EP1548280B1 - Compresseur à piston - Google Patents

Compresseur à piston Download PDF

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Publication number
EP1548280B1
EP1548280B1 EP04030336A EP04030336A EP1548280B1 EP 1548280 B1 EP1548280 B1 EP 1548280B1 EP 04030336 A EP04030336 A EP 04030336A EP 04030336 A EP04030336 A EP 04030336A EP 1548280 B1 EP1548280 B1 EP 1548280B1
Authority
EP
European Patent Office
Prior art keywords
piston
valve
cylinder
housing
crankshafts
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
EP04030336A
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German (de)
English (en)
Other versions
EP1548280A1 (fr
Inventor
Peter Dr.-Ing. Kreuter
Armin Dipl.-Ing. Zoschke
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.)
Meta Motoren und Energie Technik GmbH
Original Assignee
Meta Motoren und Energie Technik 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
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Publication of EP1548280A1 publication Critical patent/EP1548280A1/fr
Application granted granted Critical
Publication of EP1548280B1 publication Critical patent/EP1548280B1/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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/12—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having plural sets of cylinders or pistons

Definitions

  • the invention relates to a reciprocating compressor, which is particularly suitable for charging an internal combustion engine.
  • the charging of internal combustion engines is not only a proven means of increasing torque and performance, but also to reduce consumption in part-load operation of an internal combustion engine with predetermined maximum power.
  • the charging of diesel engines is particularly advantageous, since in diesel engines existing in gasoline engines knocking problems are not present.
  • turbocharging the energy contained in the exhaust gas of an internal combustion engine is used to drive a turbocharger, which drives a turbine that supplies compressed air to the internal combustion engine.
  • turbocharger which drives a turbine that supplies compressed air to the internal combustion engine.
  • the compressor is driven by its own drive, for example the crankshaft of the internal combustion engine to be supercharged, or another engine, for example an electric motor, in order to compress the air supplied to the internal combustion engine.
  • Different types of externally driven compressors are known, for example Routs blower, spiral loader or reciprocating compressor.
  • US 4,486,157 describes a reciprocating compressor with a double-acting piston whose wall connecting the piston crowns is formed with a transverse to the direction of movement of the piston slot in which a crank pin of a drive shaft engages.
  • a working chamber is formed within the cylinder, which is connected to the environment via each designed as a spring-loaded check valve inlet valve and exhaust valve.
  • the invention has for its object to provide a particular suitable for charging an internal combustion engine reciprocating compressor, which has a high efficiency with a simple structure.
  • crankshafts extend transversely to the direction of movement of the piston between its bottoms, so that the area of the piston which is effective for compression or air delivery is not reduced by the crankshafts. Furthermore, the two crankshafts rotate in opposite directions and at the same speed, so that the oscillations emanating from a conventional crankshaft drive can be compensated for and the reciprocating compressor, despite its high delivery volume, runs with low vibration, which is advantageous for the supercharging of vehicle internal combustion engines.
  • a reciprocating compressor according to the invention has a double-sided cylinder 2 closed by end walls, in which a piston 4 can be moved back and forth.
  • the piston 4 includes two mutually spaced piston bottoms 6 and 8, which are advantageously equipped at their peripheral edges for sealing with piston rings and the two inside the cylinder 2 working chambers 10 and 12 separate.
  • the two piston plates 6 and 8 are connected by struts 14 rigidly together, for example screwed.
  • On the mutually facing inner sides of the piston heads 6 and 8 guide surfaces 16 and 17 are formed, which serve to guide sliding blocks 18.
  • the cylinder 2 is received in a housing 32 by means of brackets forming partitions 28 and 30.
  • the housing 32 has at least one suction opening 34 and an ejection opening 36, wherein, as can be seen, between the outer housing 32 and the Cylinder 2 formed by the partition walls 28 and 30 is divided so that an inlet channel 38 is formed which connects the suction port 34 with the inlet valves 20 and 22 or of these selectively open or closed, leading into the working chambers 10 and 12 inlet openings, and an exhaust passage 40 is formed which connects the exhaust valves 24, 26, or selectively open or closed exhaust ports of the working chambers 10 and 12, to the exhaust port 36.
  • FIG. 1 the direction of movement of the piston 4 is horizontal. In FIGS. 2 to 8, it is perpendicular, so that the representations of FIGS. 2 to 8 in accordance with the arrangement according to FIG. Fig. 1 are rotated by 90 °.
