EP2984347B1 - Dispositif destiné à l'économie de puissance dans un compresseur à piston - Google Patents

Dispositif destiné à l'économie de puissance dans un compresseur à piston Download PDF

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Publication number
EP2984347B1
EP2984347B1 EP14715843.0A EP14715843A EP2984347B1 EP 2984347 B1 EP2984347 B1 EP 2984347B1 EP 14715843 A EP14715843 A EP 14715843A EP 2984347 B1 EP2984347 B1 EP 2984347B1
Authority
EP
European Patent Office
Prior art keywords
suction
valve
pressure
cylinder head
lamella
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.)
Not-in-force
Application number
EP14715843.0A
Other languages
German (de)
English (en)
Other versions
EP2984347A1 (fr
Inventor
Jörg MELLAR
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.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer 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 fuer Nutzfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Publication of EP2984347A1 publication Critical patent/EP2984347A1/fr
Application granted granted Critical
Publication of EP2984347B1 publication Critical patent/EP2984347B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B49/22—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
    • F04B49/225—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 with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • 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
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0003—Piston machines or pumps characterised by having positively-driven valving the distribution member forming both the inlet and discharge distributor for one single pumping chamber
    • F04B7/0007—Piston machines or pumps characterised by having positively-driven valving the distribution member forming both the inlet and discharge distributor for one single pumping chamber and having a rotating movement
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0042—Piston machines or pumps characterised by having positively-driven valving with specific kinematics of the distribution member
    • F04B7/0046—Piston machines or pumps characterised by having positively-driven valving with specific kinematics of the distribution member for rotating 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
    • F04B39/08—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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0057—Mechanical driving means therefor, e.g. cams
    • F04B7/0061—Mechanical driving means therefor, e.g. cams for a rotating member

