EP1607630B1 - Piston compressor - Google Patents

Piston compressor Download PDF

Info

Publication number
EP1607630B1
EP1607630B1 EP05010105A EP05010105A EP1607630B1 EP 1607630 B1 EP1607630 B1 EP 1607630B1 EP 05010105 A EP05010105 A EP 05010105A EP 05010105 A EP05010105 A EP 05010105A EP 1607630 B1 EP1607630 B1 EP 1607630B1
Authority
EP
European Patent Office
Prior art keywords
drive shaft
compressor according
wobble plate
joints
articulated
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.)
Active
Application number
EP05010105A
Other languages
German (de)
French (fr)
Other versions
EP1607630A1 (en
Inventor
Peter Prof. Dr.-Ing. Kuhn
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.)
Obrist Engineering GmbH
Original Assignee
Obrist Engineering 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 Obrist Engineering GmbH filed Critical Obrist Engineering GmbH
Publication of EP1607630A1 publication Critical patent/EP1607630A1/en
Application granted granted Critical
Publication of EP1607630B1 publication Critical patent/EP1607630B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F04B27/08—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
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1072—Pivot mechanisms
    • 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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • 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
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1045—Cylinders
    • 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
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1063—Actuating-element bearing means or driving-axis bearing 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
    • 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
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1081—Casings, housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/40—Movement of component
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the invention relates to a reciprocating compressor with a plurality of mutually and to a drive shaft arranged in parallel in a common compressor housing cylinder-piston units, wherein the drive shaft is enclosed by a pivotally coupled with her swash plate, with which the pistons are connected via a hinged sliding coupling.
  • Such a compressor is known from EP 1388668 A.
  • the e.g. for the air conditioning of a vehicle provided compressor 1 has a by bearings 2 in its housing 3 centrally mounted drive shaft 4, which carries at its outer end a pulley 5 to make a drive connection with the vehicle engine.
  • the housing 3 encloses an inner housing part 6, distributed in the circumferential direction, for example, seven cylinder bores 7 are provided and in which the rolling bearing 2 visible in the drawing is held.
  • the guided in the cylinder bores piston 8 have at its drive end end an articulated sliding coupling with a coupling bracket 9, in which the outer peripheral portion 10 of the swash plate 11 engages and in which this is about spherical segment sliding blocks 12,13 with the piston 8 in drive connection.
  • the two-sided spherical surfaces 14,15 required for the rotatable mounting of the sliding blocks 12,13 in the coupling bracket 9 are incorporated according to the aforementioned prior art in separate and additional insectsörpem that are inserted into the coupling bracket.
  • the spherical surfaces 14,15 as shown in Figures 9 and 10 by means of rotationally driven, cutting tools 16 and 17 are made by at least one axial boundary wall 18 of the coupling bracket 9 a the introduction of the cutting head 19th , 20 of the tool 16,17 in the coupling bracket 9 permitting opening 21 has.
  • this opening 21 is in the piston 8 facing away from the boundary wall 18 of the coupling bracket 9, because the opening 21 surrounding this, opposite the opposite spherical surface 15 smaller spherical surface 14 is loaded only during the suction movement of the piston 8, and correspondingly by smaller forces than they occur during the compression stroke.
  • the pistons 8 can be made as a separate part sleeve-shaped by deep drawing, to be subsequently attached to the coupling bracket 9.
  • the coupling bracket 9, however, can be preformed in a simple manner as a section of an extruded profile.
  • the shaft side joints 25,26 on the other joints 27,28 opposite side of the shaft axis 30 at a Wellenauskröpfung 29 are provided so that this extends through an opening 33 provided eccentrically in the swash plate 11.
  • the swash plate 11 can be made relatively thin by the described embodiment of their coupling with the piston 8, over its entire radial extent, whereby a further contribution to the design of the compressor 1 is given with the greatest possible flow rate.
  • the distance between the shaft-side joints 25,26 smaller distance of the joints 27,28 of the thus trapezoidal four-bar linkage 22 is determined by the height of both sides of the swash plate 11 projecting, cheek-like joint carrier 31,32.
  • the four-bar linkage 22 is on both sides of the wave projection 29, i. Executed twice, wherein the Wellenauskröpfung 29 is bounded laterally by mutually parallel surfaces 34,35 so that they can also lead the flattened articulated arms 23,24 laterally.
  • the double-sided articulated arms 23,24 are preferably rigidly connected together by a transverse web 36, which can also form a stop on the drive shaft 3 for the maximum pivotal movement of the articulated arms 23,24 and thus the swash plate 11.
  • the shaft projection and the articulated carriers 31, 32 provided on the swashplate 11 can have a central guide slot (not shown) for the double-sided guidance of a flat articulated arm.
  • a pivot pin 37 is either secured in the provided in the articulated arms 23 holes 38,39 by a press fit so that it has a sliding bearing in the equiaxed bore 40 of the joint carrier 31 or the holes 38,39 of the articulated arms 23 form Slide bearing, so that the pivot pin 37 is held in the hinge bracket 31 by press-fitting.
  • FIG. 7 is on both sides each provided with a head 41,42 pivot pin 43,44 nested.
  • a continuous pivot pin 45 is used, which is axially secured on the one hand by a pin head 46 and on the other hand by a locking ring 47.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Pressure Welding/Diffusion-Bonding (AREA)
  • Reciprocating Pumps (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