  • FIGS. 2 and 3 show perspective views of the piston 4, each with two crankshafts 42 and 44 traversing the pistons.
  • the axles of the crankshafts which are stationary relative to the cylinder 2 and the housing 32 are designated A in FIG.
  • Each crankshaft has at least one each eccentrically to its axis arranged crank pulley 46 and 48, which cooperates with the sliding blocks 18, along the guide surfaces 16, 17 of the piston heads 6 and 8 linearly perpendicular to the axes of the crankshafts are displaced, so that a Gleitstein- or gate guide is created, with the circumferential eccentric movement of the crank disks in a conventional manner in an oscillating movement of the guided inside the cylinder 2 piston can be converted.
  • the sliding blocks are advantageously divided for easy mounting.
  • FIG. 4 shows the crankshafts 42 and 44 in a design for two respective cylinders 2 arranged behind one another within a housing 32 (FIG. 1), in each of which a piston 4 operates.
  • each piston on the crankshaft 42 is associated with two crank disks 46 and on the crankshaft 44 a crank disk 48 which cooperates with corresponding sliding blocks 18.
  • the crank disks 46 and 48 are axially offset from each other, so that their trajectories pass radially, whereby a smaller distance between the crankshafts 42 and 44 is possible.
  • the crankshafts 42 and 44 are provided in a conventional manner with balancing weights 50 and 52, respectively.
  • crankshafts 42 and 44 may be mounted, for example, in each case in the wall of the cylinder 2.
  • crankshafts cam 54 and 56 To drive the valves 20, 22, 24 and 26, the crankshafts cam 54 and 56, with which the valves are actuated via actuators.
  • a gearwheel 58 or 60 is connected in each case to one end of the crankshaft in a rotationally fixed manner to the respective crankshaft.
  • the gears 58 and 60 are equal in size and mesh with each other, so that the crankshafts 42 and 44 rotate in opposite directions at the same speed.
  • the gears 58, 60 serve as elements of a gear pump, which is arranged in a coolant and / or lubricant circuit of the compressor.
  • Fig. 5 shows the gem.
  • FIG. 6 shows a perspective view of sections of a left side of the crankshafts 42, 44 arranged according to the figure, a cylinder associated crank / valve train.
  • cams 54 and 56 are formed on each crankshaft 42 and 44 on both sides outside of the cylinder, with which roller tappets 62 and 64 cooperate, each actuating a cylinder-like cross-over valve member 66 and 68 respectively.
  • the left valve member 66 shown in FIG. 6 actuates a plurality of inlet valves 20 (FIG. 1).
  • the right valve member 68 actuates a plurality of exhaust valves 24.
  • the valves are forcibly guided on the respective valve members.
  • four intake valves and four exhaust valves are arranged on an end wall of the cylinder 2 in the illustrated example and are actuated by means of a respective valve member.
  • valves 20, 22 and the outlet valves 24, 26 are opposite each other, they are arranged on the left side or right side (FIG. 1) or above or below the piston (FIGS. 2 to 8) Valve drives arranged the same or mirror symmetry.
  • the intake valves and the exhaust valves are each actuated by 180 ° out of phase with respect to the rotation of the crankshafts, so that in opposite directions rotation of the juxtaposed crankshafts 42, 44 at the same speed and appropriate design of the cam 54, 56 results in an in-phase actuation of the respective valves.
  • valve members 66 and 68 are guided in a linearly movable guides not shown in the housing and are reciprocated by the cams 54 and 56 against the force of the springs 70 and 72, which are supported between the housing 32 and the respective valve member ,
  • the bridge-type valve member 66 (FIG. 9) actuating the exhaust valves 20 includes for each exhaust valve a pilot passage 74 through which the stem of the exhaust valve 20 extends and which leads into a recess 76 in which the stem of the valve terminates. Between an end flange 78 of the valve stem and the valve member 66, a valve spring 80 is supported, which urges the exhaust valve 20 in the closed position. The end flange 28 opposite a threaded pin 82 is screwed into the valve member 66, which serves for clearance adjustment.
  • the valve member 68 actuating the exhaust valves 24 also has, for each exhaust valve 24, a pilot passage 84 through which the valve stem extends.
  • the valve stem 84 terminates in an example screwed with him stop 86, the distance from the valve disc to the game setting is adjustable.
  • a valve spring 88 is supported between the valve member 68 and the valve.
  • FIGS. 9 and 10 which can be varied in many ways, it is achieved that no separate housing-fixed guide is required for the valve stems that the inlet valves 20 as shown in FIG. 9 in each case during a downward movement of the valve member 66 are opened and the exhaust valves 24 are opened as shown in FIG. 10 at a movement of the valve member 68 upwards.
  • the inlet valve 20 at strong Vacuum in the associated working chamber opens without the valve member 66 being moved and / or the exhaust valve 24 opening at high overpressure in the associated working chamber without the valve member 68 being moved.
