WO2017129553A1 - 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
WO2017129553A1
WO2017129553A1 PCT/EP2017/051406 EP2017051406W WO2017129553A1 WO 2017129553 A1 WO2017129553 A1 WO 2017129553A1 EP 2017051406 W EP2017051406 W EP 2017051406W WO 2017129553 A1 WO2017129553 A1 WO 2017129553A1
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WO
WIPO (PCT)
Prior art keywords
valve
pressure
piston compressor
compression chamber
inlet
Prior art date
Application number
PCT/EP2017/051406
Other languages
German (de)
English (en)
Inventor
Gilles Hebrard
Wolfgang Kiener
Jean-Baptiste Marescot
Jörg MELLAR
Michel Saintive
Thomas Weinhold
Original Assignee
Knorr-Bremse Systeme für Nutzfahrzeuge GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Knorr-Bremse Systeme für Nutzfahrzeuge GmbH filed Critical Knorr-Bremse Systeme für Nutzfahrzeuge GmbH
Priority to CN201780020387.9A priority Critical patent/CN108884820B/zh
Priority to KR1020187024477A priority patent/KR20180105211A/ko
Priority to EP17701320.8A priority patent/EP3408536B1/fr
Priority to BR112018015262-5A priority patent/BR112018015262B1/pt
Priority to JP2018539067A priority patent/JP2019503453A/ja
Publication of WO2017129553A1 publication Critical patent/WO2017129553A1/fr
Priority to US16/047,854 priority patent/US20180372087A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component 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
    • F04B39/12Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/125Cylinder heads
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00Control, 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
    • F04B49/16Control, 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00Piston 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
    • F04B35/04Piston 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00Piston 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
    • F04B35/002Piston 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component 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
    • F04B39/08Actuation of distribution members
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00Control, 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
    • F04B49/02Stopping, starting, unloading or idling control
    • F04B49/022Stopping, starting, unloading or idling control by means of pressure

Definitions

  • the invention relates to a piston compressor for compressing a gas, which is optionally separable by means of a clutch from a drive device, with an inlet valve which is arranged between an inlet line for gas to be compressed and a compression chamber of the reciprocating compressor and an outlet valve, which between the compression space of
  • Piston compressor and a discharge line for compressed gas is arranged.
  • Such compressors are used for example for the compressed air supply of commercial vehicles, in particular for the compressed air supply of the brake system.
  • the drive of the compressor is carried out via the drive train of the internal combustion engine.
  • a clutch is arranged to separate the compressor from the drive when the compressed air system of the commercial vehicle is filled with compressed air.
  • the discharge line of the compressor is emptied simultaneously with the opening of the clutch.
  • the pressure in the then pressure-free outlet line must first be rebuilt before compressed air can be supplied to the compressed air system.
  • solutions are also known in which the outlet line is not switched pressure-free, while the reciprocating compressor is not driven.
  • Contaminants such as deposits by lubricating oil residues or especially of such dissolved particles is leaking.
  • the exhaust valves often have a valve tongue, between which and the valve seat such contaminants can get there and prevent the complete closing of the valve.
  • compressed air may return to the compression space of the compressor.
  • the pressure in the compression chamber of a reciprocating compressor in a 12.5 bar system can then rise to up to 6 bar.
  • a compression of the gas in the compression chamber results in the first compression stroke of the piston, a compression of the gas in the compression chamber to about 60 bar.
  • the torque occurring here is far too high for the clutch, which slips in this case, overheated and excessively excessive wear.
  • such a high pressure in the compression chamber can also lead to damage to the compressor itself.
  • the invention is therefore based on the object to provide an improved reciprocating compressor, which the aforementioned disadvantages and the resulting undesirable
  • a piston compressor for compressing a gas which is optionally separable by means of a clutch of a drive device, with an inlet valve, which between an inlet line for gas to be compressed and a compression space of
  • Piston compressor is arranged and an exhaust valve, which is arranged between the compression chamber of the reciprocating compressor and a discharge line for compressed gas.
  • Piston compressor has a venting device through which compressed gas from the compression space can be discharged, which during the separation of the reciprocating compressor of the
  • 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 space of the reciprocating compressor.
