EP1438504B1 - Reciprocating piston motor comprising a sliding sleeve - Google Patents

Reciprocating piston motor comprising a sliding sleeve Download PDF

Info

Publication number
EP1438504B1
EP1438504B1 EP02704758A EP02704758A EP1438504B1 EP 1438504 B1 EP1438504 B1 EP 1438504B1 EP 02704758 A EP02704758 A EP 02704758A EP 02704758 A EP02704758 A EP 02704758A EP 1438504 B1 EP1438504 B1 EP 1438504B1
Authority
EP
European Patent Office
Prior art keywords
machine shaft
sliding body
cavity
driver
reciprocating piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02704758A
Other languages
German (de)
French (fr)
Other versions
EP1438504A2 (en
EP1438504B8 (en
Inventor
Roland Cäsar
Peter 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
Mercedes Benz Group AG
Original Assignee
Obrist Engineering GmbH
Daimler 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
Application filed by Obrist Engineering GmbH, Daimler AG filed Critical Obrist Engineering GmbH
Publication of EP1438504A2 publication Critical patent/EP1438504A2/en
Application granted granted Critical
Publication of EP1438504B1 publication Critical patent/EP1438504B1/en
Publication of EP1438504B8 publication Critical patent/EP1438504B8/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • 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

Definitions

  • the invention relates to a reciprocating engine according to the preamble of claim 1.
  • Machine shaft, driver, sliding sleeve and swivel disk are arranged in a so-called drive chamber in which gaseous working fluid of the reciprocating engine is present at a certain pressure.
  • the delivery volume and thus the delivery rate of the reciprocating engine are dependent on the pressure ratio between the suction side and pressure side of the piston or accordingly depending on the pressures in the cylinders on the one hand and in the drive chamber on the other.
  • the EP 0 896 153 A2 is to be taken as a refrigerant compressor for a motor vehicle air conditioning reciprocating engine, which comprises a machine shaft, a plurality of circularly arranged around the machine shaft pistons, and a driven by the machine shaft swash plate which engages via a hinge assembly to the piston.
  • the swash plate is pivotally connected via a driver for transmitting the drive forces to the machine shaft and pivotally mounted about a transversely oriented to the machine shaft hinge axis on a slider designed as a sliding body.
  • the gaseous working medium to be compressed by means of the pistons generally also comprises further, in particular liquid substances, such as lubricating oil and / or water.
  • the sliding body therefore has, on its inner side facing the machine shaft, a cavity for separating the solid or liquid from the gaseous components of the working medium, in which a bore guided through the machine shaft opens.
  • a bore guided through the machine shaft opens.
  • the bore can basically as a drain line for removing separated solid or liquid components of the Working medium can be used with appropriate pressure compensation.
  • a disadvantage of the known reciprocating engine is the fact to be considered that the separation or removal of the solid or liquid components of the gaseous working fluid can be made to a significant extent only in the range of a minimum deflection state of the swash plate, whereby the performance of the reciprocating engine is adversely affected accordingly ,
  • the object of the invention is to provide a reciprocating engine with improved performance.
  • the reciprocating piston engine according to the invention is characterized in that the cavity enclosed by the sliding body is formed by an annular groove which extends over the entire circumference of the sliding body over a large part of its inner side.
  • liquid and / or solid substances can be separated from the working medium of the reciprocating piston engine with the aid of the groove and the bore according to the invention.
  • the reciprocating engine according to the invention with the slide comprising the groove in conjunction with the drain line or the bore in the machine shaft allows separation of undesirable substances from the working fluid of the reciprocating engine by utilizing centrifugal and gravitational forces.
  • the space provided in the sliding body cavity or the groove are in other words for deflecting and guiding the reaching into the bore or the drain line flow.
  • the cavity has an opening to a drive chamber of the reciprocating engine, wherein the opening is arranged at a distance in the direction of the axis of rotation of the machine shaft to the mouth of the provided in the machine shaft bore or discharge line.
  • the working fluid supplied to the discharge line first passes through the opening into the cavity, is guided in this a certain distance parallel to the axis of rotation of the machine shaft and subsequently passes into the discharge line.
  • liquid and gaseous components of the working medium are separated from each other, in particular lubricants and other liquids are separated from a gaseous working fluid and returned in a corresponding arrangement by gravity in the drive chamber.
  • the opening in the region of a recess of the sliding body is arranged.
  • the bore is inclined and / or perpendicular and / or coaxial with the axis of rotation.
  • a particularly effective separation or removal of solid or liquid components can be achieved by the gaseous working medium.
  • a separation is particularly effective in a bore which is arranged inclined relative to the axis of rotation.