  • roller tappet 62 with roller 88 mounted in it and housing-fixed guide 90.
  • FIG. 13 shows a section of the two crankshafts 42 and 44 with the cams 54 and 56.
  • the crankshaft 42 has only one crank disk 46
  • the crankshaft 44 has two crank disks 48.
  • the cam 54 which actuates the inlet valves associated with the roller tappets or bridge members 66, as a "negative cam” is formed, the bridge member 66 is normally in the position gem.
  • Fig. 9 urges against the springs 70 and causes only in its smaller diameter cam portion to take place as shown in Fig. 9 downward movement of the valve member 66 to open the inlet valve 20.
  • the exhaust valves associated cam 56 of the crankshaft 44 is formed as a normal cam with a diameter enlarged cam lobe.
  • the cylinder 2 are then attached, each consisting of two centrally divided halves. Subsequently, the valve trains are mounted in each mounted on the cylinders mounting surfaces and the entire assembly is assembled in the housing 32 also formed in two parts.
  • the cylinder halves and the housing halves may be integrally formed with each other.
  • FIG. 14 shows a piston compressor 92 according to the invention flanged to the intake side of a motor housing or cylinder head 94 of an internal combustion engine.
  • 96 denotes a pulley for driving one of the crankshafts.
  • an intake assembly may be flanged in addition, which may include, for example, a throttle valve and / or a device for measuring the inflowing air amount, etc.
  • the compressor is operated in two-stroke operation.
  • the piston 4 moves from left to right according to FIG. 1, above all the inlet valve 20 and the outlet valve 26 are actuated such that fresh air flows into the working chamber 10 and fresh air compressed from the working chamber 20 is ejected at a suitable pressure level.
  • the inlet valve 22 and the outlet valve 24 are advantageously in the movement from left to right of the piston 4 to.
  • the actuations of the valves occur in opposite directions, i. the fresh charge flow is then determined by the inlet valve 22 and outlet valve 24, whereas valves 20 and 26 are preferred.
  • the intake valves and exhaust valves can be controlled by suitable, per se known, phase adjustment and / or Hubverstell landmarken such that the delivered air flow (air mass flow) to the respective, required for an internal combustion engine operating conditions and the compressor by appropriate appropriate Setting the respective opening and closing times of the valves relative to the dead centers of the piston movement works with high efficiency.
  • the reciprocating compressor according to the invention works, even if it contains only one cylinder and arranged therein, a double-acting piston, with high efficiency and low pressure pulsations.
  • the formation of the piston with two mutually spaced piston crowns, between which the crank mechanism is arranged not only has the advantage that the crankshaft and its lubrication is completely separate from the work spaces, but also allows easy storage of the crankshaft (s) in the cylinder wall.
  • the reciprocating compressor may include any number of cylinders having pistons therein, with the individual cylinders being operated out of phase so as to achieve minimum pressure pulsations.
  • the possible small stroke / bore ratio allows low piston speeds, which favorably affects the durability.
  • the design allows for large cross-sections of the intake and exhaust valves relative to the cylinder cross-section, allowing the compressor to operate with low flow resistance.
  • the loader can be flange-mounted directly on the cylinder head or a suction pipe of an engine to be charged.
  • the housing 32 may have along its length a plurality of discharge ports 36 connected within the housing that lead directly into the intake ports of the individual cylinders.
  • a suction part can be flanged in front of the compressor, which contains, for example, a throttle cap, contains a connection for exhaust gas recirculation or from which a bypass line emanates, which leads bypassing the compressor directly into a suction pipe of the internal combustion engine.
  • the design allows for a high surface-to-volume ratio in relation to the stroke volume, whereby large charge exchange valves are possible.
  • the crank mechanism may include one or more crankshafts, wherein the implementation of the rotational movement of the crankshaft (s) in a reciprocating motion of the piston via a variety of known mechanisms can be done.
  • the mechanism described by means of sliding or sliding blocks is easy to install, works friction and leads to a soft, sinusoidal movement of the piston.
  • the described embodiment with two counter-rotating crankshafts can work as Lancester compensation, with oscillating, sinusoidal mass forces of piston and sliding blocks in the crank mechanism of each piston are completely compensated. Furthermore, each individual cylinder is balanced, so that no cylinder dynamic mass forces are introduced into the housing. Furthermore, there are no outwardly acting mass forces outside of the housing, so that the compressor according to the invention operates very low vibration.
