the clutch 3.
  • a drive device not shown, here an internal combustion engine
  • the clutch 3 When the clutch 3 is disengaged, no torque is transmitted to the crankshaft 11 of the piston compressor 10, so that the crankshaft 11 stands still during the separation of the piston compressor 10 from the drive device.
  • the crankshaft 11 is connected to a connecting rod 12 eccentrically mounted thereon, on which a piston 13 is mounted.
  • the piston 13 is mounted so that it can move axially in a cylinder 14 of the piston compressor 10.
  • the crank drive 15, which has at least one crankshaft 11, a connecting rod 12 and a piston 13, is arranged in a crankcase 16 which is fixedly connected to the cylinder 14.
  • the piston 13 is moved by the connecting rod 12 in the cylinder 14 in such a way that it executes a stroke movement.
  • the cylinder 14 is closed by a valve plate 20.
  • the cylinder 14, the piston 13 and the valve plate 20 thus define the compression chamber 17 in the cylinder 14.
  • the inlet line 22 is part of an inlet system 23 which sucks in fresh air from the environment through a filter (not shown) and supplies it to the compression chamber 17 via the inlet line 22 through the cylinder head (not shown).
  • the cylinder head is arranged above the valve plate 20 and has a cylinder head volume 24, which over the Inlet valve 21 is in communication with the compression chamber 17.
  • the inlet valve 21 is designed as a shut-off valve, which enables fresh air to be sucked into the compression chamber 17, but prevents the air drawn in via the inlet line 22 from flowing back into the compression chamber 17.
  • FIG. 11 shows an illustration of an exemplary discharge valve 26 as is frequently used in reciprocating compressors 10 in the prior art.
  • the outlet valve 26 is arranged on the valve plate 20 of the reciprocating compressor 10 above the compression chamber 17.
  • the valve plate 20 has an outlet opening 28 which connects the compression chamber 17 to a cylinder head volume 27a which is arranged in the valve plate 20 and cylinder head of the piston compressor 10 and which forms part of the outlet line 27.
  • the outlet valve 26 has a valve tongue 26a as the valve body, which is released from the valve seat 26b from a predetermined pressure difference between the compression chamber 17 and the outlet line 27 and enables air to flow from the compression chamber 17 into the outlet line 27.
  • the outlet valve 26 also has a contact element 26c which is arranged above the outlet opening 28 and on which the valve tongue 26a rests in the open state. As soon as the valve tongue 26a detaches from the valve seat 26b, the pressurized air can flow from the compression chamber 17 through the lateral open areas past the valve tongue 26a and the contact element 26c into the outlet line 27.
  • the valve plate 20 or the cylinder head volume 27a can, for example, have a pressure of up to 6 bar applied to it by the air flowing back there.
  • the piston compressor 10 If the piston compressor 10 is then reconnected to the drive device, the piston compressor 10 generates an internal pressure of approximately 60 bar on the first stroke. If the compression chamber 17 can withstand this enormous internal pressure, the torque generated on the crankshaft 11 is usually much too high for the clutch 3, so that the clutch 3 slips, overheats and wears impermissibly quickly.
  • FIG. 3 shows a schematic representation of a fourth exemplary embodiment of a reciprocating compressor 10 according to the invention.
  • the structure of the reciprocating compressor 10 in FIG Fig. 3 largely corresponds to the structure of the in Fig. 1 piston compressor 10 illustrated and described for this purpose, so that the same elements of the piston compressors 10 are denoted by the same reference numerals. Only the differences of the reciprocating compressor 10 are discussed below Fig. 3 compared to the piston compressor 10 Fig. 1 explained.
  • the in Fig. 3 The piston compressor 10 shown has a ventilation device in the form of a ventilation duct 34 which is arranged between the compression chamber 17 and the inlet system 23.
  • the ventilation channel 34 establishes a connection through which air can flow between the compression chamber 17 and the inlet system 23, so that when the piston compressor is at a standstill, no pressure can build up in the compression chamber 17 that is significantly higher than the ambient pressure.