The piston compressor has wobble plate (11) connected to drive shaft (4) through single or double four bar linkage comprising swivellable articulated brackets in each axially separated implemented joints (27,28) mounted on drive shaft.

Description

Die Erfindung betrifft einen Hubkolbenkompressor mit mehreren, zueinander und zu einer Triebwelle parallel in einem gemeinsamen Kompressorgehäuse angeordneten Zylinder-Kolbeneinheiten, wobei die Triebwelle von einer mit ihr schwenkbar gekoppelten Taumelscheibe umschlossen ist, mit der die Kolben über eine gelenkige Gleitkupplung verbunden sind.The invention relates to a reciprocating compressor with a plurality of mutually and to a drive shaft arranged in parallel in a common compressor housing cylinder-piston units, wherein the drive shaft is enclosed by a pivotally coupled with her swash plate, with which the pistons are connected via a hinged sliding coupling.

Ein solcher Kompressor ist aus der EP 1388668 A bekannt.Such a compressor is known from EP 1388668 A.

Ein anderer Kompressor dieser Art ist bekannt durch die DE 4139186. Bei diesem ist die Taumelscheibe auf einem von der Triebwelle getragenen Kugelkörper schwenkbar geführt und in radialem Abstand von diesem über einen Mitnehmer mit der Triebwelle verbunden. Um die für die Veränderung der Kolbenhubweite erforderliche Schwenkbewegung ausführen zu können, erfolgt die Verbindung mit dem Mitnehmer über einen in einem Langloch des Mitnehmers geführten Verbindungsbolzen.Another compressor of this type is known from DE 4139186. In this, the swash plate is pivotally guided on a supported by the drive shaft ball body and connected at a radial distance from this via a driver with the drive shaft. In order to perform the required for the change of the piston stroke width pivoting movement, the connection is made with the driver via a guided in a slot of the driver connecting pin.

Da die Taumelscheibenneigung sich aufgrund der an den Kolben wirkenden, geregelten Druckdifferenz einstellen soll, ist es für die betreffende Ansprechempfindlichkeit der Regelung von besonderer Bedeutung, dass die Schwenkbewegung mit geringem Reibungswiderstand ausgeführt wird. Der Erfindung liegt die Aufgabe zugrunde, einen Hubkolbenkompressor zu finden, der durch geringe Reibungswiderstände bei der Ausführung der Schwenkbewegung ein verbessertes Regelverhalten aufweist, der weiterhin bei kompakten Abmessungen eine verhältnismäßig große maximale Hubweite seiner Kolben aufweist und folglich eine große Förderleistung ermöglicht und der dabei verhältnismäßig einfach und damit preisgünstig herstellbar ist. Die Lösung der genannten Aufgaben erfolgt aufgrund der kennzeichnenden Merkmale des Patentanspruchs 1. Vorteilhafte Ausführungsformen der Erfindung sind Gegenstand der abhängigen Patentansprüche und der folgenden Beschreibung anhand der Zeichnungen entnehmbar. Es zeigt:

Fig.1
eine teilweise axial geschnittene Seitenansicht eines erfindungsgemäßen Kompressors mit zur Triebwelle schräg geschwenkter Taumelscheibe,
Fig.2
eine Darstellung entsprechend Fig.1 bei Leerlaufstellung der Taumelscheibe,
Fig.3
eine perspektivische Darstellung der Mechanik des Kompressors nach Fig. 1 nach Weglassung des Kompressorgehäuses,
Fig.4
eine perspektivische Darstellung der Anordnung nach Fig.3 unter anderem Blickwinkel,
Fig.5
eine seitliche Teilansicht des Kompressorgetriebes im Bereich ihres Gelenkvierecks,
Fig. 6
eine Querschnittsdarstellung eines Gelenks entlang der Linie VI-VI der Fig.5,
Fig.7 und Fig.8
Querschnittsdarstellungen weiterer Ausführungsformen des Gelenkes,
Fig.9
eine vergrößerte Querschnittsdarstellung eines Kolbens, mit Darstellung der Werkzeugführung bei der Bearbeitung einer kugeligen Eingriffsfläche und
Fig.10
eine Darstellung entsprechend Fig.9 bei der Bearbeitung der zum Beispiel nach Fig.9 gegenüberliegenden Eingriffsfläche.
Since the swash plate inclination should be due to the controlled pressure difference acting on the piston, it is of particular importance for the relevant responsiveness of the control that the pivoting movement is performed with low frictional resistance. The invention has for its object to find a reciprocating compressor, which has an improved control behavior by low frictional resistance in the execution of the pivoting movement, which further has a relatively large maximum stroke of its pistons in compact dimensions and thus allows a large flow rate and thereby relatively simple and thus inexpensive to produce. The solution of the above objects is due to the characterizing features of claim 1. Advantageous embodiments of the invention are the subject of the dependent claims and the following description with reference to the drawings. It shows:
Fig.1
a partially axially sectioned side view of a compressor according to the invention with the drive shaft obliquely tilted swash plate,
Fig.2
a representation corresponding to Figure 1 at idle position of the swash plate,
Figure 3
a perspective view of the mechanics of the compressor of Figure 1 after omission of the compressor housing.
Figure 4
3 shows a perspective view of the arrangement according to FIG. 3 from another angle of view,
Figure 5
a partial side view of the compressor gear in the region of its four-bar linkage,
Fig. 6
a cross-sectional view of a joint along the line VI-VI of Figure 5,
Fig.7 and Fig.8
Cross-sectional views of further embodiments of the joint,
Figure 9
an enlarged cross-sectional view of a piston, showing the tool guide in the machining of a spherical engagement surface and
Figure 10
a representation corresponding to Figure 9 in the processing of the opposite example of Figure 9 engagement surface.

Der z.B. für die Klimaanlage eines Fahrzeuges vorgesehene Kompressor 1 hat eine durch Wälzlager 2 in seinem Gehäuse 3 zentral gelagerte Triebwelle 4, die an ihrem äußeren Ende ein Riemenrad 5 trägt, um eine Antriebsverbindung mit dem Fahrzeugmotor herzustellen. Dabei umschließt das Gehäuse 3 einen inneren Gehäuseteil 6, in dem in Umfangsrichtung verteilt beispielsweise sieben Zylinderbohrungen 7 vorgesehen sind und in dem das in der Zeichnung sichtbare Wälzlager 2 gehalten ist.The e.g. for the air conditioning of a vehicle provided compressor 1 has a by bearings 2 in its housing 3 centrally mounted drive shaft 4, which carries at its outer end a pulley 5 to make a drive connection with the vehicle engine. In this case, the housing 3 encloses an inner housing part 6, distributed in the circumferential direction, for example, seven cylinder bores 7 are provided and in which the rolling bearing 2 visible in the drawing is held.

Die in den Zylinderbohrungen geführten Kolben 8 haben an ihrem antriebsseitigen Ende eine gelenkige Gleitkupplung mit einem Kopplungsbügel 9, in den der äußere Umfangsbereich 10 der Taumelscheibe 11 eingreift und in dem diese über kugelsegmentförmige Gleitsteine 12,13 mit den Kolben 8 in Antriebsverbindung steht. Die für die drehbare Lagerung der Gleitsteine 12,13 im Kopplungsbügel 9 erforderlichen beidseitigen Kugelflächen 14,15 werden entsprechend dem eingangs genannten Stand der Technik in separaten und zusätzlichen Zwischenkörpem eingearbeitet, die in den Kopplungsbügel eingefügt werden.The guided in the cylinder bores piston 8 have at its drive end end an articulated sliding coupling with a coupling bracket 9, in which the outer peripheral portion 10 of the swash plate 11 engages and in which this is about spherical segment sliding blocks 12,13 with the piston 8 in drive connection. The two-sided spherical surfaces 14,15 required for the rotatable mounting of the sliding blocks 12,13 in the coupling bracket 9 are incorporated according to the aforementioned prior art in separate and additional Zwischenkörpem that are inserted into the coupling bracket.