  • crankpin and the crank disks with mutual axial offset leads on the one hand to a compact design and on the other hand, to a low mechanical stress and thus high speed resistance of the crank mechanism.
  • the gears 58 and 60 at the ends of the crankshafts serve for synchronization and power transmission between the crankshafts.
  • the gears can also be replaced by belting means, such as a toothed belt. Only one crankshaft has to be driven from one end, for example by means of the pulley 96 (FIG. 14).
  • the gears 58 and 60 may be used as elements of a gear pump capable of delivering a cooling / lubricating fluid circulating in channels formed in the compressor.
  • a gear pump capable of delivering a cooling / lubricating fluid circulating in channels formed in the compressor.
  • at least the working chamber 10 and 12 bounding walls of the cylinder are cooled, wherein the short zoneleitwege for a provide efficient cooling.
  • the loader may additionally have an internal heat exchanger arranged in front of the discharge opening 36. Alternatively or additionally, the compressed air can flow through an external heat exchanger before it enters the internal combustion engine.
  • the advantageously integrally formed lubricant / coolant circuit of the supercharger can be connected to the internal combustion engine or be formed separately therefrom.
  • an important aspect of the compressor according to the invention is that, on the one hand, the compressed air flowing through the discharge opening 36 is free of any lubricant and, on the other hand, is as cool as possible. It is advantageous for both that the two crankshafts, which are at the same time camshafts, are guided between the piston bottoms and are mounted in the cylinder 2 by means of easily sealable bearings, so that inside the piston an outwardly dense lubricant space is formed, the liquid lubricant serves as a coolant through which crankshafts can be supplied simultaneously.
  • the lubricant / coolant can effectively cool the piston crowns from the inside. It will be understood that fluid return is formed through channels passing through the cylinder wall, the space between the cylinder and the housing and the housing, so that the coolant / lubricant circulates.
  • Shaft guides for the roller tappets 64 may be lubricated by wetting the crankshafts so that the lubricant does not enter the fresh air.
  • Advantageous are very hard ram stem ends or contact surface combinations.
  • the charger according to the invention advantageously operates in the two-stroke process.
  • the intake and exhaust valves can be operated in a variety of ways. In the embodiment, they can not only be operated via the valve members with appropriate dimensioning of the springs, but also work as check valves, the intake valves open at negative pressure in the respective working chamber and open the exhaust valves at overpressure. In alternative embodiments, only the intake valves or only the exhaust valves may be formed as check valves and the other valves may be actuated by the one or more crankshafts.
  • the intake and / or exhaust valves can also be controlled by means of per se known valve actuation mechanisms, for example by changing the effective tap lever and / or the Abgriffswinkel that their opening or closing function is variable, and / or can in the open or closed position being held.
  • the speed of the crankshaft of the compressor may be rigidly coupled to the crankshaft of an internal combustion engine. Between the supercharged internal combustion engine and the compressor, a transmission with stepwise or continuously adjustable ratio can be arranged be. By means of a clutch, the compressor can be completely disconnected from the internal combustion engine.
  • the delivery rate of the compressor can also be varied by variable actuation of the valves, with valves in the open position having a low-flow path from the intake opening 34 to the discharge opening 36 (FIG. 1).
  • fresh air can be supplied via a bypass line.
  • the delivery rate of the loader can be changed as required by controllable openings in the partitions 28 and 30.
  • the inlet opening 34 may be preceded by a throttle valve.
  • each of the crankshafts may be provided with two or more crankshafts associated with each piston.
  • valves can also be operated completely independently of the rotation of the crankshaft by its own drives, such as electromagnetic, hydraulic or other suitable drives. Instead of the two crankshafts, only one crankshaft can extend through each piston, etc.
  • the compressor offers numerous possibilities for controlling maximum compression of the air via light compression, no compression up to the recoil, in which the compressor is used for braking.
  • the compressor or supercharger according to the invention is suitable for charging all types of internal combustion engines, two-stroke engines, four-stroke engines or machines operating with different timing, gasoline engines, diesel engines, gas engines, etc.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Dry Shavers And Clippers (AREA)

