EP0372154B1 - Einrichtung zur Leistungseinsparung bei Kolbenverdichtern, insbesondere für die Drucklufterzeugung in Kraftfahrzeugen - Google Patents

Einrichtung zur Leistungseinsparung bei Kolbenverdichtern, insbesondere für die Drucklufterzeugung in Kraftfahrzeugen Download PDF

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Publication number
EP0372154B1
EP0372154B1 EP89108141A EP89108141A EP0372154B1 EP 0372154 B1 EP0372154 B1 EP 0372154B1 EP 89108141 A EP89108141 A EP 89108141A EP 89108141 A EP89108141 A EP 89108141A EP 0372154 B1 EP0372154 B1 EP 0372154B1
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EP
European Patent Office
Prior art keywords
suction
valve
pressure
suction plate
cylinder
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.)
Expired - Lifetime
Application number
EP89108141A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0372154A1 (de
Inventor
Dieter Spurny
Hans Unger
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 AG
Original Assignee
Knorr Bremse AG
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
Priority claimed from DE19893909531 external-priority patent/DE3909531A1/de
Application filed by Knorr Bremse AG filed Critical Knorr Bremse AG
Priority to AT89108141T priority Critical patent/ATE91753T1/de
Publication of EP0372154A1 publication Critical patent/EP0372154A1/de
Application granted granted Critical
Publication of EP0372154B1 publication Critical patent/EP0372154B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • 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
    • F04B39/1086—Adaptations or arrangements of distribution members the members being reed valves flat annular 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