In vorteilhafter Ausgestaltung der vorliegenden Erfindung können die Kugelflächen 14,15 entsprechend den Darstellungen in Fig.9 und 10 mittels rotierend angetriebener, spanabhebender Werkzeuge 16 und 17 hergestellt werden, indem mindestens eine in Achsrichtung seitliche Begrenzungswand 18 des Kopplungsbügels 9 eine die Einführung des Schneidkopfes 19,20 des Werkzeuges 16,17 in den Kopplungsbügel 9 zulassende Öffnung 21 aufweist. Vorzugsweise befindet sich diese Öffnung 21 in der den Kolben 8 abgekehrten Begrenzungswand 18 des Kopplungsbügels 9, denn die diese Öffnung 21 umschließende, gegenüber der gegenüberliegenden Kugelfläche 15 kleinere Kugelfläche 14 wird nur während der Ansaugbewegung des Kolbens 8 belastet, und entsprechend durch kleinere Kräfte, als sie beim Kompressionshub auftreten.In an advantageous embodiment of the present invention, the spherical surfaces 14,15 as shown in Figures 9 and 10 by means of rotationally driven, cutting tools 16 and 17 are made by at least one axial boundary wall 18 of the coupling bracket 9 a the introduction of the cutting head 19th , 20 of the tool 16,17 in the coupling bracket 9 permitting opening 21 has. Preferably, this opening 21 is in the piston 8 facing away from the boundary wall 18 of the coupling bracket 9, because the opening 21 surrounding this, opposite the opposite spherical surface 15 smaller spherical surface 14 is loaded only during the suction movement of the piston 8, and correspondingly by smaller forces than they occur during the compression stroke.

Die Kolben 8 können als separates Teil hülsenförmig durch Tiefziehen hergestellt werden, um anschließend am Kopplungsbügel 9 befestigt zu werden. Der Kopplungsbügel 9 hingegen lässt sich auf einfache Weise als Abschnitt eines Strangprofils vorformen.The pistons 8 can be made as a separate part sleeve-shaped by deep drawing, to be subsequently attached to the coupling bracket 9. The coupling bracket 9, however, can be preformed in a simple manner as a section of an extruded profile.

Die zur Steuerung der Kolbenhubweite erforderliche schwenkbare Führung der Taumelscheibe 11 sowie die für ihren Drehantrieb erforderliche Kopplung mit der Triebwelle 4 erfolgt erfindungsgemäß durch ein Gelenkviereck 22, das durch zwei schwenkbar an der Triebwelle 4 gelagerte Gelenkarme 23,24, den Abstand zwischen den wellenseitigen Gelenken 25,26 und den Abstand zwischen taumelscheibenseitigen Gelenken 27,28 des Gelenkvierecks 22 gebildet wird.The required for controlling the Kolbenhubweite pivotable guidance of the swash plate 11 and required for their rotary drive coupling with the drive shaft 4 according to the invention by a four-bar linkage 22, by two pivotally mounted on the drive shaft 4 articulated arms 23,24, the distance between the shaft-side joints 25th , 26 and the distance between the swash plate side joints 27,28 of the four-bar linkage 22 is formed.

Für einen bei relativ geringem Durchmesser der Taumelscheibe 11 großen Verstellbereich der Hubweite der Kolben 8 und eine dadurch große, mögliche Förderleistung sind die wellenseitigen Gelenke 25,26 auf der den anderen Gelenken 27,28 gegenüberliegenden Seite der Wellenachse 30 an einer Wellenauskröpfung 29 vorgesehen, so dass sich diese durch eine exzentrisch in der Taumelscheibe 11 vorgesehene Öffnung 33 erstreckt. Außerdem kann die Taumelscheibe 11 durch die beschriebene Ausführung ihrer Kopplung mit den Kolben 8, über ihre gesamte radiale Erstreckung verhältnismäßig dünn ausgeführt werden, wodurch ein weiterer Beitrag für die Ausführung des Kompressors 1 mit möglichst großer Förderleistung gegeben ist.For a relatively large diameter of the swash plate 11 large adjustment range of the stroke of the piston 8 and thereby large, possible delivery capacity, the shaft side joints 25,26 on the other joints 27,28 opposite side of the shaft axis 30 at a Wellenauskröpfung 29 are provided so that this extends through an opening 33 provided eccentrically in the swash plate 11. In addition, the swash plate 11 can be made relatively thin by the described embodiment of their coupling with the piston 8, over its entire radial extent, whereby a further contribution to the design of the compressor 1 is given with the greatest possible flow rate.

