EP2757264A2 - Unité de compresseur et système de compresseur doté de celle-ci - Google Patents

Unité de compresseur et système de compresseur doté de celle-ci Download PDF

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Publication number
EP2757264A2
EP2757264A2 EP14000124.9A EP14000124A EP2757264A2 EP 2757264 A2 EP2757264 A2 EP 2757264A2 EP 14000124 A EP14000124 A EP 14000124A EP 2757264 A2 EP2757264 A2 EP 2757264A2
Authority
EP
European Patent Office
Prior art keywords
pressure
compressor unit
compressor
relief
piston
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.)
Withdrawn
Application number
EP14000124.9A
Other languages
German (de)
English (en)
Other versions
EP2757264A3 (fr
Inventor
Alfred Deubler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Duerr Dental SE
Original Assignee
Duerr Dental SE
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 Duerr Dental SE filed Critical Duerr Dental SE
Publication of EP2757264A2 publication Critical patent/EP2757264A2/fr
Publication of EP2757264A3 publication Critical patent/EP2757264A3/fr
Withdrawn legal-status Critical Current

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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
    • F04B39/0027—Pulsation and noise damping means
    • 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
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/02—Pumping installations or systems specially adapted for elastic fluids having reservoirs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • F04B49/035—Bypassing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B49/22—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 means of valves
    • F04B49/24—Bypassing
    • F04B49/243—Bypassing by keeping open the inlet valve