  • an inlet valve is arranged between the inlet line and the compression space, which is open during the intake of gas to be compressed into the compression space (the pressure in the compression space is lower than the pressure in the inlet line).
  • the intake valve closes the compression space opposite to the intake pipe.
  • an outlet valve is arranged, which is open when the compressed gas is expelled from the compression space (the pressure in
  • Compression space is higher than the pressure in the outlet pipe) and so a connection between the Compression space and the outlet defined.
  • the exhaust valve closes the connection between the compression space and the outlet line during the suction of gas to be compressed into the compression space (the pressure in the compression space is lower than the pressure in the outlet line) to prevent backflow of compressed gas from the discharge line into the compression space.
  • Both intake and exhaust valves of reciprocating compressors often employ valves with a closing body that is forced onto the valve seat depending on the pressure difference on either side of the valve and thereby closes or lifts off the valve seat, thereby opening the valve.
  • a common type of such valves has a serving as a closing body valve tongue.
  • the piston compressor according to the invention has a venting device, through which compressed gas from the compression chamber can be discharged in order to lower the pressure therein.
  • compressed gas is discharged, which passes during a separation of the reciprocating compressor of the drive device in particular by a not completely closing exhaust valve from the pressurized outlet line back into the compression space and there a
  • the compressed gas is by means of
  • Venting device from the compression chamber into a region of lower pressure
  • the compressed gas can escape into a region which has a lower pressure than the compression space, in which compressed gas has penetrated from the outlet line.
  • the pressure in the compression chamber decreases.
  • the region is formed with the ambient pressure from 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 inlet system can be, for example, the inlet line or a gas space connected to it, which is formed, for example, in the cylinder head of the piston compressor and thus also forms part of the inlet line.
  • the area is formed with the ambient pressure from the interior of the crankcase of the reciprocating compressor, which is characterized by the
  • Venting device from the compression chamber of the reciprocating compressor gas flowing into the Crankcase out where in particular first takes place a pressure equalization in the crankcase and then via the venting system with the environment.
  • Crankcase of the reciprocating compressor pressure fluctuations occur: in the intake system in particular depending on the Frischgasansaugung - for example, when the intake system is in communication with the intake system of a correspondingly large-sized engine - or due in particular previous crank drive movements in the crankcase.
  • the pressure prevailing in a gas space connected to the intake system or in the crankcase in the context of this invention is considered as ambient pressure ,
  • a switchable valve device forms the
  • Venting device by means of which compressed gas from the compression space can be discharged by a connection of the compression chamber with a region of lower pressure, in particular ambient pressure can be produced.
  • It may be a switchable valve device, by means of which a
  • vent opening of the compression chamber of the reciprocating compressor is optionally connectable to a region of lower pressure, in particular ambient pressure.
  • a 2/2-way valve can be used which, for example, is so switchable that it opens and closes in particular parallel or offset with the actuation of the clutch and thus enables a pressure equalization in the compression chamber by the discharge of compressed gas, as long as the Piston compressor is not driven.
  • it can also be provided to also switch such a valve device dependent on other parameters, such as, for example, the pressure actually prevailing in the compression chamber, which pressure is detected by pressure sensors connected thereto or in another suitable manner.
  • pilot-operated check valve which also assumes the function of the intake valve.
  • a pilot-operated check valve represents a switchable valve device which is located between the inlet line and the compression chamber of the compressor is arranged and the connection between the inlet line and the compression chamber in particular automatically opens and closes according to the function of an inlet valve.
  • a pilot-operated check valve is a switchable valve device, by means of which the connection between the inlet line and the compression chamber is optionally openable and closable in order to allow pressure reduction by discharging compressed gas from the compression chamber.
  • such a releasable check valve as well as the previously described switching valve in parallel or offset from the clutch operation switchable or in response to other, in particular with the pressure in the compression chamber related parameters, which are detected for example by means of sensors.
  • the inlet valve in the form of a pilot-operated check valve during a standstill of the compressor, a pressure equalization between the compression chamber and the inlet system take place, so that no significant pressure build-up can take place in the compression chamber.
  • Venting device by means of which compressed gas from the compression space can be discharged.