Der gegenüber dem Abstand der wellenseitigen Gelenke 25,26 kleinere Abstand der Gelenke 27,28 des somit trapezförmigen Gelenkvierecks 22 wird durch die Höhe von beidseitig von der Taumelscheibe 11 abstehende, wangenartige Gelenkträger 31,32 bestimmt.The distance between the shaft-side joints 25,26 smaller distance of the joints 27,28 of the thus trapezoidal four-bar linkage 22 is determined by the height of both sides of the swash plate 11 projecting, cheek-like joint carrier 31,32.

Vorzugsweise ist das Gelenkviereck 22 beidseitig der Wellenauskröpfung 29, d.h. doppelt ausgeführt, wobei die Wellenauskröpfung 29 seitlich durch zueinander parallele Flächen 34,35 begrenzt ist, so dass diese die ebenfalls abgeflachten Gelenkarme 23,24 seitlich führen können. Die doppelseitigen Gelenkarme 23,24 sind dabei vorzugsweise durch einen Quersteg 36 starr miteinander verbunden, der auch einen Anschlag an der Triebwelle 3 für die maximale Schwenkbewegung der Gelenkarme 23,24 und damit der Taumelscheibe 11 bilden kann.Preferably, the four-bar linkage 22 is on both sides of the wave projection 29, i. Executed twice, wherein the Wellenauskröpfung 29 is bounded laterally by mutually parallel surfaces 34,35 so that they can also lead the flattened articulated arms 23,24 laterally. The double-sided articulated arms 23,24 are preferably rigidly connected together by a transverse web 36, which can also form a stop on the drive shaft 3 for the maximum pivotal movement of the articulated arms 23,24 and thus the swash plate 11.

Bei einfacher anstatt doppelter Ausführung des Gelenkvierecks können die Wellenauskröpfung und die an der Taumelscheibe 11 vorgesehenen Gelenkträger 31,32 einen nicht dargestellten zentralen Führungsschlitz für die beidseitige Führung eines flachen Gelenkarmes aufweisen.In the case of a simple instead of a double design of the four-bar linkage, the shaft projection and the articulated carriers 31, 32 provided on the swashplate 11 can have a central guide slot (not shown) for the double-sided guidance of a flat articulated arm.

Die Fig. 6 bis 8 zeigen drei Ausführungsbeispiele für die Gelenke 25 bis 28 eines doppelten Gelenkvierecks 22.6 to 8 show three embodiments of the joints 25 to 28 of a double four-bar linkage 22nd

Entsprechend Fig.6 ist ein Gelenkzapfen 37 entweder in den in den Gelenkarmen 23 vorgesehenen Bohrungen 38,39 durch eine Presspassung gesichert, so dass er in der gleichachsigen Bohrung 40 des Gelenkträgers 31 ein Gleitlager hat oder die Bohrungen 38,39 der Gelenkarme 23 bilden ein Gleitlager, so dass der Gelenkzapfen 37 in dem Gelenkträger 31 durch Presspassung gehalten ist.According to Fig.6 a pivot pin 37 is either secured in the provided in the articulated arms 23 holes 38,39 by a press fit so that it has a sliding bearing in the equiaxed bore 40 of the joint carrier 31 or the holes 38,39 of the articulated arms 23 form Slide bearing, so that the pivot pin 37 is held in the hinge bracket 31 by press-fitting.