Definitions

  • Such compressor units are known as piston compressors.
  • piston compressors In known from the market compressor units and Compressor systems has the difficulty that the piston actuators used, for example, single-phase AC capacitor motors, only produce a limited starting torque and therefore can not start well against pressure.
  • the piston drive is cyclically activated and deactivated in a known manner as a function of the pressure prevailing in the pressure accumulator and the start-up procedure proceeds correspondingly frequently, a load-free starting is desirable.
  • this type of pressure relief is not abrupt, so that at the outlet of the compressor unit and thus at the working space still largely the operating pressure of the compressor system is applied when the piston expires without drive. This means that the piston is decelerated very quickly by the applied pressure. Depending on the applied pressure and the mass ratios of the installed components, it may happen, for example, that a motor shaft of the piston drive from an operating speed between 1400 and 2800 min -1 in less than half a revolution is slowed down to a standstill.
  • the invention is based on the recognition that a pressure relief can also take place from the working space at the outlet valve assembly, so that the piston expire without load can. In particular, it does not cause a noise, since no pressure must be drained. In this case, the pressure relief in contrast to known systems, in particular on the suction side of the compressor unit.
  • the pressure in the pressurized lines between the outlet of the compressor unit and the accumulator can be maintained, so that the compressor system is also quickly back to operating pressure.
  • the discharge flow path can also be kept open at the start of the piston and only be locked when the piston drive has reached its operating speed. Thus, the piston does not have to work against the pressure applied to the outlet when starting up.
  • the relief device comprises a relief valve arrangement in the relief flow path which assumes an open configuration during a compression stroke of the piston.
  • the discharge flow path can be selectively enabled or disabled by a corresponding control of the relief valve assembly.
  • the relief valve assembly When the relief valve assembly is formed by the inlet valve assembly, advantageously no additional components need to be installed.
  • the relief valve assembly may be a separate relief valve assembly that operates independently of the inlet valve assembly.
  • the compressor unit comprises an adjusting device, by means of which the relief valve arrangement can be brought into an open configuration such that the open configuration is maintained during a compression stroke of the piston.
  • the adjusting device operates pneumatically and has a pressure medium input.
  • the adjusting device can also be operated magnetically or mechanically.
  • the adjusting device comprises a movable actuator, by which a valve body of the relief valve assembly can be brought into an open position.
  • the actuator can be moved for example by a Bowden cable or the like.
  • a technically advantageous solution is when the relief valve assembly is designed as a leaf spring valve and the valve body as a leaf spring.
  • a leaf spring can be pushed away from an otherwise closed opening in a relatively simple manner and optionally held in this open position.
  • the compressor unit is a compressor unit according to one of claims 5 to 9, i. in particular, that it operates pneumatically, and a flow path from the pressure line or from the pressure accumulator to the pressure medium input of the adjusting device can be produced or blocked.
  • a control valve is provided, through which the flow path from the pressure line or from the pressure accumulator to the pressure medium input of the actuating device can be produced or blocked and which can assume a control position or a blocking position for this purpose.
  • the applied pressure in the pressurized lines pressure can be used to operate the actuator. There is no separate supply to operate the actuator required.
  • control valve is a 2/2-way valve and the adjusting device comprises a pressure release opening through which pressure medium can flow out of the adjusting device. This will be discussed in more detail below.
  • control valve is a 3/2-way valve and locks in its blocking position the flow path from the pressure line to the pressure medium input of the actuator and also connects the pressure medium input of the actuator with a largely pressure-free pressure relief output. This will also be explained in more detail below.
  • the compressor unit comprises the separate relief valve arrangement and a pressure control is provided by which the pressure in the pressure accumulator can be detected and which controls the separate relief valve arrangement such that it assumes its discharge position when the pressure in the accumulator exceeds a predetermined threshold , In this case, can be dispensed with an additional control valve on the accumulator.
  • the separate relief valve assembly is formed as a responsive 2/2-way valve.
  • FIG. 1 Reference is made showing a section of a gaseous working fluid compressor unit 10 used in compressor systems 12, 14, or also 128, 134 and 136, which in turn are incorporated in the FIGS. 4 and 5 and Figures 6 and 7 and 8, respectively, are discussed in more detail below.
  • the compressor unit 10 are shown schematically and only the essential components here.
  • the compressor unit 10 is designed as a compressed air compressor 16 and serves to provide compressed air as a working fluid for dental, medical or technical applications.
  • the pneumatic compressor 16 comprises a cylinder arrangement with a cylinder housing 18, in which a cylinder 20 is housed, which on an end face 22 to a crankcase 24 is open, which is connected to the cylinder housing 18.
  • a piston 26 is movable by means of a piston drive 28.
  • the piston drive 28 comprises in a manner known per se a connecting rod 30, which is coupled at one end to the piston 26 and at the opposite end with an eccentric 32.
  • the eccentric 32 is arranged in the crankcase 24 and in turn sits non-rotatably on a motor shaft 34 of an electric motor 36, which need not be further explained otherwise.
  • a cylinder inlet port 40 and a cylinder outlet port 42 are present, wherein the cylinder outlet port 42 due to the cut is not in the FIGS. 1 to 3 , but in the FIGS. 4 and 5 can be seen.
  • the end wall 38 of the cylinder 20 is formed in the present embodiment by a portion of the cylinder housing 18, that is, the cylinder 20 is hereby made as a cylinder sleeve.
  • the end wall 38 may also belong to the cylinder 20 itself, as it is a modification in the FIGS. 4 and 5 is illustrated. In this case, the cylinder 20 is cup-shaped.
  • a working chamber 44 of the cylinder 20 is now formed, the volume of which depends on the position of the piston 26 in the cylinder 20 and which is limited radially by the inner circumferential surface of the cylinder 20.
  • the cylinder inlet port 40 is connected via an intake passage 46 with the interior of the crankcase 24 of the pneumatic compressor 16.