  • a check valve is particularly designed so that it then opens and the
  • Compression chamber with a region of lower pressure, in particular ambient pressure connects, when the pressure in the compression chamber due to a compressed during a separation of the piston compressor from the drive device from the discharge line back into the compression chamber compressed gas during a first compression stroke increases so much that damage to the piston compressor or a device connected to the reciprocating compressor threatens.
  • the check valve establishes a connection of the compression space with a region of lower pressure, in particular ambient pressure, whereby the compressed gas, which has passed from the outlet line back into the compression space during a separation of the piston compressor from the drive device, can be discharged.
  • the inlet valve forms the venting device.
  • the inlet valve is designed so that thus a connection between the inlet pipe and the
  • Compaction space is closed only from a pressure in the compression chamber, which is at least 0.1 bar, preferably at least 0.2 bar and in particular at least 0.5 bar higher than the pressure in the inlet line, which corresponds substantially to the ambient pressure.
  • a pressure in the compression chamber which is below the limit of at least 0.1 bar, preferably at least 0.2 bar and in particular at least 0.5 bar overpressure, there is a continuing connection between the
  • the inlet valve in which the inlet valve is closed only from a predetermined pressure in the compression chamber, the inlet valve has a concave valve seat in particular on the valve plate and a substantially planar formed valve tongue, so that the valve tongue only after one by a pressure caused in the compression space elastic deformation sealingly against the valve seat.
  • Embodiment closes the inlet valve only when a sufficiently high pressure acts in the compression space during the compression stroke, which deforms the valve tongue so that it bears sealingly against the concave valve seat.
  • the inlet valve is open.
  • the inlet valve in which the inlet valve can be closed only from a predetermined pressure in the compression chamber, the inlet valve has a flat valve seat and a bent valve tongue. Consequently, the valve tongue is sealingly attached to the valve seat only after an elastic deformation caused by the pressure in the compression space. Also in this embodiment, the inlet valve closes only when during a compression stroke, a sufficiently high pressure acts in the compression space, which deforms the bent valve tongue designed such that it sealingly against the newly formed valve seat is applied. Again, the inlet valve remains open as long as the pressure in the compression chamber has a lower value than the pressure, which leads in particular during a compression stroke to close the inlet valve. Thus, even in this embodiment, a compressed gas that passes from the outlet line back into the compression chamber during the separation of the piston compressor from the drive means, leading to any pressure build-up in the compression chamber.
  • Venting device By such a vent channel, which in particular produces a permanent connection to a region with a relation to the compression space lower pressure, in particular ambient pressure, gas from one end of the vent passage in
  • Compression space which is under a higher pressure, are discharged through the vent channel in a region of lower pressure, in particular ambient pressure at the other end of the vent channel.
  • a pressure equalization takes place with the compression chamber. If, therefore, during a separation of the piston compressor from the drive device gas from the pressurized outlet line passes back into the compression space, there can be no increased pressure build up because the gas is discharged through the vent channel.
  • At least one end of the vent passage is disposed in the valve plate and in particular establishes a connection of the compression space to the surroundings of the reciprocating compressor or to its inlet system.
  • a disadvantage of a permanently open venting channel is that it also allows for escape of the gas from the compression chamber during a compression stroke, whereby the efficiency of the compressor is reduced.
  • the vent channel has such a small cross-section that a pressure equalization through the vent channel is possible, the throttling action of the small cross-section of the vent passage but prevents the pressure flow of a larger volume flow during a compression stroke.
  • An alternative design which restricts escape of the gas from the compression space during a compression stroke has a suitable check valve in the vent passage, which closes it from a predetermined overpressure.
  • a suitable check valve is for example a gravity ball valve.
  • such a check valve is robust against a
  • At least one end of the ventilation channel is arranged in the cylinder wall, for example, a connection with the environment of the
  • Piston compressor produces. Starting from the outside of the cylinder wall, the
  • Venting channel having a connection device in the form of a line which serves as an extension of the vent passage and this connects in particular with the inlet system or with the interior of the crankcase of the reciprocating compressor.
  • a venting channel also forms an opening in the compression chamber, through which gas can escape from the compression chamber even during the compression stroke, with the result that the efficiency of the piston compressor drops.