Entsprechend Fig.7 ist beidseitig je ein mit einem Kopf 41,42 versehener Gelenkzapfen 43,44 nagelartig eingepresst. Beim Ausführungsbeispiel nach Fig.8 wird ein durchgehender Gelenkzapfen 45 verwendet, der einerseits durch einen Zapfenkopf 46 und anderseits durch einen Sicherungsring 47 axial gesichert ist.According to Figure 7 is on both sides each provided with a head 41,42 pivot pin 43,44 nested. In the embodiment of Figure 8, a continuous pivot pin 45 is used, which is axially secured on the one hand by a pin head 46 and on the other hand by a locking ring 47.

Da die beschriebenen Gelenke 25 bis 28 des Gelenkvierecks 22 somit als Drehgelenke ausgeführt sind, ergeben sich bei der Verstellbewegung gegenüber bisher üblichen Schubgelenken wesentlich geringere Reibungswiderstände, so dass auf diese Weise auch die eingangs genannte Aufgabe eines verbesserten Regelverhaltens gelöst wird.Since the described joints 25 to 28 of the four-bar linkage 22 are thus designed as swivel joints, substantially lower frictional resistances result in the adjustment movement compared to previously known push joints, so that in this way the object of improved control behavior mentioned at the outset is also achieved.

Claims (10)

  1. Reciprocating piston compressor with several cylinder-piston units (7, 8) positioned parallel to one another and to a drive shaft (4) in a common compressor casing (3), the drive shaft (4) being embraced by a wobble plate (11) swivellably coupled thereto and to which the pistons (8) are connected by means of an articulated sliding coupling (12,13),characterized in that the wobble plate (11) is coupled to the drive shaft (4) by means of a single or double four-bar linkage (22) having a swivellable articulated bracket (23, 24) and in each case one (27, 28) of the uniaxially implemented four joints (25 to 28) are bilaterally provided on the wobble plate (11), whilst two other joints (25, 26) are provided in axially spaced manner on the drive shaft (4).
  2. Compressor according to claim 1, characterized in that the joints (25, 26) provided with mutual axial spacing on the drive shaft (4) are provided on the side of the shaft axis (30) opposite to the wobble plate-side joints (27, 28) on a right-angled bend (29) of the drive shaft (4), so that the articulated brackets (23, 24) swivellable relative to the drive shaft (4) run at right angles to the drive shaft axis (30) and the bend (29) extends through an eccentric opening (33) of the wobble plate (11).
  3. Compressor according to claim 1 or 2, characterized in that cheek-like, laterally projecting joint supports (31, 32) are provided bilaterally on the wobble plate (11) and on each of the free ends thereof is located a joint (27, 28) of the single or double four-bar linkage (22).
  4. Compressor according to claim 3, characterized in that the joint supports (31, 32) and the right-angled bend (29) of the drive shaft (4) are laterally flattened and through each of these extends a hinge pin (37; 43, 44; 45) for the rotary mounting of flattened articulated brackets (23, 24) of a double four-bar linkage (22).
  5. Compressor according to one of the claims 1 to 4, characterized in that the joints (25 to 28) of the four-bar linkage (22) are uniaxial swivel joints (figs. 6 to 8).
  6. Compressor according to one of the claims 1 to 5, characterized in that in each case one articulated bracket pair (23 or 24) of a double four-bar linkage (22) through a connecting bar (36) forms a rigid unit.
  7. Compressor according to one of the claims 1 to 6, characterized in that the articulated sliding coupling between the wobble plate (11) and the pistons (8) has spherical segmental sliding pads (12, 13) bilaterally engaging on the wobble plate (11) and which are held in spherical bearing surfaces (14, 15) worked into lateral boundary walls (18) of a coupling bracket (9) connected to the pistons (8).
  8. Compressor according to claim 7, characterized in that at least one of the spherical bearing surfaces (14) surrounds an opening (21) in the adjacent, lateral boundary wall (18) of the coupling bracket (9).
  9. Compressor according to claim 8, characterized in that an opening (21) is provided in the lateral boundary wall (18) remote from the piston (8) and through it can be introduced a tool (16, 17) for the rotary working of the bearing surface (14) in coupling bracket (9).
  10. Compressor according to one of the claims 7 to 9, characterized in that the pistons (8) comprise a deep-drawn sleeve and are fixed to a coupling bracket (9) comprising a portion of an extruded profile.
EP05010105A 2004-06-14 2005-05-10 Piston compressor Active EP1607630B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004028747 2004-06-14
DE102004028747A DE102004028747A1 (en) 2004-06-14 2004-06-14 reciprocating compressor

Publications (2)