Claims (12)

  1. Compresseur à piston, en particulier pour suralimenter un moteur à combustion, comportant au moins un cylindre (2) à l'intérieur duquel deux chambres de travail (10, 12) situées sur des côtés du piston détournés l'un de l'autre sont formées par un piston déplaçable en va-et-vient avec deux fonds de piston (6, 8) agencés à distance mutuelle, chambres qui présentent chacune au moins un orifice d'admission et un orifice de sortie dans chacun desquels travaille une soupape d'admission (20, 22) et une soupape de sortie (24, 26),
    un boîtier (32) entourant le cylindre avec un orifice d'aspiration (34) relié aux orifices d'admission et un orifice d'éjection (36) relié aux orifices de sortie, et
    un dispositif d'entraînement pour déplacer en va-et-vient le piston, dans lequel à chaque course de mouvement du piston la soupape d'admission d'une chambre de travail s'ouvre et celle de l'autre chambre de travail se ferme et la soupape de sortie de ladite une chambre de travail se ferme et celle de l'autre chambre de travail s'ouvre,
    caractérisé en ce que
    le dispositif d'entraînement présente deux arbres à manivelle (42, 44) qui tournent en sens inverse avec la même vitesse, qui s'étendent à travers le piston et à travers le cylindre (2), transversalement à la direction de mouvement du piston (4) entre les fonds (6, 8) de celui-ci.
  2. Compresseur à piston selon la revendication 1, caractérisé en ce que les arbres à manivelle (42, 44) s'étendent au moins partiellement à travers le boîtier (32).
  3. Compresseur à piston selon la revendication 1 ou 2, caractérisé en ce que les arbres à manivelle (42, 44) sont montés dans le cylindre (2) et/ou dans le boîtier (32), et la transmission de mouvement entre le piston (4) et les arbres à manivelle (42, 44) a lieu via des coulisseaux (18) déplaçables sur le piston (4).
  4. Compresseur à piston selon l'une des revendications 1 à 3, caractérisé en ce que des entraînements de déplacement (18, 46 ; 18, 48) sont décalés axialement les uns par rapport aux autres entre les arbres à manivelle (42, 44) et le piston (4) et se chevauchent radialement.
  5. Compresseur à piston selon l'une des revendications 1 à 4, caractérisé en ce qu'un des arbres à manivelle (42, 44) peut être entraîné de l'extérieur et est en engagement solidaire en rotation avec l'autre arbre à manivelle.
  6. Compresseur à piston selon l'une des revendications 1 à 5, caractérisé en ce qu'au moins une des soupapes (20, 22, 24, 26) est actionnée par un arbre à manivelle (42, 44).
  7. Compresseur à piston selon l'une des revendications 1 à 6, caractérisé en ce qu'il est prévu un mécanisme d'actionnement pilotable indépendamment du mouvement de piston pour au moins une des soupapes (20, 22, 24, 26).