  • Venting channel is therefore designed in particular large enough to equalize the pressure
  • the venting channel is arranged in the cylinder wall so that one end passes from the piston during the compression stroke from a certain piston position and thus is closed. This is the case in particular when the venting channel is arranged between an average stroke position of the piston and its top dead center.
  • a check valve or a check valve is arranged in the venting channel or in a connecting device connected thereto.
  • Such check valve or check valve on the one hand avoid escape of gas during a compression stroke of the piston compressor from the compression chamber, on the other hand, such
  • Check valve or check valve also serve to prevent suction of possibly contaminated gas in particular from the crankcase in the compression chamber.
  • the piston, the cylinder, the cylinder head, etc. have been previously addressed in connection with the components of the reciprocating compressor, the characteristics described herein apply to a reciprocating compressor having two or more of these elements, since the present invention is not limited to single-stage reciprocating compressors but also for multi-stage reciprocating compressors can be used.
  • 1 is a schematic representation of an exemplary reciprocating compressor of the state of
  • FIG. 2 is an illustration of an exemplary exhaust valve as used in piston compressors in the prior art
  • FIG. 3 is a schematic representation of a first exemplary embodiment of a
  • venting device has a switchable valve device
  • FIG. 4 is a schematic representation of a second exemplary embodiment of a
  • venting device has a switchable valve device
  • Fig. 5 is a schematic representation of a third exemplary embodiment of a
  • Fig. 6 is a schematic representation of a fourth exemplary embodiment of a
  • Fig. 7 is a schematic representation of a fifth exemplary embodiment of a
  • FIG. 8 is a schematic representation of a sixth exemplary embodiment of a piston compressor according to the invention, in which the venting a
  • FIG. 9 is a schematic representation of a seventh exemplary embodiment of a
  • FIG. 10 is a schematic representation of an eighth exemplary embodiment of a
  • FIG. 11 is an illustration of a detail of a ninth exemplary embodiment of a
  • Fig. 1 shows a schematic representation of an exemplary reciprocating compressor 10 as known in the art.
  • the crankshaft 11 of the reciprocating compressor 10 is connected via a clutch 3 to a drive device (not shown, here an internal combustion engine) and selectively separable by means of the clutch 3 of this drive device.
  • a drive device not shown, here an internal combustion engine
  • Crankshaft 11 is stopped during the separation of the reciprocating compressor 10 of the drive device.
  • crankshaft 11 is connected to an eccentrically mounted thereon connecting rod 12, on which a piston 13 is mounted.
  • the piston 13 is mounted axially movable in a cylinder 14 of the reciprocating compressor 10.
  • the at least one crankshaft 11, a connecting rod 12 and a piston 13 having
  • crank drive 15 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 so that it performs a lifting movement.
  • the cylinder 14 is closed by a valve plate 20.
  • the cylinder 14, the piston 13 and the valve plate 20 define the compression space 17 in the cylinder 14.
  • an inlet valve 21 is arranged, which is arranged between an inlet line 22 and the compression space 17.
  • the inlet duct 22 is part of an inlet system 23, the fresh air from the environment through a filter (not shown) sucks and via the inlet line 22 through the cylinder head (not shown) to the compression space 17 supplies.
  • the cylinder head is arranged above the valve plate 20 and has a cylinder head volume 24, which communicates via the inlet valve 21 with the compression chamber 17.
  • the inlet valve 21 is designed as a check valve, which allows fresh air to be drawn into the compression space 17, but prevents backflow of the air sucked into the compression space 17 via the inlet line 22.
  • an outlet valve 26 is further arranged, which is arranged between the compression chamber 17 and an outlet 27.
  • compressed gas here air
  • a compressed air storage not shown here supplied.
  • the exhaust valve 26 which is also designed as a check valve, a back flow of compressed air from the
  • FIG. 2 is an illustration of an exemplary exhaust valve 26 commonly used in piston compressors 10 in the prior art.
  • the outlet valve 26 is attached to the valve plate 20 of the
  • Piston compressor 10 is disposed above the compression space 17.