Publication Number Publication Date
EP1607630A1 EP1607630A1 (en) 2005-12-21
EP1607630B1 true EP1607630B1 (en) 2006-10-04

Family

ID=34936328

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05010105A Active EP1607630B1 (en) 2004-06-14 2005-05-10 Piston compressor

Country Status (7)

Country Link
US (1) US7267041B2 (en)
EP (1) EP1607630B1 (en)
JP (1) JP4448063B2 (en)
KR (1) KR100700861B1 (en)
CN (1) CN1715645B (en)
AT (1) ATE341710T1 (en)
DE (2) DE102004028747A1 (en)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004028747A1 (en) 2004-06-14 2005-12-29 Obrist Engineering Gmbh reciprocating compressor
JP4663545B2 (en) * 2006-02-16 2011-04-06 サンデン株式会社 Variable capacity compressor
JP4663546B2 (en) * 2006-02-17 2011-04-06 サンデン株式会社 Variable capacity compressor
JP4855118B2 (en) * 2006-03-28 2012-01-18 サンデン株式会社 Variable capacity compressor
DE102006031738A1 (en) * 2006-07-10 2008-01-17 Kastriot Merlaku Brake system e.g. disk brake, for e.g. motorcycle, has flat, disk-shaped container filled with liquid e.g. electrorheologica liquid, which changes their physical aggregation state of liquid to ductile or solid and vice versa
DE102006031855A1 (en) * 2006-07-10 2008-01-17 Kastriot Merlaku Brake device i.e. rotation brake, for single-lane vehicle e.g. bicycle or motor cycle, has pistons coupled with disk near to disk edge by lever, and hinge fixedly or flexibly connected with disk at end and with static part at another end
DE102006031747A1 (en) * 2006-07-10 2008-01-17 Kastriot Merlaku Brake system, for e.g. passenger car, has electro-valve that is installed in connection-channel, controller that is coupled with electro-valve, and rod or pivot that allows tumbling motion of disk and blocks rotation of disk
KR100792495B1 (en) 2007-02-07 2008-01-10 학교법인 두원학원 Assembly structure of drive shaft and swash plate for swash plate type compressor
KR100863221B1 (en) 2007-05-18 2008-10-13 학교법인 두원학원 2-step mechanism spring of a swash plate type compressor and the swash plate type compressor
US8499729B2 (en) * 2007-05-30 2013-08-06 High Density Powertrain, Inc. Super charged engine
US7823546B2 (en) * 2007-05-30 2010-11-02 High Density Powertrain, Inc. Super charged engine
AT10065U1 (en) * 2007-08-28 2008-08-15 Acc Austria Gmbh REFRIGERANT COMPRESSOR
US20090107327A1 (en) * 2007-10-03 2009-04-30 Masaki Ota Capacity-variable type swash plate compressor
KR100903034B1 (en) 2007-12-26 2009-06-18 학교법인 두원학원 Swash plate type compressor having link hinge mechanism
JP6047307B2 (en) 2012-05-28 2016-12-21 サンデンホールディングス株式会社 Variable capacity compressor
JP6171875B2 (en) * 2013-11-13 2017-08-02 株式会社豊田自動織機 Variable capacity swash plate compressor

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1170743B (en) * 1959-10-06 1964-05-21 Linde Eismasch Ag Hydrostatic transmission
US3861829A (en) * 1973-04-04 1975-01-21 Borg Warner Variable capacity wobble plate compressor
JPS58162783A (en) * 1982-03-20 1983-09-27 Toyoda Autom Loom Works Ltd Swash plate type variable displacement compressor
US4815358A (en) * 1988-01-27 1989-03-28 General Motors Corporation Balanced variable stroke axial piston machine
US4836090A (en) * 1988-01-27 1989-06-06 General Motors Corporation Balanced variable stroke axial piston machine
KR950003458Y1 (en) * 1990-11-29 1995-05-02 가부시끼가이샤 도요다지도쇽끼 세이사꾸쇼 Swash plate compressor
JPH08312528A (en) * 1995-05-22 1996-11-26 Calsonic Corp Swash plate type variable capacity compressor
JP2000110717A (en) * 1998-10-06 2000-04-18 Nippon Soken Inc Swash plate type variable capacity compressor
JP4332294B2 (en) * 2000-12-18 2009-09-16 サンデン株式会社 Manufacturing method of single-head swash plate compressor
JP2001323874A (en) 2001-05-24 2001-11-22 Zexel Valeo Climate Control Corp Variable displacement compressor
DE10250591B4 (en) * 2001-11-02 2018-01-18 Denso Corporation Compressor with guide grooves as connecting mechanism between drive pulley and shaft
JP2004068757A (en) * 2002-08-08 2004-03-04 Toyota Industries Corp Variable displacement compressor
DE102004028747A1 (en) 2004-06-14 2005-12-29 Obrist Engineering Gmbh reciprocating compressor