  • the swash plate which is connected via a driver for transmitting the drive forces articulated to the machine shaft and the other pivotally mounted about a transverse to the machine shaft hinge axis on a sliding body, wherein the sliding body in a Direction of the axis of rotation of the machine shaft has open recess which surrounds the driver at least partially.
  • the sliding body is preferably designed as a sleeve with a recess in the form of a one-sided open slot.
  • the driver protrudes in the assembled state through the slot and is thus surrounded on several sides of the sleeve.
  • Machine shaft, swivel disk and sliding body are preferably at least partially disposed in the drive chamber within the housing of the reciprocating engine in which the working medium to be compressed is present.
  • the sliding body may have a first abutment surface acting against the driver in the region of its recess and a second abutment surface acting against a holding element on the part of the machine shaft on an axial end side.
  • the stop surfaces serve to limit the movement of the sliding body on the machine shaft; they are arranged with respect to the driver in the axial direction respectively on the same side of the sliding body.
  • the stop surfaces are the extreme positions of the sliding body defined, wherein the first extreme position to be achieved when the swash plate and machine shaft include a minimum angle and the piston perform a maximum stroke during rotation of the swash plate. In this case, the first stop surface abuts against the driver.
  • the second extreme position is to be achieved when the swash plate with the machine shaft at least approximately encloses a right angle and thus assumes a "neutral position" in which the pistons of the reciprocating engine are not moved by the swash plate.
  • the second stop surface abuts against the holding member from the machine shaft.
  • the holding element is preferably designed as releasable from the machine shaft locking ring.
  • a spring element in particular a weak plate spring, is arranged between the holding element and the second stop surface of the sliding body.
  • the spring element is assigned to the holding element such that when the sliding body with its second stop surface completely compresses the spring element, the swash plate assumes its "neutral position".
  • the spring element is preferably only active when the sliding body is in the vicinity of its second extreme position.
  • the spring element continuously serves to balance forces on the sliding body.
  • Fig.1 is a longitudinal section through a reciprocating engine 1 in the form of a refrigerant compressor for a motor vehicle air conditioner shown.
  • the reciprocating piston engine 1 has a plurality of pistons 4 arranged in a machine housing 3. All piston axes 12 are arranged at a fixed distance from the axis of rotation 11, ie geometrically on a cylinder jacket about the machine shaft 2 around.
  • the pistons 4 are guided in cylindrical bushings 10, in which cylindrical compression chambers 13 are formed, the pistons 4 separating the compression chambers 13 from a so-called drive chamber 14 ("crankcase"). All piston axes 12 are aligned parallel to the axis of rotation 11 of the machine shaft 2.
  • the rotational movement of the machine shaft 2 is converted into a translational movement of the piston 4.
  • a sliding body is guided in the form of a sliding sleeve 9.
  • an annular swash plate 5 is mounted, wherein the swash plate 5 is displaceable together with the sliding sleeve 9 parallel to the direction of the axis of rotation 11.
  • two short pins are mounted on both sides, which define a transverse to the axis of rotation 11 of the machine shaft 2 aligned hinge axis 8 about which the swash plate 5 is pivotable.
  • a driver 7 is fixed in a recess 2a of the machine shaft 2, a driver 7 is fixed.
  • the driver 7 protrudes approximately at right angles from the machine shaft 2 and engages with a spherical articulation section in a radially open receptacle 15 on the part of the swash plate 5 (see. Fig. 2 ). Since the driver 7 is fixed to the machine shaft 2, the pivoting of the swash plate 5 is coupled to the hinge axis 8 to the sliding of the sliding sleeve 9.
  • the rotation of the machine shaft 2 is transmitted to the swashplate 5 via the driver 7 (rotational movement in the direction of the arrow w).
  • a main center plane extending through the axis of rotation 11 is defined, which separates a suction side from a pressure side of the reciprocating piston engine 1.
  • the main center plane rotates with the machine shaft 2.
  • the swash plate 5 is encompassed on its circumference in the region of each piston 4 by a joint arrangement 6 which slides over the swash plate 5 when it executes its rotational movement w.
  • inclination of the swash plate 5 relative to the machine shaft 2 causes the swash plate 5 in the course of its rotation, the piston located on the pressure side 4 to a compression movement and lying on the suction side of the piston 4 to a suction movement.
  • Fig. 2 is a simplified schematic diagram for power transmission between the machine shaft 2 and the piston 4 shown. Further information on the structure and function of the reciprocating engine 1 are from the DE 197 49 727 A1 to which reference is expressly incorporated herein by reference. At the time of the DE 197 49 727 A1 known variant of the reciprocating engine, the sliding path of the sliding sleeve is limited by abutment of a slot on the driver to both sides. This means that the driver protrudes through the slot and can be pressed into the machine shaft into this only after pushing the sliding sleeve. This causes considerable assembly problems.