Definitions

  • the invention relates to a device for power saving in a reciprocating compressor, in particular for compressed air generation in a motor vehicle, with a piston arranged axially movable in a cylinder for generating compressed air, which passes through at least one intake valve for compressing into a compression chamber of the cylinder, wherein the intake valve with pressure-controlled means for power saving cooperates.
  • the field of application of the invention extends primarily to reciprocating compressors for motor vehicle construction, in particular commercial vehicle construction, which are primarily used for generating compressed air for compressed air systems in the motor vehicle.
  • the pressure valve opens at the top of the valve plate as before at a certain pressure level. Compressed air enters the pressure regulator from the pressure chamber where it is blown off to the atmosphere via a relief valve.
  • the lubricating oil present in the crankcase has an increased tendency to creep upwardly along the piston rings due to the reduced pressure level in the compression space, so that the lubricating oil can eventually enter the compression space and contribute to an increased accumulation in the air with lubricating oil , With prolonged operation at high temperatures, consequently, increased carbon accumulation is to be accepted.
  • the suction valve has a serving to hold open the same actuating mechanism.
  • This is a plunger which acts on the suction valve and carries a piston which can be acted upon by the pressure of the pressure vessel connected to the compressor, such that the plunger is displaced through the piston when a pressure threshold is exceeded and the suction valve is accordingly opened.
  • a check valve is provided in the suction line thereof, which opens when a negative pressure in the suction line, to suck air into the reciprocating compressor.
  • the pressure valve of the reciprocating compressor is unaffected by the operation of the suction valve, which is constantly in the ready state, so that even in idle position of the suction valve always a certain compression work is done.
  • the pressure valve opens at a certain pressure level, thereby performing compressor work.
  • pressure levels in the compression chamber is also in constructions of this kind the Problem that the lubricating oil along the piston rings can go up, ie in the compression space and thus enriching the air with lubricating oil is given.
  • due to the non-return valve throttle losses which adversely affect the efficiency of the compressor.
  • the object of the present invention is to provide a device for power saving in a reciprocating compressor with which as complete as possible power savings is achieved in the shutdown or idling phase, and that unnecessarily reach lubricating oil from the crankcase in the compression chamber and there An oil enrichment of the air in the suction line can contribute.
  • the invention includes the technical teaching that the actuating means the suction plate of the valve plate so coordinated actuated that it at least partially closes the at least one pressure valve opening in the valve plate or a comparable component in the idle position and simultaneously releases adjacent Saugventilquer4.000e and the suction port on the cylinder head cover or a shut off comparable component by means of a slider or the like to form an increased harmful space in the region of the cylinder head.
  • the suction blade can be moved as a sliding or rotary blade by means of the actuating means under control of a pressure regulator or otherwise provided control signal from its working position to the idle position, in which the at least one suction port is either partially or completely exposed, such that the in the air sucked in the compression chamber can flow back into the suction chamber.
  • the achievable power savings is on the order of about 60%.
  • the solution according to the invention ensures that no unnecessary volume of air is displaced on the pressure side of the compressor. It is also prevented in particular in parallel to the suction line of the reciprocating compressor turbochargers or compressors that occur in these by sucking air laden with lubricating oil under the action of high temperatures coking. Furthermore, the efficiency of the compressor in the delivery phase is not adversely affected by the inventive solution, so it throttle losses are avoided.
  • the suction lamella is designed so that it works without friction. As a result, no wear between the suction plate and the valve plate occurs even with very little lubricating oil in the compression chamber. This design is therefore particularly suitable for oil-reduced compressors as well as for oil-free compressor types.
  • the suction plate is formed so that in the idle phase, the pressure openings are completely or partially closed as needed. An unnecessary displacement of a volume fraction of air in the pressure chamber therefore does not take place. Only if a certain amount of residual air to avoid icing or contamination is desired, a partial opening of the pressure openings in the valve plate is set. In addition, by closing the suction port creates a certain back pressure in the compression chamber, which helps that the lubricating oil is retained from the crankcase. The partial or complete covering of the suction openings thus contributes to a further optimization in the achievable power saving.
  • the actuating means which are preferably pneumatically actuated for adjusting the suction lamella and the slide, act in a preferred embodiment of the invention substantially parallel to the plane of the valve plate and have an actuating piston which can be acted upon by a control pressure.
  • the actuating piston can be guided in a bore of the cylinder head cover, which can be formed by casting in the cylinder head cover.
  • the actuating piston acts by means of a driving pin extending through the bore, both on an actuating member rotating the suction lamella between the working and idle position and on the slide closing the suction connection.
  • the closing the suction port in the cylinder head cover slide is designed according to a preferred embodiment as a hinged thereto pivoting slide and lies within the cylinder head cover.
  • the slider is furthermore preferably provided with a minimum air valve in the region closing off the suction connection.
  • the minimum air valve acting as a check valve is a lamellar valve which consists of a minimum air valve catcher with a valve lamella cooperating therewith as a breakthrough on one end side of the pusher.
  • the plurality of suction openings formed in the valve plate are arranged in a circular ring and can be closed with a disk-shaped as a rotary blade with openings and recesses formed suction lamella.
  • a plurality formed in the valve plate pressure valve cross-sections can be arranged in an annular shape, which open inside the cylinder cover in a pressure chamber with connection to the pressure line, which are alternately closed with the disc-shaped suction plate.
  • These pressure valve cross-sections interact with a pressure-valve unit arranged inside the cylinder head, preferably consisting of pressure-valve catch, pressure-valve spring and pressure-valve lamella.
  • a piston compressor for producing compressed air essentially consists of a piston 100, which is articulated to a driven crankshaft 300 via a connecting rod 200.
  • the crankshaft 300 is rotatably mounted in a crankcase 400.
  • the crankcase 400 includes a cylinder which together with the piston 100 forms a compression space 500, which is provided on the front side with a cylinder head 600, which is shown here only schematically, with a power saving device integrated therein.