  • a cylinder inlet port 48 is in the present embodiment by a in the crankcase 24 built-filter housing formed in which a particulate filter is installed. The suction takes place through this filter and the interior of the crankcase 24 to the intake passage 46.
  • the cylinder outlet port 42 leads via a discharge channel 50 to an outlet formed as outlet 52, the former only in the FIGS. 4 and 5 can be seen.
  • the cylinder inlet port 40 and the intake port 46 are thus portions of a flow path 54 between the inlet port 48 and the working space 44 of the cylinder 20, while the cylinder outlet port 42 and the discharge channel 50 are portions of a flow path 56 between the working space 44 and the outlet port 52 ,
  • an inlet valve assembly 58 is arranged in the flow path 54. This forms a check valve 60, which opens in the flow direction to the working space 44 and closes in the direction of the inlet port 48 through.
  • the check valve 60 is formed as a leaf spring valve 62 with a leaf spring 64 which abuts from the inside to the cylinder inlet port 40, as it is known per se.
  • an outlet valve arrangement 66 is arranged in the flow path 56 between the working space 44 and the outlet connection 52.
  • the check valve 68 is formed as a leaf spring valve 70 with a leaf spring 72 as a valve body, which rests in a manner known per se from the outside to the cylinder outlet opening 42.
  • Air is thus in a manner known per se during an intake stroke of the piston 26 on a path via the inlet valve assembly 58 is sucked into the working space 44 and pressed on a compression stroke of the piston 26 via the outlet valve assembly 66 out of the working space 44, wherein the inlet valve assembly 58 and the outlet valve assembly 66 are in opposite directions in an open and a closed configuration.
  • the compressor unit 10 further comprises a relief device 74, by means of which a discharge flow path 76 can be produced, can flow through the working fluid during a compression stroke of the piston at the outlet valve assembly 66 over from the working space 44.
  • the relief device 74 By the relief device 74, the relief flow path 76 between the working chamber 44 of the cylinder 20 and a discharge outlet 78 can be made and kept open for a predetermined period.
  • the relief device 74 is in the Figures 2 and 3 to recognize on a larger scale; For the sake of clarity, the associated components are also provided there only with reference numerals.
  • the relief port 78 is formed through the inlet port 48 and the relief flow path 76 through the flow path 54 between the cylinder inlet port 40 and the inlet port 48.
  • the relief device 74 comprises an adjusting device 80, through which the flow path between the cylinder inlet port 40 and the crankcase 24 can be opened and kept open for a predeterminable period.
  • an actuator 82 which is adjustable between a neutral position and a relief position.
  • the actuator 82 does not act on the leaf spring 64 and releases it so that it can open the cylinder inlet port 40 during a suction stroke of the piston 26 and close at a compression stroke of the piston 26.
  • the actuator 82 presses against the leaf spring 64 of the inlet valve assembly 58 such that it is held in an open position in which the cylinder inlet port 40 is released (see. FIG. 3 ).
  • the flow path 54 between the working chamber 44 and the crankcase 24 and thus the inlet port 48 is permanently open in this case and the discharge flow path 76 is established, whereby the piston 26 can move freely in the cylinder 20.
  • neutral position means all positions of the actuator 82 in which it does not affect the inlet valve assembly 58.
  • the inlet valve assembly 58 thus forms a relief valve assembly 59 disposed in the relief flowpath 76.
  • the relief valve assembly 59 may be brought into its open configuration by the actuator 80 such that the open configuration is maintained even during a compression stroke of the piston 26.
  • the actuator 82 comprises in the present embodiment, a control piston 84 which is guided in a control cylinder 86 of the adjusting device 80, and connected to the actuating piston 84 control rod 88 which protrudes outwardly from the control cylinder 86.
  • the control rod 88 is retracted in the neutral position of the actuator 82 of the leaf spring 64 away in the control cylinder 86, while it is extended in the relief position of the actuator 82 in contrast from the control cylinder 86.
  • the actuating piston 84 is spring-loaded by a spring 90 such that the actuator 82 is held in its neutral position without further force or, if appropriate, initially moved into its neutral position.
  • control cylinder 86 In order to bring the actuator 82 in its discharge position, the control cylinder 86 is connected via a control channel 92 with a pressure medium input 94, via which a pressure chamber 96 (see. FIG. 3 ) of the control cylinder 86 can be acted upon on the remote from the control rod 88 side of the actuating piston 84 with compressed air, which then acts on the control piston 84. As a result, the actuator 82 is moved against the force of the spring 90 from the neutral position to the discharge position.
  • the actuator 82 Without compressed air supply to the control cylinder 86, the actuator 82 is held by the spring force of the spring 90 in its neutral position or moves, if necessary, previously from its discharge position initially back in its neutral position.
  • the actuator 82 is thus operated pneumatically.
  • the actuator 82 may also be moved electromagnetically or mechanically, for example by means of a Bowden cable.
  • the compressor unit 10 is part of a compressor system 12, which in FIG. 4 is illustrated in which the compressor unit 10 in the form of the pneumatic compressor 16 is shown again schematically.
  • Its outlet nozzle 52 is connected via a pressure line 98 to a pressure accumulator 100, from which compressed air can be removed via a removal connection 102.
  • a check valve 104 is arranged, which closes in the direction of the compressed air compressor 16 out.
  • the pressure line 98 is connected via a branch line 106 with a control valve 108, which can assume a control or a blocking position.
  • the branch line 106 is connected to a control line 112, which leads to the pressure medium input 94 of the discharge device 74.
  • the blocking position of the control valve 108 the branch line 106 is blocked.
  • the control valve 108 is designed as a 2/2-way valve 110.
  • a flow path which is formed here by the branch line 106 and the control line 112, from the pressure line 98 to the pressure medium input 94 of the adjusting device 80 are made or blocked.
  • Its control cylinder 86 has a pressure release opening 114 in the compressor system 14, via which the pressure chamber 96 of the control cylinder 86 is open to the environment.
  • the pressure release opening 114 leads to a throttle 115, which allows a controlled outflow of the control air; As a result, the pressure in the pressure line 98 is slowly degraded.