  • a recess 9a which is open in the direction of the axis of rotation 11 of the machine shaft 2 is provided in the sliding sleeve 9 instead of an oblong hole, which recess partially surrounds the driver 7 in the mounted state.
  • a first stop surface 21 is provided in the region of the recess 9 a, which, as in the FIGS. 2 and 3 shown against the driver 7 abuts when the sliding sleeve 9 is in its first, lower extreme position.
  • the first, lower extreme position of the sliding sleeve 9 corresponds to an orientation of the swash plate 5, in which the swash plate 5 encloses a minimum angle with the machine shaft 2 and the pistons 4 perform a maximum stroke during rotation of the swash plate 5.
  • a second stop surface 22 is further provided, which is assigned as a counterpart on the part of the machine shaft 2, a holding element in the form of a securing ring 20.
  • a spring element in the form of a weak plate spring 23 is provided between spring ring 20 and stop surface 22.
  • the swash plate with the machine shaft includes at least approximately a right angle and is thus in a "neutral position", in which the piston. 4 the reciprocating engine 1 are not moved by the swash plate.
  • the swash plate 5 can be kept in the pressure-balanced state of the compressor at a certain distance from its "neutral position", so that the conveying effect begins immediately after initiation.
  • Fig. 3 the sliding sleeve 9 according to the invention is shown in perspective.
  • the stop surfaces 21, 22 are arranged in the mounted state in the direction of the axis of rotation 11 on the same side of the driver 7.
  • the piston stroke and thus the delivery volume of the reciprocating engine 1 is effected by changing the pivot angle of the swash plate 5.
  • the pivot angle preferably changes with the pressure in the drive chamber 14, which acts directly on the underside of the piston 4.
  • the delivery volume can therefore be regulated by changing the pressure in the drive chamber. This happens, for example, in that the drive chamber 14 through a small throttle (not shown) constantly fed a small amount of funded by the reciprocating engine 1 working medium from the high pressure side and that the amount of the drive from the drive (possibly to the suction side) flowing through the working medium a control valve is determined.
  • a drain line is provided - formed from the bores 24, 25, over which the medium from the drive chamber 14 can be removed.
  • FIG. 2 schematically another embodiment of a drain line in the form of holes 24, 26 is shown.
  • the holes 24, 25, 26 again from the 4 and 5 seen.
  • an annular groove 18 is provided which extends over the entire circumference over a large part of the inside of the sliding sleeve.
  • a cavity 17 In the installed position ( Fig. 1 . 2 . 4 and 5 ) is formed between the sliding sleeve 9 and the machine shaft 2, a cavity 17.
  • the cavity 17 is connected to the drive chamber 14 through the recess 9a and possibly through further openings.
  • the bores 25, 26 lead through the machine shaft 2 radially inwardly to the coaxial drain hole 24, so that the drive chamber 14 is connected via the bores 25, 26 with the drain hole 24.
  • the bore 25 in the shaft 2 is arranged so that it is perpendicular to the axis of rotation 11, while the bore 26 is inclined to the axis of rotation 11.
  • the drive chamber 14 is located during operation of the reciprocating engine 1 in general, not only to be compressed by the reciprocating engine 1 working fluid, but also other, especially liquid substances such as lubricating oil and / or water. This may result in an unwanted manner present in the drive chamber 14 mixture of the working fluid and the other substances.
  • liquid and / or solid substances from the working medium of the reciprocating engine 1 can be deposited.
  • the arrow A with a solid line indicates the path of the mixture, on which increasingly undesirable liquid and / or solid substances are deposited, which in particular return to the drive chamber 14 under the influence of gravity on a path indicated by the dashed arrow B.
  • Such a separation is particularly effective in the bore 26 which is arranged inclined relative to the axis of rotation 11.
  • the bore 24 may be shorter, ie less deep than in the embodiment according to Figure 4 ,
  • the proposed, designed as a sliding sleeve sliding body 9 can be stuck on the machine shaft 2 and the driver 7, even if they are firmly connected. It is therefore possible to carry out a pressing in of the driver 7 in the machine shaft 2 or to perform the machine shaft 2 and the driver 7 in one piece in a first assembly step. Since the bending stress of the driver 7 continues into the associated recess 9a in the machine shaft 2, so that micro-displacements occur in the press joint during an interference fit between the driver 7 and the machine shaft 2, the flexural rigidity of the carrier 7 can be increased, thereby reducing bending are when the driver 7 and the machine shaft 2 consist of one piece. It results in a higher load capacity of driver 7 and machine shaft 2, resulting in an improved performance of the reciprocating engine 1 results.
  • the reciprocating engine 1 according to the invention with the groove 18 comprising the sliding sleeve 9 in conjunction with the drain line or bores 24, 25, 26 in the machine shaft 2 allows separation of undesirable substances from the working fluid of the reciprocating engine 1 by utilizing centrifugal and gravitational forces , Thus, pure working fluid can be removed from the drive chamber 14, resulting in improved controllability and thus improved performance of the reciprocating engine 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)