  8. Compresseur à piston selon l'une des revendications 1 à 7, caractérisé en ce qu'un élément de soupape (66, 68) guidé sur le boîtier (32) est déplacé par au moins une came (54, 56) réalisée sur l'arbre à manivelle (42, 44), élément de soupape dans lequel est guidée une tige d'au moins une soupape d'admission ou de sortie (20, 22), laquelle soupape prend appui sur l'élément de soupape via un ressort (80, 88) de telle sorte qu'il peut être actionné par l'élément de soupape et qu'il peut être déplacé indépendamment de l'élément de soupape.
  9. Compresseur à piston selon l'une des revendications 1 à 8, caractérisé par une roue dentée (58, 60) reliée de manière solidaire en rotation avec un arbre à manivelle (42, 44), laquelle forme un élément de pompage d'un système de refroidissement et/ou de lubrification du compresseur.
  10. Compresseur à piston selon l'une des revendications 1 à 9, caractérisé en ce que le boîtier (32) entourant le cylindre (2) est réalisé avec une cloison de séparation (28, 30) qui subdivise un espace intermédiaire entre le cylindre et le boîtier de telle sorte que l'orifice d'aspiration (34) est relié avec les orifices d'admission et l'orifice d'éjection (36) est relié aux orifices de sortie.
  11. Compresseur à piston selon la revendication 10, caractérisé en ce que la cloison de séparation (28, 30) subdivise l'espace intermédiaire réalisé entre le boîtier (32) et le cylindre (2) en deux chambres (38, 40) dont l'une forme un canal d'admission (38) reliant les orifices de sortie (34) aux orifices d'admission et l'autre forme un canal de sortie (40) reliant l'orifice d'éjection (36) aux orifices de sortie.
  12. Compresseur à piston selon l'une des revendications 1 à 11, caractérisé par plusieurs cylindres (2) reçus dans un boîtier (32) commun avec des pistons (4) agencés dans ceux-ci, qui sont déplacés en va-et-vient par au moins un arbre à manivelle (42, 44) commun.
EP04030336A 2003-12-23 2004-12-21 Compresseur à piston Not-in-force EP1548280B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10360920 2003-12-23
DE10360920A DE10360920B3 (de) 2003-12-23 2003-12-23 Hubkolbenverdichter

Publications (2)

Publication Number Publication Date
EP1548280A1 EP1548280A1 (fr) 2005-06-29
EP1548280B1 true EP1548280B1 (fr) 2006-10-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP04030336A Not-in-force EP1548280B1 (fr) 2003-12-23 2004-12-21 Compresseur à piston

Country Status (6)

Country Link
US (1) US7780425B2 (fr)
EP (1) EP1548280B1 (fr)
JP (1) JP4491683B2 (fr)
CN (1) CN100424345C (fr)
AT (1) ATE342441T1 (fr)
DE (2) DE10360920B3 (fr)

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Also Published As

Publication number Publication date
US20050152798A1 (en) 2005-07-14
DE10360920B3 (de) 2005-09-22
CN1637281A (zh) 2005-07-13
JP4491683B2 (ja) 2010-06-30
CN100424345C (zh) 2008-10-08
EP1548280A1 (fr) 2005-06-29
DE502004001717D1 (de) 2006-11-23
JP2005180454A (ja) 2005-07-07
US7780425B2 (en) 2010-08-24
ATE342441T1 (de) 2006-11-15

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