  • the cylinder head 600 comprises a slide 7 which functions as a 2/2-way valve and activates a suction connection 1 of the reciprocating compressor with integrated minimum air valve 8.
  • the ambient air sucked in via the suction connection 1 passes via the slide 7 within the cylinder head 600 into a dead space formed therein and switchable Serving suction chamber 18.
  • Direction of compression chamber 500, the suction chamber 18 opens in the cylinder head 600 via a - not shown - valve plate in trained suction openings. 3
  • the suction openings 3 are controlled via a 2/2-Wegeventilbesclien designed as a suction plate 4 to prevent in the valve position shown, which corresponds to the working position of the compressor via a check valve function, a return flow of compressed air into the suction chamber 18 and the generated compressed air over at least a likewise formed in the valve plate pressure bore 5 with downstream pressure valve unit 9 eject.
  • a voltage applied to the actuating means for the device for power saving control pressure S - as shown here - the mechanism is pressed by the spring force of a return spring 12 in the working position.
  • the control pressure S is applied, the pressure bores 5 are at least partially closed and the suction openings 3 are opened - in the other switching position of the suction lamella 4, not shown here.
  • the piston 100 then only compresses into the now closed suction chamber 18.
  • the minimum air valve 8 of the slide 7 also serves to ensure a reduced flow rate in the case of a blocked in the closed position mechanism and thus constitutes a safety function.
  • the cylinder head 600 in the outer view essentially consists of a valve plate 2, on which an intermediate plate 20 is placed for extended placement of the device for power saving, which is followed by a cylinder head cover 21.
  • a valve plate 2 on which an intermediate plate 20 is placed for extended placement of the device for power saving, which is followed by a cylinder head cover 21.
  • the cylinder head cover 21 there is disposed an opening for supplying the control pressure S for the power saving device to be accommodated inside the cylinder head 600.
  • the disc-shaped designed as a rotary blade suction plate 4 is arranged at the bottom of the valve plate 2.
  • the Sauglamelle 4 is here in the working position, wherein - in accordance with FIG. 1 - Which are arranged annularly arranged in the valve plate 2 introduced pressure holes 5, while here - not recognizable - covered by the suction plate 4 and also annularly arranged in the valve plate 2 suction ports 3 are covered.
  • FIG. 3 11 illustrates, in contrast to the external view described above, a partial sectional bottom view of the power saving device with omission of the intermediate plate 20 and cylinder head cover 21, showing in detail the actuating means for the power saving device in the working position.
  • the pneumatically actuated actuating means comprise a parallel to the plane of the valve plate 2 guided and acted upon by the control pressure S actuating piston 11.
  • the actuating means are in the control pressure-less Starting position.
  • a coupled to the actuating piston 11 driving pin 17 acts via a rotary lever 10 with a rotary lever axis 14 for actuation on the suction plate 4, to switch them between working and idle position.
  • the driving pin 17 of the actuating piston 11 actuates the slide 7 serving to actuate the suction port 1 (not shown), which is articulated via a pivot bearing 13 and designed as a pivoting slide.
  • the slide 7 is provided in the region closing off the suction connection 1 with a minimum air valve 8a, 8b.
  • the suction lamella 4 closes the suction openings 3 formed in the valve plate, while at the same time adjacent pressure valve cross sections 5 are released via openings 6 in the suction lamella 4.
  • the pressure valve cross sections 5 cooperate with a pressure valve unit 9a-9c, which form a check valve to the delivery side.
  • FIG. 4 is a top view of the in the FIG. 3 shown mechanism, the above in connection with the FIG. 3 used reference numerals apply using the above detailed description. Illustrated by way of illustration here is the functional position of the actuating means of the device for power saving. In addition, it can be seen that the slide 7 is provided at the end, which is not shown here - the suction connection 1, with a minimum air intake opening 15 of the minimum air valve 8 (not shown here).
  • the device for power saving using the component designation according to the preceding detailed description is shown in the working position.
  • the attached to the valve plate 2 suction plate 4 covers the introduced into the valve plate 2 suction ports 3 and the adjacent pressure valve cross sections 5 of the valve plate 2 are opened via the openings 6 in the suction plate 4.
  • the suction port 1 is not in - further illustrated - cylinder head because of the pivoted away therefrom slide 7 in the open position.
  • This working position is achieved in the control-pressure-free state of the actuating piston 11, which is pressed by a return spring 12 in the starting position.
  • the actuating piston 11 is tax-pressurized, so that the device for power saving is in the neutral position.
  • the suction openings 3 of the valve plate 2 are opened by recesses 16 of the suction plate 4, whereas the pressure valve cross-sections 5 are closed, since they are not in accordance with the corresponding openings 6 in the suction plate 4.
  • the suction port 1 in the cylinder head (not shown here) is closed by the end of the slide 7, so that air can only flow via the minimum air valve 8 through the minimum air intake 15 into the suction chamber 18 (not shown here).
  • FIG. 7 is a sectional view of line VV FIG. 6 and illustrates the device for power saving in neutral position.
  • the actuating piston 11 of the actuating means for the power-saving device in a corresponding bore 22 in the cylinder head cover 21 is guided to form a piston-cylinder unit, which is acted upon by the control pressure.
  • the driving pin 17 arranged on the outer circumference of the actuating piston 11 extends through an oblong hole-shaped recess in the cylinder head cover 21 into the slide 7 designed as a pivoting lever.
  • the pressure valve unit cooperating with the pressure valve cross sections 5 in the valve plate 2 consists of a pressure valve catch 9a, a pressure valve spring 9b and a pressure valve cam 9c, which is arranged here in the region of the intermediate plate 20 of the cylinder head.
  • FIG. 8 is a sectional view of line IV-IV in FIG. 4 and illustrates the device for power saving in the working position. Incidentally, the above detailed description also applies here with regard to the reference numbers used.
  • FIG. 9 shows a two-cylinder construction of a reciprocating compressor, in which the same suction space is used by both cylinders.
  • the slider 7 ' is present only once, since there is only one suction port 1 in this embodiment.
  • Each compression chamber 500 and 500a is associated with its own rotatable suction plate 4 and 4a.
  • the idle phase then pushes a piston 100, the air via the suction chamber 18 in the other compression chamber 500a at 180 ° stroke displacement at this moment just a downwardly moving piston 100a has, so sucks.
  • the cylinder pressure on the size of the approved Saugkanalqueritese interpret so that enough back pressure to avoid oil leakage remains.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Claims (10)