Definitions

  • the invention relates to a device for saving power according to the preamble of claim 1.
  • suction work is still carried out for the piston compressor while the drive continues to run, i.e. air is sucked into the compression chamber of the compressor via the suction line, the opened suction connection and the suction valve in the idle position and is at least partially pushed back into the suction line when the piston of the compressor does the compression work.
  • the air sucked into the compression chamber is loaded with the oil particles, which crawl along the piston rings in the direction of the compression chamber due to the reduced pressure level in the cylinder chamber; this air loaded with oil particles is at least partially through the suction line pushed out again so that paper filters in the suction line are contaminated by the oil particles.
  • FR-Al 098 045 describes a piston compressor, the suction valve of which has an actuating mechanism which serves to keep it open; it is a plunger acting on the suction valve, which carries a piston which can be acted upon by the pressure of the pressure vessel connected to the four-sealer, such that the plunger is displaced by the piston after a pressure threshold has been exceeded and the suction valve is accordingly opened.
  • a non-return flap is provided in the suction line thereof, which opens when a negative pressure occurs in the suction line in order to suck air into the piston compressor.
  • the pressure valve of the piston compressor is unaffected by the actuation of the suction valve, ie it is always in the operational position, so that a certain amount of compression work is always carried out even when the suction valve is in the idle position.
  • the pressure valve opens from a certain pressure level, ie the compressor work is carried out.
  • the oil can get upward along the piston rings, ie into the compression chamber, and thus there is a certain enrichment of the air with oil.
  • the object of the invention is to design a piston compressor of the generic type in such a way that, in the shutdown or idling phase, the best possible, i.e. full performance savings is achieved; it should be ensured that no unnecessary air volume is shifted on the pressure side of the compressor, on the other hand it should be ensured that oil does not unnecessarily get from the crankcase into the compression chamber and from there can contribute to an oil enrichment of the air in the suction line. It should also be prevented, in particular in the case of turbochargers or compressors connected in parallel to the suction line of the piston compressor, that coking occurs in the latter by sucking in air laden with oil under the action of high temperatures.
  • the features according to the characterizing part of claim 1 are used Suction lamella in the open position, by the further, at least partially closing of the pressure openings of the compressor and by the use of the check valve within the cylinder head, an optimization of the means used to save power is achieved; in the idling phase, the movable suction lamella in conjunction with the check valve in the cylinder head ensures that the suction line and any filters and / or compressor systems connected to the suction line remain unaffected by the further idling of the piston of the compressor. The simultaneous, at least partially completed closure of the pressure openings of the piston compressor also ensures that there is an unnecessary blowing off of air.
  • the suction lamella can be moved as a sliding lamella with the aid of the actuating device under the control of the pressure regulator from its operating position, i.e. pumping position, to the idle or switch-off position, in which the suction holes are either partially or completely exposed, in such a way that the air sucked into the compression chamber can flow back into the suction chamber.
  • the resultant performance savings are of the order of 60%.
  • the suction lamella is designed so that the pressure holes are completely or partially closed as required in the idle phase; an unnecessary displacement of a volume fraction of air into the pressure chamber does not therefore take place.
  • a cylinder 1 In the partial view of a piston compressor shown partially in section in FIG. 1, a cylinder 1, a valve carrier 3 and a cylinder head 5 indicated by dash-dotted lines are provided.
  • the valve carrier 3 of the piston compressor is designed in a known manner as an intermediate plate, on the underside of which a valve member in the form of a suction lamella 7 (FIGS. 2 and 3) and on the top of which a valve member (not shown), for example in the form of a pressure lamella, are provided.
  • the suction lamella 7 is assigned suction openings 9, which penetrate the intermediate plate and open at the top in a suction chamber of the cylinder head 5.
  • the suction lamella 7 lies flat against the underside of the valve support 3, with flat seals being inserted between the upper and underside of the valve support 3 and the cylinder head 5 or cylinder 1 in the assembled state.
  • screw bolts (not shown) have, for example, the arrangement shown in FIG. 1 with the holes 8, such that both the cylinder head 5 and the cylinder 1 can be tightened against the seals on the valve carrier 3.
  • 2 and 3 show two pressure openings 11 in the exemplary embodiment shown, to which a pressure valve (not shown), which is known per se, is assigned on the side of the valve carrier 3 facing the cylinder head 5. This can be a pressure lamella held in a valve catcher.
  • the pressure openings 11 according to the invention can be made in the same way as the suction openings 9 Suction lamella 7 are exposed or covered by it.
  • the suction lamella 7 has, for example, an annular shape with a central recess 13 and is approximately rectangular at its right end as shown, ie it has a fastening tab 15 which is penetrated by two elongated holes 17 and 19.
  • the slot 17 is closed and the slot 19 is wedge-shaped open towards the end of the fastening tab.
  • the suction lamella 7 is held on pins 21 and 23 which extend from the valve support 30 and which are guided in the elongated holes 17 and 19 in such a way that the suction lamella 7 can perform displacement movements parallel to the longitudinal axis of these elongated holes.
  • the annular section of the suction lamella 7 covers suction openings 9, while the pressure openings 11 are exposed.
  • the suction lamella 7 acts in a conventional manner with respect to the suction openings 9, ie during the suction cycle the suction lamella lifts elastically from the suction openings 9 so that air to be compressed can be sucked into the interior of the compression space in the cylinder, while the suction lamella 7 is pressed against the suction openings 9 during the compression stroke and the previously opened connection is closed.