  • the valve plate 20 has an outlet opening 28 which connects the compression space 17 with a cylinder head volume 27 a arranged in valve plate 20 and cylinder head of the piston compressor 10, which forms part of the outlet line 27.
  • the outlet valve 26 has a valve body 26a on a valve tongue, which extends from a
  • the outlet valve 26 further has a contact element 26c arranged above the outlet opening 28, against which the valve tongue 26a bears in the opened state.
  • the pressurized air from the compression chamber 17 can flow through the lateral open areas on the valve tongue 26a and the contact element 26c over into the outlet 27.
  • impurities from the compression chamber 17 or from the cylinder head volume 27a for example, from forming deposits by residues in the air flowing through the hot top of the piston 13, the valve plate 20 or the cylinder head volume 27a solve, - In between the valve tongue 26 a and the valve seat 26 b, there is a risk that the exhaust valve 26 does not close completely. In this case, compressed air from the outlet conduit 27 in the
  • Compression chamber 17 flow back as soon as the pressure in the compression chamber 17 drops below the pressure in the outlet 27.
  • the pressure in the compression chamber 17 drops below the pressure in the outlet 27.
  • Compression chamber 17 of the reciprocating compressor 10 for example, be acted upon by the air flowing back therefrom with a pressure of up to 6 bar.
  • the reciprocating compressor 10 is then reconnected to the drive means, the reciprocating compressor 10 generates one at the first stroke
  • FIG. 3 shows a schematic representation of a first exemplary embodiment of a piston compressor 10 according to the invention.
  • the structure of the piston compressor 10 in FIG. 3 largely corresponds to the construction of the piston compressor 10 shown in FIG. 1 and described in that respect, so that identical elements of the piston compressors 10 are the same Reference signs are designated. In the following, only the differences between the reciprocating compressor 10 from FIG. 3 and the reciprocating compressor 10 from FIG. 1 will be explained.
  • the piston compressor 10 shown in FIG. 3 has a venting device in the form of a 2/2-way valve 31, which is arranged between the compression chamber 17 and the inlet system 23.
  • the 2/2-way valve is a switchable valve device.
  • the control line 31a of the 2/2-way valve 31 is connected to the control of the clutch 3
  • the 2/2-way valve 31 is switched from the illustrated closed position to an open position in order to establish a connection between the compression chamber 17 and the inlet system 23 through which air can flow.
  • FIG. 4 shows a schematic representation of a second exemplary embodiment of a piston compressor 10 according to the invention.
  • the construction of the piston compressor 10 in FIG. 4 corresponds largely to the structure of the piston shown in FIG. 1 and described for this purpose
  • Reciprocating compressor 10 of FIG. 4 compared to the reciprocating compressor 10 of FIG. 1 explained.
  • the piston compressor 10 shown in Fig. 4 has a venting device in the form of a pilot-operated check valve 32, which also serves as an inlet valve.
  • a venting device in the form of a pilot-operated check valve 32, which also serves as an inlet valve.
  • the pilot-operated check valve 32 between the compression chamber 17 and the inlet system 23 is arranged.
  • the unlockable check valve 32 is also also a switchable valve device, which in addition to the automatic opening during the intake of fresh air and by means of a control signal in an open position is switchable.
  • Control device signal connected.
  • the pilot-operated check valve 32 can be opened in order to establish a connection between the compression chamber 17 and the inlet line 22. If, during the standstill of the piston compressor 10, compressed air enters the compression chamber 17, for example in the case of an outlet valve 26 which no longer closes tightly, the pilot-operated check valve 32 can be opened in order to allow pressure equalization with the inlet line 22. Thus, no pressure build-up in the compression chamber 17 take place, which could lead to damage of the reciprocating compressor 10 and / or the clutch 3 in particular during the first compression stroke of the reciprocating compressor 10 when it is restarted.
  • the pilot-operated check valve 32 is switched by the control device back to the working position in which it automatically opens when sucking fresh air from the inlet line 22 into the compression chamber 17 due to the pressure difference applied thereto.
  • FIG. 5 shows a schematic representation of a third exemplary embodiment of a piston compressor 10 according to the invention.