  • the vent channel 34 is arranged in the area of the valve plate 20 on the upper side of the cylinder 14, so that a constant pressure equalization with the inlet line 32 of the piston compressor 10 takes place through the vent channel 34. If compressed air reaches the compression chamber 17 from the outlet line 27 while the piston compressor 10 is at a standstill, pressure equalization with the inlet line 22 takes place through the ventilation duct 34, so that no pressure build-up can occur in the compression chamber 17.
  • a disadvantage of such a ventilation duct 34 is that it is also open during a compression stroke of the piston compressor 10 and air to be compressed escapes from the compression chamber 17 in this phase. This lowers the efficiency of the reciprocating compressor 10.
  • vent channel 34 is therefore like this designed that this has only a small cross-section to enable sufficient pressure equalization while the piston compressor 10 is at a standstill with the inlet system 23, but on the other hand has a throttling effect at high pressures in order to limit the volume flow of the discharged air.
  • FIG. 4 shows a representation of a detail of a ninth exemplary embodiment of a piston compressor 10 according to the invention, in which the inlet valve 21 forms the venting device.
  • the elements of the inlet valve 21 are shown in FIG Fig. 4 shown in exploded view.
  • the inlet valve 21 forms the upper end of the compression chamber 17 in the cylinder 14.
  • the valve tongue 21a is designed in one piece with a first element of the inlet valve 21, which is arranged between the cylinder 14 and a contact element 21b of the inlet valve 21.
  • the contact element 21b shown as an example has two valve openings 21c which are closed by the valve tongue 21a depending on the pressure difference between the compression chamber 17 in the cylinder 14 and the pressure in the inlet system 23.
  • the valve tongue 21a has a curvature which is designed in such a way that the valve tongue 21a rests against the contact element 21b from a pressure in the compression chamber 22 (dashed representation of the valve tongue 21a) which in the exemplary embodiment is 0.4 bar higher than the pressure in the inlet system 23 ( Ambient pressure) and thereby closes the valve openings 21c.
  • the valve tongue 21a always has a curvature that there is a connection between the inlet system 23 and the compression chamber 17.
  • a compressed gas that has entered the compression chamber 17 can be discharged through the valve openings 21c of the inlet valve 21 into the inlet line 22 without a pressure build-up in the compression chamber 17 of the compressor 10.
  • FIG. 5 shows a schematic representation of a further exemplary embodiment of a piston compressor 10 according to the invention.
  • the structure of the piston compressor 10 in FIG. 5 largely corresponds to the structure of the piston compressor 10 in FIG Fig. 3 piston compressor 10 illustrated and described for this purpose, so that identical elements of the piston compressors 10 are denoted by the same reference numerals. In the following, only the differences between the piston compressor 10 from FIG. 5 and the piston compressor 10 will be discussed Fig. 3 explained.
  • a piston compressor 10 which also has a venting device in the form of a venting channel 39, which runs between the compression space 17 and the inlet system 23 is arranged.
  • a check valve in the form of a gravity ball valve 40 is arranged in the vent duct 39, which closes the vent duct 39 when the pressure in the compression chamber 17 exceeds a predetermined value, which presses the ball of the gravity ball valve 40 against its gravity on a valve seat located at the top of the gravity ball valve 40.
  • the shut-off valve thus restricts the escape of compressed air from the compression chamber 17 during a compression stroke.
  • the inlet valve 21 can also have a contact element 21b which has a recess in the area of the valve openings 21c, so that the valve tongue 21a in this embodiment as well only from a predetermined pressure in Compression chamber 17 rests sealingly on contact element 21b.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (8)