  • the located on the top of the valve carrier 3, not shown pressure plate works in a corresponding manner with respect to the pressure openings 11.
  • the pressure plate closes with respect to the pressure openings 11 and during the actual working stroke of the piston in the cylinder, the pressure plate opens in a conventional manner, so that compressed air can be pushed out of the compression chamber through the pressure openings.
  • the suction lamella 7 is under the influence of those described below Actuating device moved into a position relative to the valve support 3, in which some of the suction openings 9 are completely exposed and some are partially covered, while according to the invention the pressure openings 11 are simultaneously covered by a sealing flap 25 of the suction lamella formed on the inner circumference.
  • the sealing tab 25 can also partially cover the pressure openings.
  • an actuating piston 27 is provided which is guided in a step-wise stepped bore 29 and is displaceable against the force of a spring 31.
  • the actuating piston 27 can be acted upon by means of the pressure medium inlet 33 on the cylinder with control pressure, preferably with control pressure from a pressure regulator connected downstream of the piston compressor, in order to carry out a longitudinal movement within the bore 29.
  • the actuating piston 27 carries a driving pin 35 which extends in the direction of the valve carrier 30 and which is guided in an elongated hole 37 (FIG. 5) opening at the top of the cylinder 1.
  • the underside of the valve support 3 facing the cylinder is expediently provided with a recess 39 corresponding to the length of the elongated hole 37, so that the displacement movements of the driving pin 35 are ensured with a sufficient length thereof.
  • the actuating piston 27 has on its circumference two seals 41 and 43, between which the driving pin 35 extends from the actuating piston, that is to say that the axial region between the two seals is sealed against outside air, that is to say also against the bore end in which the spring is located 31 is located.
  • the suction lamella 7 located on the underside of the valve support 3 carries a transmission lever 45 which is articulated on the suction lamella by means of a pin 47; the transmission lever 45 can thus perform movements relative to the suction lamella 7 about the longitudinal axis of the pin 47.
  • the translation lever is also by means of Elongated hole 19 guided pin 23 articulated on the valve support 3, ie that the transmission lever can be pivoted about the longitudinal axis of the pin 23 when the suction lamella is moved from the position shown in FIG. 2 to the position shown in FIG.
  • An eye 49 is also provided on the transmission lever 45, that is to say an opening which is at a predetermined distance from the pins 23 and 47 and serves to receive the driving pin 35.
  • the transmission lever 45 is consequently forced to pivot about the longitudinal axis running through the pin 23; this pivoting movement is made possible because the suction lamella 7 can be displaced in the longitudinal direction as a result of the elongated hole engagement 17, 21 or 19, 23.
  • the transmission lever 45 performs a relative rotational movement both with respect to the suction lamella and with respect to the valve carrier 3, as a result of which it assumes the position shown in FIG. 3 in the switch-off position.
  • a depression 51 comparable to the depression 39 is expediently provided on the underside of the valve carrier 3 in order to be able to give the pin 47 a certain overall length in the same way as for the driving pin 35. As a result, there is sufficient free space for the arcuate path of the pin 47 when it is moved from the position according to FIG. 2 to the position according to FIG. 3 relative to the valve carrier.
  • the diameter of the actuating piston can also be chosen to be sufficiently large to convey the force required to pivot the transmission lever 25 and thus to move the suction lamella 7.
  • the area of the actuating piston in the cylinder 1 is not exposed to those thermal loads which exist directly in the valve carrier 3. This is also of particular advantage with regard to the existing thermal loads in continuous operation.
  • the actuating piston 27 can also be arranged in the cylinder head 5, the element actuating the transmission lever 45 passing through the valve carrier 3. Even if the actuating piston 27 is arranged in the cylinder head 5, much more installation space is available than in the valve carrier 3 itself, with the result that sufficiently large diameters and thus sufficiently large axial forces of the actuating piston can be achieved.
  • Piston compressors of the type in question have high temperatures which lead to coking when compressing oil-containing air; Coal particles can consequently be deposited in the area of the suction and compression space in the cylinder, in the area of the valve carrier and also in the cylinder head.
  • the configuration of the transmission lever 45 and its rotational position is selected such that the elongated hole 37 is covered in all operating positions. The space between the two seals 41 and 43 within the bore 29 is thus also protected against the penetration of harmful combustion particles.
  • the piston compressor further has a check valve 53 located in the cylinder head 5, which is located in the connection between the suction connection 55 of the piston compressor shown in FIG. 5 and the valve carrier 3.
  • the check valve 53 is preferably designed as a lamella check valve which is formed from a valve lamella 57 and from a valve catcher 59.
  • the valve lamella and the valve catcher are fastened in the interior of the cylinder head 5 by means of a fastening screw 61; the valve catcher in the form of a sheet steel part supports the opening movements of the valve lamella 57 made of valve steel in a known manner.
  • the valve lamella acts against an opening 63, which is formed in a plate 65 that is structurally integrated with the cylinder head.
  • the check valve 53 explained above is implemented in the exemplary embodiment according to FIG. 5 in a piston compressor of the construction explained above with reference to FIGS. 1-4, the sectional view according to FIG. 5 (with a different dimensioning) being realized by two of the ones in FIG. 3 reproduced suction openings 9 runs.
  • the suction lamella 7 likewise shown in section in FIG. 5 can be actuated in the manner explained in more detail above with the aid of the transmission lever 45, the pin 47 guided on the suction lamella engaging in the central position of the lamella body.
  • the check valve 53 delimits the suction chamber 67 between itself and the valve carrier 3, such that a connection between the suction chamber 67 and the suction connection 55 is blocked in the closed position of the check valve.