  • the construction of the piston compressor 10 in FIG. 5 corresponds largely to the construction of the one illustrated in FIG. 1 and described for this purpose
  • Piston compressor 10 of FIG. 5 compared to the reciprocating compressor 10 of FIG. 1 explained.
  • the piston compressor 10 shown in FIG. 5 has a venting device in the form of a check valve 33, which is arranged between the compression chamber 17 and the inlet system 23.
  • the check valve 33 arranged in addition to the inlet valve 21 between the compression chamber 17 and the inlet system 23 blocks in the opposite direction to the inlet valve 21, so that this is closed during the intake of fresh air into the compression chamber 17 and during compression during normal operation of the piston compressor 10. If, in the embodiment shown in FIG. 5, compressed air enters the compression chamber 17 during standstill of the piston compressor 10, for example in the case of an outlet valve 26 which no longer closes tightly, a pressure build-up in the compression chamber 17 first takes place here.
  • Piston compressor 10 and / or the clutch 3 can lead.
  • the check valve 33 is therefore designed so that it opens a connection between the compression chamber 17 and the inlet line 21 with a sufficiently large cross section to remove air from the compression chamber 17 as soon as the pressure in the compression chamber 17 exceeds a critical value.
  • Piston compressor 10 for a commercial vehicle is the peak pressure in the compression chamber at
  • An exemplary check valve 33 is therefore so executed that it opens, for example, at a pressure of 20 bar in the compression chamber 17 and thus discharges compressed air from the compression chamber 17.
  • FIG. 6 shows a schematic representation of a fourth exemplary embodiment of a piston compressor 10 according to the invention.
  • the construction of the piston compressor 10 in FIG. 6 also largely corresponds to the structure of the piston shown in FIG. 6
  • Piston compressor 10 of FIG. 6 compared to the reciprocating compressor 10 of FIG. 1 explained.
  • the piston compressor 10 shown in FIG. 6 has a ventilation device in the form of a ventilation channel 34, which is arranged between the compression chamber 17 and the inlet system 23.
  • the venting channel 34 establishes a connection between the compression chamber 17 and the inlet system 23, through which air can flow, so that during a standstill of the piston compressor, no pressure can build up in the compression chamber 17 which is substantially above the ambient pressure.
  • the venting channel 34 is arranged in the region of the valve plate 20 on the upper side of the cylinder 14 so that a continuous pressure equalization with the inlet line 32 of the reciprocating compressor 10 takes place through the venting channel 34. If, during a standstill of the reciprocating compressor 10 compressed air from the outlet 27 passes into the compression chamber 17, takes place through the vent passage 34, a pressure equalization with the inlet line 22 instead, whereby no pressure build-up in the compression chamber 17 can take place.
  • a disadvantage of such a venting channel 34 that this is also during a compression stroke of the
  • Piston compressor 10 is open and escapes to be compressed air from the compression chamber 17 in this phase. This reduces the efficiency of the reciprocating compressor 10.
  • the vent passage 34 is therefore designed so that it has only a small cross section in order to allow a sufficient pressure equalization during the stoppage of the reciprocating compressor 10 with the inlet system 23, but on the other hand has a throttling effect at high pressures, to limit the volume flow of the discharged air.
  • 7 shows a schematic representation of a sixth exemplary embodiment of a piston compressor 10 according to the invention.
  • the construction of the piston compressor 10 in FIG. 7 largely corresponds to the construction of the piston compressor 10 illustrated in FIG. 6 and described in that respect, so that identical elements of the piston compressors 10 are identical Reference signs are designated. In the following, only the differences between the reciprocating compressor 10 from FIG. 7 and the reciprocating compressor 10 from FIG. 6 are explained.
  • FIG. 7 shows a piston compressor 10, which also has a ventilation device in the form of a ventilation channel 39, which is arranged between the compression chamber 17 and the inlet system 23.
  • a check valve in the form of a gravity ball valve 40 is arranged, which closes the vent passage 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 top of the gravity ball valve 40 arranged valve seat.
  • the check valve thus restricts the escape of compressed air from the compression chamber 17 during a compression stroke.
  • FIG. 8 shows a schematic representation of a sixth exemplary embodiment of a piston compressor 10 according to the invention.