  1. Dispositif pour économiser de la puissance dans un compresseur à piston, notamment pour produire de l'air comprimé dans un véhicule automobile, comprenant un piston (100) délimitant un espace (500) de compression pour produire de l'air comprimé, qui, en provenance de l'atmosphère ambiante, arrive, afin d'être comprimé dans l'espace (500) de compression, par au moins un raccord (1) d'aspiration constitué sur un couvercle (21) de tête de cylindre et par un dispositif de vanne d'aspiration monté sur un plateau (2) de vanne, dans lequel, pour économiser de la puissance, un dispositif de marche à vide, agissant en fonction de la pression, est prévu pour le dispositif de vanne d'aspiration pourvu d'une lamelle (4) d'aspiration associée, la lamelle (4) d'aspiration pouvant, par des moyens d'actionnement, tourner entre une position de travail recouvrant au moins une ouverture (3) d'aspiration et une position de marche à vide dégageant, au moins en partie, la au moins une ouverture (3) d'aspiration,
    caractérisé en ce que les moyens d'actionnement actionnent de manière coordonnée la lamelle (4) d'aspiration, de manière à ce que celle-ci dégage, dans la position de marche à vide, la au moins une ouverture (3) d'aspiration du plateau (2) de vanne et en même temps ferme, au moins en partie, des sections (5) transversales de soupape de refoulement voisines, ainsi que le raccord (1) d'aspiration sur le couvercle (21) de tête de cylindre au moyen d'un tiroir (7) pour former un espace mort agrandi dans la région de la tête (60) de cylindre.
  2. Dispositif suivant la revendication 1,
    caractérisé en ce que les moyens d'actionnement commandés pneumatiquement ont un piston (11) d'actionnement guidé dans la région du couvercle (21) de tête de cylindre sensiblement parallèlement au plan du plateau (2) de vanne et pouvant être alimenté par une pression de commande.
  3. Dispositif suivant la revendication 2,
    caractérisé en ce que le piston (11) d'actionnement est guidé dans un alésage (22) du couvercle (21) de tête de cylindre.
  4. Dispositif suivant la revendication 2,
    caractérisé en ce que le piston (11) d'actionnement pneumatique pouvant être alimenté par une pression de commande est réglable par un ressort (12) de rappel dans une position initiale sans pression de commande, qui correspond à la position de travail.
  5. Dispositif suivant les revendications 2 et 3,
    caractérisé en ce que le piston (11) d'actionnement agit au moyen d'un toc (17) d'entraînement qui y est couplé à la fois sur un axe (14) de levier de rotation faisant tourner la lamelle (4) d'aspiration entre la position de travail et la position de marche à vide et sur le tiroir (7) fermant le raccord (1) d'aspiration.
  6. Dispositif suivant la revendication 1,
    caractérisé en ce que le tiroir (7) fermant le raccord (1) d'aspiration est constitué sous la forme d'un tiroir pivotant articulé au couvercle (21) de tête de cylindre.
  7. Dispositif suivant la revendication 1,
    caractérisé en ce que le tiroir (7) est pourvu d'une soupape (8a, 8b) de minimum d'air dans la région fermant le raccord (1) d'aspiration.
  8. Dispositif suivant la revendication 7,
    caractérisé en ce que la soupape (8a, 8b) de minimum d'air constituée sous la forme d'un clapet antiretour est une soupape à lamelle, qui est constituée sous la forme d'un collecteur de vanne de minimum d'air constitué en passage (8a) à un côté d'extrémité du tiroir et ayant une lamelle (8b) de vanne coopérant avec lui.
  9. Dispositif suivant la revendication 1,
    caractérisé en ce que plusieurs ouvertures (3) d'aspiration constituées dans le plateau (2) de vanne sont disposées en forme d'anneau de cercle et coopèrent avec une lamelle (4) d'aspiration discoïdale sous la forme d'une lamelle tournante ayant des traversées (6) et des évidements (16).
  10. Dispositif suivant la revendication 9,
    caractérisé en ce que, en outre, plusieurs sections (5) transversales de soupape de refoulement constituées dans le plateau (2) de vanne sont disposées en forme d'anneau de cercle et coopèrent, à la manière d'une soupape, en alternance avec la lamelle (4) d'aspiration discoïdale.
EP14715843.0A 2013-04-10 2014-04-04 Dispositif destiné à l'économie de puissance dans un compresseur à piston Not-in-force EP2984347B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013006138.5A DE102013006138A1 (de) 2013-04-10 2013-04-10 Einrichtung zur Leistungseinsparung bei einem Kolbenverdichter
PCT/EP2014/000908 WO2014166615A1 (fr) 2013-04-10 2014-04-04 Dispositif destiné à l'économie de puissance dans un compresseur à piston