  • the electric motor 36 is activated. Now air is in an intake stroke of the piston 26 via the inlet port 48 and the crankcase 24 and the intake passage 46 is sucked into the working chamber 44 and discharged in a compression stroke of the piston 26 from the working space 44 on the way through the outlet valve assembly 66, the discharge channel 50, the outlet port 52 and the pressure line 98 into the pressure accumulator 100.
  • a working pressure builds up in a known manner, which is detected by the pressure sensor 118 of the pressure control 116.
  • the pressure control 116 is adjusted so that the control valve 108 is brought into the control position and only then back into the blocking position when the pressure in the pressure vessel 100 drops below its predetermined threshold and the electric motor 36 is activated again.
  • the diameter of the pressure relief opening 114 is selected such that it is possible, on the one hand, to build up a pressure in the pressure chamber 96 sufficient to move the actuator 82 into its unloaded position, and, on the other hand, the outflow of compressed air from the pressure chamber 96 to take place so slowly in that the cylinder inlet opening 40 is kept permanently open so long that the piston 26 is able to leak freely until it is at a standstill.
  • a corresponding opening for example in the form of a pressure release nozzle, may also be provided elsewhere, for example in the control line 112.
  • the relief flow path 76 is thus again disabled and the inlet valve assembly 58 can again function in its basic function. If now the working pressure in the pressure accumulator 100 drops to a lower, predetermined threshold value, the electric motor 36 is reactivated and the pressure in the pressure accumulator 100 rebuilt; wherein the control valve 108, as mentioned above, has been brought back into its blocking position.
  • FIG. 5 shown compressor system 16 is opposite to the compressor system 14 after FIG. 4 slightly modified.
  • the control cylinder 86 has no pressure release opening 114.
  • the control valve 108 locks in its blocking position not only the branch line 106, but connects in this blocking position at the same time the control line 112 with a largely pressure-free pressure relief outlet 122, which in the present case is open to the environment.
  • the control valve 108 is formed in this embodiment as a 3/2-way valve 124.
  • a silencer 126 may be provided at the pressure release port 122.
  • the compressor system 16 after FIG. 5 basically works the same way as the compressor system 14 FIG. 4 , Only the pressure reduction from the pressure chamber 96 of the actuating cylinder 86 takes place here in other ways, after the discharge flow path 76 has been established.
  • the pressure chamber 96 of the actuating cylinder 86 is connected via the control line 112 to the pressure relief output 122, so that Air from the control cylinder 86 can flow back through the control line 112, whereby the pressure in the pressure chamber 96 of the control cylinder 86 decreases and the actuator 82 moves back to its neutral position.
  • the compressed air in the pressure chamber 96 can flow off sufficiently slowly after the start of the electric motor 36. This ensures that the inlet valve assembly 58 is released only delayed and the compressor unit 10 starts without pressure, as is the case when leaving.
  • the pressure-free start-up also requires less engine power at startup. Under certain circumstances, an electric motor 36 with a lower power consumption can be used.
  • control valve 108 in the present case in the form of the 2/2-way valve 110 or the 3/2-way valve 124, briefly brought into its control position and then back into its blocking position, whereby air from the working space 44th first acts on the actuator 82 and the cylinder inlet port 40 is opened.
  • the piston 26 can then be moved without load when the discharge flow path 76 is open in the further start-up procedure, until the electric motor 36 has reached a certain operating speed.
  • FIG. 6 shows a yet modified compressor system 128.
  • the control valve 108 is formed as a responsive 3/2-way valve 132, which occupies the control position as the starting position; in this is the connection line 128 with the control line 112 connected, which leads to the pressure medium input 94 of the discharge device 74.
  • the control valve 108 locks in this embodiment, on the one hand, the connecting line 128 and on the other hand connecting the control line 112 to the pressure relief output 122, as it also in the compressor system 14 after FIG. 5 the case is.
  • control valve 108 establishes a connection between the pressure vessel 100 and the discharge device 74 in its rest position, the actuator 82 remains in its extended position until the pressure in the pressure vessel 100 is below the predetermined pressure threshold.
  • a direct switching 3/2-way valve can also be used.
  • the pressure relief after switching back via a mechanical throttle nozzle so that the pressure in the control cylinder 96 slowly degrades after the start of the electric motor 36 and the suction valve for automatic opening and closing releases again.
  • FIGS. 7 and 8th each show a compressor system 134 and 136 and a respective modified compressor unit 10, in which the relief device 74 instead of the inlet valve assembly 58 each comprise a separate relief valve assembly 138 with a pressure medium input 94 which operates independently of the inlet valve assembly 58.
  • the relief valve assembly 138 is actuated there.
  • the relief flow path 76 also has a course independent of the flow path 54, and the relief outlet 78 is separate and no longer formed through the inlet port 48.
  • compressor system 134 is this instead of the control cylinder 86 with the actuator 82, a pressure-controlled 2/2-way valve 140 is provided, which is connected via the discharge outlet 78 directly to the working chamber 44 and driven by the control valve 108 in the form of responsive 3/2-way valve 132 in flow-rest position becomes.
  • the relief valve assembly 138 In its neutral position, the relief valve assembly 138 closes the relief outlet 78. In the relief position, the relief valve assembly 138 connects the relief valve assembly 78 to a relief conduit 142 which is open to the atmosphere and in which a muffler 144 may again be located.
  • compressor system 136 shown comprises the relief valve assembly 138 instead of the 2/2-way valve 140 a responsive 2/2-way valve 146.
  • a responsive 2/2-way valve 146 can be dispensed with the control valve 108 at the pressure accumulator 100; Rather, the An Anlagenverzögerte 2/2-way valve 146 is connected via the pressure control 116 to the pressure accumulator 100.
  • the 2/2-way responsive valve 146 is placed in its unloaded position and the compressor unit 10 can leak pressure-relieved.
  • the pressure relief of the working space 44 takes place on the suction side of the compressor unit 10.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Dental Tools And Instruments Or Auxiliary Dental Instruments (AREA)
  • Compressor (AREA)
EP14000124.9A 2013-01-16 2014-01-14 Unité de compresseur et système de compresseur doté de celle-ci Withdrawn EP2757264A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102013000623.6A DE102013000623A1 (de) 2013-01-16 2013-01-16 Verdichtereinheit und Kompressorsystem mit einer solchem