  • check valve described with reference to a single-cylinder construction can also be used in a particularly advantageous manner in the case of multi-cylinder designs, the check valve integrated design in the cylinder head avoiding that multiple suction connections are required.
  • FIG. 6 two check valves of the type in question are provided in a two-cylinder construction, each of which delimits a suction space for itself.
  • a common suction chamber 69 is provided above the check valves, to which a single suction port 71 is assigned.
  • the pressure openings in the valve carrier and the pressure connection of the cylinder head are not shown.
  • the suction lamella 7 In normal pump operation of the piston compressor, the suction lamella 7 is in the relative position shown in FIG. 2 with respect to the suction openings 9 and the pressure openings 11. In this position, the suction lamella and the pressure lamella work in a normal manner, i.e. During a suction stroke of the piston 73 working in the cylinder, indicated in FIG. 5, the suction lamella 7 lifts off from the suction openings 9. In the same way, the check valve 53 opens under the suction, so that the compression space 75 above the piston 73 is filled with air.
  • the suction lamella 7 closes automatically and is additionally pressed against the suction openings 9 under the pressure of the compressed air; the (not shown) pressure lamella of the pressure valve, however, opens, so that the compressed air from the compression chamber 75 after passing through the pressure openings 11 into the (not shown) pressure port of the piston compressor and from there to the pressure regulator and downstream consumers.
  • the non-return valve 53 additionally opening due to the negative pressure arising in the cylinder.
  • the check valve 53 closes in the same way as the actual suction valve, which is formed by the suction lamella 7 and the suction openings 9.
  • the suction lamella 7 When a certain pressure is reached, which takes effect in the pressure regulator, the suction lamella 7 is shifted from its operating, ie pumping position according to FIG. 2 into the switch-off position or idling position according to FIG. 3 with the aid of the control pressure derived from the pressure regulator. As a result, the suction openings 9 are opened so far that the air sucked in by the piston of the compressor can flow back into the suction space 67 shown in FIGS. 5 and 6 of the drawing during the compression thrust.
  • the check valve 53 prevents further backflow in the direction the suction connection 55 or 71; consequently, in the switch-off phase, no air can be pushed into the suction line and into the filter system upstream of the suction line. Pulsation movements in the suction line of the piston compressor and the associated loss of energy are thus switched off despite the suction lamella being open.
  • the control pressure of the pressure regulator (not shown) is effective via the pressure medium inlet 33 on the relatively large cross-section of the actuating piston 27 and moves it upwards in the illustration according to FIG through the elongated hole 37 on the top of the cylinder extending driving pin 35 under guidance of the eye 49 of the transmission lever 45 rotates the latter about the axis of rotation of the pin 23, so that the suction lamella 7 pivots from the position according to FIG. 2 into the position according to FIG becomes.
  • the pressure openings 11 are partially or completely covered by the sealing tab 25 of the suction lamella, so that a certain dynamic pressure arises within the compression space 75 and the suction space 67 during the compression stroke of the piston with the suction openings 9 open.
  • This dynamic pressure contributes to the fact that oil creeping upward along the piston rings (not shown) of the compressor piston is pushed back into the crankcase. This precludes unnecessary enrichment of the air with oil from the crankcase.
  • the oil consumption of the compressor is kept low by an appropriate back pressure. It is also possible to only partially cover the pressure openings 11 by the suction lamella, which is achieved by a corresponding shaping of the sealing tab 25.
  • the suction lamella 7 is returned from the position according to FIG. 3 to the pumping position according to FIG. 2 when the pressure regulator switches back again when the pressure drops, as a result of which the control pressure is completely reduced, i.e. the control output on the pressure regulator is vented so that the actuating piston 27 is now pushed back into the position shown in FIG. 4 under the action of the tensioned spring 31.
  • the driving pin 35 pivots the transmission lever 45 from the position shown in FIG. 3 back to the position shown in FIG. the suction lamella 7 is withdrawn by the forces acting on the transmission lever.
  • the suction openings 9 are again in the functional position according to FIG. 2 and the pressure openings 11 are exposed again.
  • each of the compressors being provided with an arrangement of the type described above.
  • the check valves 53 of the two piston compressors are advantageously arranged within the cylinder head in a manner comparable to the embodiment according to FIG. 5, with an individual suction chamber 67 being assigned to each compressor. Nevertheless, only a single suction connection 71 is required, since a merging of the suction spaces 67 into the common suction chamber 69 is made possible.
  • the check valve 53 which is preferably designed as a lamellar valve, is guided in the exemplary embodiment shown on the plate 65 cast in one piece with the cylinder head.
  • a separate valve support plate can also be provided, on which the valve plate 57 of the check valve 53 is arranged.
  • This valve carrier plate can be used with suitable means in different relative positions, i.e. Distance positions can be mounted relative to the valve support 3, such that the volume of the suction space 67 is variable.
  • This is advantageous with regard to the additional function of the suction space 67, which acts as a switchable volume for the compressor when the suction lamella 7 is in the switched-off position, that is to say when the suction openings 9 are open. In this sense, the suction space 67 takes up increased pressure, which would occur when the pressure openings 11 were closed.
  • the actuating piston can be connected to a mechanism (not shown) which, when configured as a sliding lamella, moves the valve lamella 57 into the open, i.e. the opening 63 moves exposed position when the suction lamella 7 is simultaneously moved into the normal working position according to FIG.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP89108141A 1988-12-08 1989-05-05 Einrichtung zur Leistungseinsparung bei Kolbenverdichtern, insbesondere für die Drucklufterzeugung in Kraftfahrzeugen Expired - Lifetime EP0372154B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89108141T ATE91753T1 (de) 1988-12-08 1989-05-05 Einrichtung zur leistungseinsparung bei kolbenverdichtern, insbesondere fuer die drucklufterzeugung in kraftfahrzeugen.