  • the construction of the piston compressor 10 in FIG. 8 largely corresponds to the construction of the piston compressor 10 shown in FIG. 6 and described in this regard, so that identical elements of the piston compressors 10 are identical Reference signs are designated. In the following, only the differences between the reciprocating compressor 10 from FIG. 8 and the reciprocating compressor 10 from FIG. 6 are explained.
  • the piston compressor 10 shown in FIG. 8 also has a ventilation device in the form of a ventilation channel 35, which is arranged between the compression chamber 17 and the inlet system 23.
  • the ventilation channel 35 is arranged in the upper region of the wall of the cylinder 14.
  • the venting channel 35 also establishes a connection between the compression chamber 17 and the cylinder head volume 24, through which air can flow, which allows pressure equalization between the compression chamber 17 and the inlet system 23.
  • vent passage 35 may be disposed approximately in the region which the upper piston ring sweeps about 60 ° before the top dead center of the piston 13. This will during the stoppage of the reciprocating compressor 10, a discharge of compressed air from the
  • Compressing space 17 is reached, which passes from the outlet 27 there, while the
  • Piston compressor 10 is disconnected from the drive device. At the same time, however, the air in the compression space 17 is prevented from escaping during the final phase of the compression stroke.
  • FIG. 9 shows a schematic illustration of a seventh exemplary embodiment of a piston compressor 10 according to the invention.
  • the construction of the piston compressor 10 in FIG. 9 largely corresponds to the structure of the piston compressor 10 illustrated in FIG. 8 and described in this regard, so that identical elements of the piston compressors 10 are identical Reference signs are designated. In the following, only the differences between the reciprocating compressor 10 from FIG. 9 and the reciprocating compressor 10 from FIG. 8 will be explained.
  • the piston compressor 10 shown in FIG. 9 has a venting device in the form of a venting channel 36, which is arranged between the compression chamber 17 and the interior of the crankcase 16. As in the case of the piston compressor 10 from FIG. 8, the ventilation channel 36 is arranged in the upper region of the wall of the cylinder 14. This one is air-permeable
  • crankcase 16 of the reciprocating compressor 10 allows pressure equalization with respect to the environment, there is substantially ambient pressure in its interior. This can be done via the vent passage 36, a pressure equalization between the compression chamber 17 and the crankcase 16.
  • FIG. 10 shows a schematic representation of an eighth exemplary embodiment of a piston compressor 10 according to the invention.
  • the construction of the piston compressor 10 in FIG. 10 largely corresponds to the structure of the piston compressor 10 shown in FIG. 9 and described in that respect, so that identical elements of the piston compressors 10 are identical Reference signs are designated. In the following, only the differences between the reciprocating compressor 10 from FIG. 10 and the reciprocating compressor 10 from FIG. 9 will be explained.
  • the piston compressor 10 shown in Fig. 10 has a venting device in the form of a vent passage 37 which, corresponding to the vent passage 36 of FIG. 9 between the
  • Compression chamber 17 and the interior of the crankcase 16 is arranged. Compared to the
  • a check valve 38 is disposed in the vent passage 37, which prevents backflow of air from the crankcase 16 in the compression chamber 17.
  • the check valve 38 may be designed so that it opens at a low pressure difference between the pressure in the compression chamber 17 and the pressure in the crankcase 16 to prevent pressure build-up in the compression chamber 17 during a service life of the reciprocating compressor 10.
  • FIG. 11 is an illustration of a detail of a ninth exemplary embodiment of a reciprocating compressor 10 according to the present invention, in which the intake valve 21 constitutes the venting means.
  • the elements of the inlet valve 21 are shown in exploded view in FIG. 11.
  • Intake valve 21 forms the upper end of the compression space 17 in the cylinder 14.
  • the valve tongue 21a is formed integrally with a first element of the intake valve 21, which is disposed between the cylinder 14 and a abutment member 21b of the intake valve 21.
  • the exemplified investment element 21b has two valve openings 21c, which depends on the
  • the valve tongue 21a has a curvature which is designed such that the valve tongue 21a rests against the contact element 21b from a pressure in the compression space 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 (FIG. Ambient pressure) while closing the valve openings 21c.