  1. Compresseur à piston pour la compression d'un gaz, qui peut être séparé d'un dispositif d'entraînement, comprenant une soupape (21) d'entrée, qui est montrée entre un conduit (22) d'entrée pour du gaz à comprimer et un espace (17) de compression du compresseur (10) à piston, et une soupape (26) de sortie, qui est montée entre l'espace (17) de compression du compresseur (10) à pistons et un conduit (27) de sortie pour du gaz comprimé, caractérisé en ce que la soupape (21) d'entrée a un siège de soupape constitué de manière plane et une lame (21a) de soupape constituée de manière incurvée, de manière à ce que la lame (21a) de soupape ne s'applique avec étanchéité au siège de soupape qu'après une déformation élastique provoquée par la pression dans l'espace (17) de compression et se ferme ainsi en fonction de la différence de pression des deux côtés de la soupape ou soit soulevée du siège de soupape, et en ce que la soupape (21) d'entrée forme un dispositif (34) de dégazage, par lequel du gaz comprimé, qui, pendant que le compresseur (10) à piston se sépare du dispositif d'entraînement, retourne du conduit (27) de sortie à l'espace (17) de compression, peut être évacué de l'espace (17) de compression.
  2. Compresseur à piston suivant la revendication 1, caractérisé en ce que le compresseur à piston peut être séparé du dispositif d'entraînement au moyen d'un embrayage.
  3. Compresseur à piston suivant la revendication 1, caractérisé en ce que le gaz comprimé peut être évacué de l'espace 17 de compression dans une région à la pression ambiante, qui est formée par l'atmosphère ambiante soi-même, un espace (22) pour du gaz communiquant avec le système (23) d'entrée ou l'intérieur du carter (16) de vilebrequin.
  4. Compresseur à piston suivant l'une des revendications 1 à 3, caractérisé en ce que la soupape (21) d'entrée est constituée de manière à pouvoir ainsi fermer une communication entre le conduit (22) d'entrée et l'espace (17) de compression seulement à partir d'une pression définie à l'avance dans l'espace (17) de compression, la pression définie à l'avance étant plus haute d'au moins 0,1 bar, de préférence d'au moins 0,2 bar et, d'une manière particulièrement préférée, d'au moins 0,5 bar que la pression dans le conduit (22) d'entrée.
  5. Compresseur à piston suivant la revendication 4, caractérisé en ce que la soupape (21) d'entrée a, au lieu d'un siège de soupape constitué de manière plane, un siège de soupape constitué de manière concave et, au lieu d'une lame (21) de soupape incurvée, une lame de soupape constituée de manière sensiblement plane, de manière à ce que la lame de soupape ne s'applique avec étanchéité au siège de la soupape que par une déformation élastique provoquée par la pression dans l'espace (17) de compression.
  6. Compresseur à piston suivant l'une des revendications 1 ou 3 précédentes, caractérisé en ce qu'un conduit (34, 39) de dégazage forme le dispositif de dégazage.
  7. Compresseur à piston suivant la revendication 6, caractérisé en ce qu'au moins une extrémité du conduit (34, 39) de dégazage est disposée dans la plaque (20) de la soupape ou dans la paroi (14) du cylindre.
  8. Compresseur à piston suivant l'une des revendications 6 ou 7, caractérisé en ce qu'un clapet anti-retour ou un robinet (40) d'arrêt est monté dans le conduit (34, 39) de dégazage.
EP17701320.8A 2016-01-27 2017-01-24 Compresseur à piston équipé d'un dispositif de dégazage Active EP3408536B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016201208.8A DE102016201208B4 (de) 2016-01-27 2016-01-27 Kolbenkompressor mit Entlüftungseinrichtung
PCT/EP2017/051406 WO2017129553A1 (fr) 2016-01-27 2017-01-24 Compresseur à piston équipé d'un dispositif de dégazage

Publications (2)

Publication Number Publication Date
EP3408536A1 EP3408536A1 (fr) 2018-12-05
EP3408536B1 true EP3408536B1 (fr) 2021-06-02

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EP17701320.8A Active EP3408536B1 (fr) 2016-01-27 2017-01-24 Compresseur à piston équipé d'un dispositif de dégazage

Country Status (7)

Country Link
US (1) US20180372087A1 (fr)
EP (1) EP3408536B1 (fr)
JP (1) JP2019503453A (fr)
KR (1) KR20180105211A (fr)
CN (1) CN108884820B (fr)
DE (1) DE102016201208B4 (fr)
WO (1) WO2017129553A1 (fr)

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JP2019503453A (ja) 2019-02-07
BR112018015262A2 (pt) 2018-12-18
KR20180105211A (ko) 2018-09-27
CN108884820A (zh) 2018-11-23
US20180372087A1 (en) 2018-12-27
DE102016201208B4 (de) 2024-01-11
WO2017129553A1 (fr) 2017-08-03
DE102016201208A1 (de) 2017-07-27
EP3408536A1 (fr) 2018-12-05
CN108884820B (zh) 2020-07-31

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