Also Published As

Publication number Publication date
DE102004028747A1 (en) 2005-12-29
CN1715645B (en) 2012-01-25
CN1715645A (en) 2006-01-04
EP1607630A1 (en) 2005-12-21
DE502005000133D1 (en) 2006-11-16
JP2006002770A (en) 2006-01-05
US20050276699A1 (en) 2005-12-15
US7267041B2 (en) 2007-09-11
KR100700861B1 (en) 2007-03-29
KR20060046465A (en) 2006-05-17
JP4448063B2 (en) 2010-04-07
ATE341710T1 (en) 2006-10-15

Similar Documents

Publication Publication Date Title
EP1607630B1 (en) Piston compressor
DE4411926C2 (en) Swash plate compressor with variable delivery rate
DE3609796C2 (en)
DE4290950C2 (en) Swash plate compressor
EP2999885B1 (en) Axial piston machine of swash plate type
EP2333336B1 (en) Reciprocating engine for use as a vacuum pump for medicinal purposes
DE69604972T2 (en) Swashplate compressor with variable delivery capacity and with an improved joint device to support the inclination of a swashplate
DE102006021570A1 (en) Hydrostatic piston machine with rotating control disc
DE69821274T2 (en) Swash plate compressors with variable delivery rates
DE69524783T2 (en) TILTING ANGLE CONTROL DEVICE FOR A SWASH DISC PUMP
DE102005018102A1 (en) Axial piston compressor for motor vehicle air conditioner, has support unit arranged at radial outer end of force transmitting unit that is hinged on support unit, where transmitting unit is rotatable and radially moveable on support unit
DE10209805A1 (en) Electronic bore pressure optimization mechanism for pumps, motors, has valve to which control signal is sent to adjust the size of variable orifice through which flow of fluid to pressure passage is detected
DE19712348C2 (en) Swash plate compressor with single-acting pistons
DE102007037199B4 (en) Taumelringverdichter with bearing of the wobble ring on two pivot pins
EP0752530B1 (en) Reciprocating piston machine with swash plate mechanism
DE10152097B4 (en) Adjustable swash plate compressor
EP1464836B1 (en) Axial piston compressor in particular CO2-compressor for a car air-conditioning apparatus
DE102013225899A1 (en) Swash plate machine, swashplate and method for hydrostatic discharge of an actuating part connection of a swashplate machine
DE102006052484A1 (en) Camshaft drive with a geometric roller stabilization
DE19515658C2 (en) Swashplate compressor with swiveling swashplate
DE102008015842A1 (en) piston compressor
DE102006044294B3 (en) Radial piston pump for internal combustion engine, has pump units with cross heads having cross head bolts that are supported in small lugs of piston rod, where lugs are designed as slotted holes with longitudinal axes
DE10358728B4 (en) Axial piston machine for independent pumping in several hydraulic circuits
DE19527649A1 (en) Axial piston machine with concentric cylinders - has guide device effective over entire lifting length of piston
DE10010132C2 (en) reciprocating engine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR LV MK YU

17P Request for examination filed

Effective date: 20060120

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061004

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061004

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061004

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061004

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061004

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061004

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20061004

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061004

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061004

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061004

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 502005000133

Country of ref document: DE

Date of ref document: 20061116

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20061116

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070104

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070104

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070104

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070115

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070204

ET Fr: translation filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070316

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20070705

BERE Be: lapsed

Owner name: OBRIST ENGINEERING GMBH

Effective date: 20070531

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070531

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070531

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070105

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061004

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070510

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070510

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061004

PGRI Patent reinstated in contracting state [announced from national office to epo]

Ref country code: IT

Effective date: 20090801

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070405

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090531

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090531

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20240521

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20240521

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20240529

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: TR

Payment date: 20240503

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20240524

Year of fee payment: 20