Publications (2)

Publication Number Publication Date
EP2757264A2 true EP2757264A2 (fr) 2014-07-23
EP2757264A3 EP2757264A3 (fr) 2016-09-21

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Application Number Title Priority Date Filing Date
EP14000124.9A Withdrawn EP2757264A3 (fr) 2013-01-16 2014-01-14 Unité de compresseur et système de compresseur doté de celle-ci

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EP (1) EP2757264A3 (fr)
DE (1) DE102013000623A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017186416A1 (fr) * 2016-03-21 2017-11-02 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Compresseur à piston comportant un dispositif de fermeture pour la conduite de sortie

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Publication number Priority date Publication date Assignee Title
DE102023128426A1 (de) * 2023-10-17 2025-04-17 Bitzer Kühlmaschinenbau Gmbh Kältemittelverdichter

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JPS5812861A (ja) * 1981-07-17 1983-01-25 Diesel Kiki Co Ltd 自動車用エア配管系の圧力制御装置
DE3136949A1 (de) * 1981-09-17 1983-03-31 Wabco Westinghouse Fahrzeugbremsen GmbH, 3000 Hannover Einrichtung zur erzeugung von druckgas
DE3214713A1 (de) * 1982-04-21 1983-10-27 Wabco Westinghouse Fahrzeugbremsen GmbH, 3000 Hannover Einrichtung zur erzeugung von druckgas
DE3329790C2 (de) * 1983-08-18 1995-11-30 Wabco Gmbh Ventilträger für Kolbenverdichter
US6109886A (en) * 1997-10-02 2000-08-29 Wabco Gmbh Compressed-air supply installation with reduced idling power
DE19850269A1 (de) * 1998-10-31 2000-05-04 Wabco Gmbh & Co Ohg Gasverdichter
US7153106B2 (en) * 2003-01-16 2006-12-26 R. Conrader Company Air compressor unit inlet control

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017186416A1 (fr) * 2016-03-21 2017-11-02 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Compresseur à piston comportant un dispositif de fermeture pour la conduite de sortie
CN108934172A (zh) * 2016-03-21 2018-12-04 克诺尔商用车制动系统有限公司 具有用于排气管路的关闭装置的活塞式压缩机
JP2019510164A (ja) * 2016-03-21 2019-04-11 クノル−ブレムゼ ジステーメ フューア ヌッツファールツォイゲ ゲゼルシャフト ミット ベシュレンクテル ハフツングＫｎｏｒｒ−Ｂｒｅｍｓｅ Ｓｙｓｔｅｍｅ ｆｕｅｒ Ｎｕｔｚｆａｈｒｚｅｕｇｅ ＧｍｂＨ 排出管路用の閉鎖装置を備えるピストンコンプレッサ
CN108934172B (zh) * 2016-03-21 2020-07-31 克诺尔商用车制动系统有限公司 具有用于排气管路的关闭装置的活塞式压缩机

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EP2757264A3 (fr) 2016-09-21
DE102013000623A1 (de) 2014-07-17

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