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE3841423 1988-12-08
DE3841415 1988-12-08
DE3841423 1988-12-08
DE3841415 1988-12-08
DE19893909531 DE3909531A1 (de) 1988-12-08 1989-03-22 Einrichtung zur leistungseinsparung bei kolbenverdichtern, insbesondere fuer die drucklufterzeugung in kraftfahrzeugen
DE3909531 1989-03-22

Publications (2)

Publication Number Publication Date
EP0372154A1 EP0372154A1 (de) 1990-06-13
EP0372154B1 true EP0372154B1 (de) 1993-07-21

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EP89108141A Expired - Lifetime EP0372154B1 (de) 1988-12-08 1989-05-05 Einrichtung zur Leistungseinsparung bei Kolbenverdichtern, insbesondere für die Drucklufterzeugung in Kraftfahrzeugen

Country Status (3)

Country Link
EP (1) EP0372154B1 (pt)
BR (1) BR8906146A (pt)
DE (1) DE58904973D1 (pt)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4006156A1 (de) * 1990-02-27 1991-08-29 Knorr Bremse Ag Kolbenverdichter, insbesondere fuer die drucklufterzeugung in kraftfahrzeugen
DE19833286A1 (de) * 1997-07-26 1999-02-04 Knorr Bremse Systeme Verbesserter Gaskompressor
US5980219A (en) * 1995-08-11 1999-11-09 Knorr-Bremse Systems Fur Nutzfahrzeuge Gmbh Piston-type compressor, especially for generating compressed air in motor vehicles
US6016833A (en) * 1995-08-06 2000-01-25 Knorr-Bremse Systems Fur Nutzfahrzeuge Gmbh Valve plate for piston compressor, especially for air compression in motor vehicles
US6113369A (en) * 1997-07-26 2000-09-05 Knorr-Bremse Systems For Commerical Vehicles Ltd. Reed valve arrangement and gas compressor employing a reed valve arrangement
US6116874A (en) * 1997-07-26 2000-09-12 Knorr-Bremse Systems For Commercial Vehicles Limited Gas compressors
US8506260B2 (en) 2008-05-30 2013-08-13 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Compressor system and method for the operation of a compressor system
DE4321013C5 (de) * 1993-06-24 2014-07-17 Wabco Gmbh Gasverdichter

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4006156A1 (de) * 1990-02-27 1991-08-29 Knorr Bremse Ag Kolbenverdichter, insbesondere fuer die drucklufterzeugung in kraftfahrzeugen
DE4321013C5 (de) * 1993-06-24 2014-07-17 Wabco Gmbh Gasverdichter
US6016833A (en) * 1995-08-06 2000-01-25 Knorr-Bremse Systems Fur Nutzfahrzeuge Gmbh Valve plate for piston compressor, especially for air compression in motor vehicles
US5980219A (en) * 1995-08-11 1999-11-09 Knorr-Bremse Systems Fur Nutzfahrzeuge Gmbh Piston-type compressor, especially for generating compressed air in motor vehicles
DE19833286A1 (de) * 1997-07-26 1999-02-04 Knorr Bremse Systeme Verbesserter Gaskompressor
US6053713A (en) * 1997-07-26 2000-04-25 Knorr-Bremse Systems For Commercial Vehicles Limited Gas compressors
US6113369A (en) * 1997-07-26 2000-09-05 Knorr-Bremse Systems For Commerical Vehicles Ltd. Reed valve arrangement and gas compressor employing a reed valve arrangement
US6116874A (en) * 1997-07-26 2000-09-12 Knorr-Bremse Systems For Commercial Vehicles Limited Gas compressors
US8506260B2 (en) 2008-05-30 2013-08-13 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Compressor system and method for the operation of a compressor system

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Publication number Publication date
DE58904973D1 (de) 1993-08-26
BR8906146A (pt) 1990-07-31
EP0372154A1 (de) 1990-06-13

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