  • a pressure difference of less than 0.4 bar the valve tongue 21a always has a curvature that a connection between the inlet system 23 and the compression chamber 17 is made.
  • a compressed gas that has entered the compression space 17 through the valve openings 21 c of the intake valve 21 in the
  • Inlet pipe 22 can be discharged without a pressure build-up in the compression chamber 17 of the compressor 10 takes place.
  • the inlet valve 21 may also have a contact element 21b, which has a recess in the region of the valve openings 21c, so that the valve tongue 21a also in this

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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)

Abstract

L'invention concerne un compresseur à piston servant à comprimer un gaz, qui peut éventuellement être séparé d'un dispositif d'entraînement au moyen d'un dispositif d'accouplement. Le compresseur à piston comprend une soupape d'admission disposée entre une conduite d'admission pour le gaz à comprimer et une chambre de compression du compresseur à piston, et une soupape de sortie qui est disposée entre la chambre de compression du compresseur à piston et une conduite de sortie pour le gaz comprimé. Le compresseur à piston selon l'invention comprend en outre un dispositif de dégazage permettant d'évacuer le gaz comprimé présent dans la chambre de compression.
PCT/EP2017/051406 2016-01-27 2017-01-24 Compresseur à piston équipé d'un dispositif de dégazage WO2017129553A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
CN201780020387.9A CN108884820B (zh) 2016-01-27 2017-01-24 具有排气装置的活塞式压缩机
KR1020187024477A KR20180105211A (ko) 2016-01-27 2017-01-24 배기 장치를 포함하는 피스톤 압축기
EP17701320.8A EP3408536B1 (fr) 2016-01-27 2017-01-24 Compresseur à piston équipé d'un dispositif de dégazage
BR112018015262-5A BR112018015262B1 (pt) 2016-01-27 2017-01-24 Compressor de pistão para comprimir um gás
JP2018539067A JP2019503453A (ja) 2016-01-27 2017-01-24 空気抜き装置を備えるピストンコンプレッサ
US16/047,854 US20180372087A1 (en) 2016-01-27 2018-07-27 Piston Compressor Having a Venting Device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016201208.8 2016-01-27
DE102016201208.8A DE102016201208B4 (de) 2016-01-27 2016-01-27 Kolbenkompressor mit Entlüftungseinrichtung

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US16/047,854 Continuation US20180372087A1 (en) 2016-01-27 2018-07-27 Piston Compressor Having a Venting Device

Publications (1)

Publication Number Publication Date
WO2017129553A1 true WO2017129553A1 (fr) 2017-08-03

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PCT/EP2017/051406 WO2017129553A1 (fr) 2016-01-27 2017-01-24 Compresseur à piston équipé d'un dispositif de dégazage

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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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US20200191138A1 (en) * 2018-12-12 2020-06-18 Danfoss Power Solutions Inc. Hydrostatic system providing volumetric efficiency when pump is neutral

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US10371132B2 (en) * 2017-02-10 2019-08-06 Peopleflo Manufacturing, Inc. Reciprocating pump and transmission assembly having a one-way clutch
KR102674603B1 (ko) 2018-09-04 2024-06-12 현대모비스 주식회사 차량용 led 램프 장치
DE102018128111A1 (de) 2018-11-09 2020-05-14 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Gehäuse sowie Kompressor und Kompressor-Einheit mit einem solchen Gehäuse
CN110953138A (zh) * 2019-11-19 2020-04-03 张金强 利用水车提高水位的水力空气压缩机

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CN108980047B (zh) * 2018-08-27 2024-07-05 珠海凌达压缩机有限公司 气缸及压缩机
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Also Published As

Publication number Publication date
EP3408536A1 (fr) 2018-12-05
DE102016201208B4 (de) 2024-01-11
US20180372087A1 (en) 2018-12-27
EP3408536B1 (fr) 2021-06-02
KR20180105211A (ko) 2018-09-27
BR112018015262A2 (pt) 2018-12-18
CN108884820B (zh) 2020-07-31
JP2019503453A (ja) 2019-02-07
DE102016201208A1 (de) 2017-07-27
CN108884820A (zh) 2018-11-23

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