Publications (2)

Publication Number Publication Date
EP2984347A1 EP2984347A1 (fr) 2016-02-17
EP2984347B1 true EP2984347B1 (fr) 2017-03-22

Family

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Application Number Title Priority Date Filing Date
EP14715843.0A Not-in-force EP2984347B1 (fr) 2013-04-10 2014-04-04 Dispositif destiné à l'économie de puissance dans un compresseur à piston

Country Status (5)

Country Link
US (1) US10072653B2 (fr)
EP (1) EP2984347B1 (fr)
CN (1) CN105102817B (fr)
DE (1) DE102013006138A1 (fr)
WO (1) WO2014166615A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020132824A1 (de) * 2020-12-09 2022-06-09 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Optimiertes Ventilsystem für Kolbenkompressoren - Ventillamelle und Ventilfänger mit aerodynamischer Dämpfung

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FR1098045A (fr) 1953-11-24 1955-07-15 Dispositif de régulation pour compresseurs d'air ou de gaz
US3351271A (en) * 1965-11-02 1967-11-07 Worthington Corp Unloading device for reciprocating compressors
DE3329790C2 (de) 1983-08-18 1995-11-30 Wabco Gmbh Ventilträger für Kolbenverdichter
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Publication number Publication date
WO2014166615A1 (fr) 2014-10-16
US10072653B2 (en) 2018-09-11
CN105102817A (zh) 2015-11-25
US20160032917A1 (en) 2016-02-04
EP2984347A1 (fr) 2016-02-17
DE102013006138A1 (de) 2014-10-16
CN105102817B (zh) 2017-02-22

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