Abstract

In a reciprocating-piston machine, in particular a refrigerant compressor for a motor vehicle air-conditioning system, including a machine shaft rotatably supported in a housing, a plurality of pistons arranged circularly around the machine shaft in the housing, and an annular pivoting disc driven by the machine shaft and engaging the pistons via a joint arrangement, the pivoting disc being connected in an articulated manner to the machine shaft via a driver for transmitting the machine shaft drive forces to the pistons and mounted on a machine shaft-supported sliding body so as to be pivotable about a hinge axis oriented transversely to the machine shaft, the sliding body has an elongated recess which is open at one axial end for receiving the driver and the sliding body further includes at its inside adjacent the machine shaft a cavity, which is in communication with a bore forming a discharge passage extending through the machine shaft.

Description

Die Erfindung betrifft eine Hubkolbenmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to a reciprocating engine according to the preamble of claim 1.

Aus der Patentschrift DE 197 49 727 C2 ist eine gattungsgemäße Hubkolbenmaschine bekannt. Sie umfasst ein Maschinengehäuse, in dem in einer kreisförmigen Anordnung mehrere Kolben um eine rotierende Antriebswelle herum angeordnet sind. Die Antriebskraft wird von der Antriebswelle über einen Mitnehmer auf eine ringförmige Schwenkscheibe und von dieser wiederum auf die parallel zur Maschinenwelle translatorisch verschiebbaren Kolben übertragen. Dabei ist die Schwenkscheibe an einer linear verschieblich an der Maschinenwelle befestigten Hülse schwenkbar gelagert. In der Hülse ist ein Langloch vorgesehen, durch das der Mitnehmer hindurchgreift, somit ist die axiale Beweglichkeit der Hülse auf der Maschinenwelle durch die Abmessungen des Langloches begrenzt. Eine Montage erfolgt durch ein Hindurchstecken des Mitnehmers durch das Langloch. Maschinenwelle, Mitnehmer, Schiebehülse und Schwenkscheibe sind in einem sogenannten Triebraum angeordnet, in dem gasförmiges Arbeitsmedium der Hubkolbenmaschine mit einem bestimmten Druck vorliegt. Das Fördervolumen und damit die Förderleistung der Hubkolbenmaschine sind abhängig vom Druckverhältnis zwischen Saugseite und Druckseite der Kolben bzw. entsprechend abhängig von den Drücken in den Zylindern einerseits und im Triebraum andererseits.From the patent DE 197 49 727 C2 is a generic reciprocating engine known. It comprises a machine housing in which a plurality of pistons are arranged around a rotating drive shaft in a circular arrangement. The driving force is transmitted from the drive shaft via a driver on an annular swash plate and from this in turn to the parallel to the machine shaft translationally displaceable piston. In this case, the swash plate is pivotally mounted on a sleeve mounted linearly displaceable on the machine shaft. In the sleeve, a slot is provided, through which engages the driver, thus the axial mobility of the sleeve is limited to the machine shaft by the dimensions of the elongated hole. An assembly takes place by a passing through the driver through the slot. Machine shaft, driver, sliding sleeve and swivel disk are arranged in a so-called drive chamber in which gaseous working fluid of the reciprocating engine is present at a certain pressure. The delivery volume and thus the delivery rate of the reciprocating engine are dependent on the pressure ratio between the suction side and pressure side of the piston or accordingly depending on the pressures in the cylinders on the one hand and in the drive chamber on the other.

Aus der EP 0 896 153 A2 ist eine als Kältemittelkompressor für eine Kraftfahrzeug-Klimaanlage ausgebildete Hubkolbenmaschine zu entnehmen, welche eine Maschinenwelle, mehrere kreisförmig um die Maschinenwelle herum angeordneten Kolben, sowie eine von der Maschinenwelle angetriebene Schwenkscheibe umfasst, die über eine Gelenkanordnung an den Kolben angreift. Die Schwenkscheibe ist dabei über einen Mitnehmer zur Übertragung der Antriebskräfte gelenkig mit der Maschinenwelle verbunden und schwenkbar um eine quer zur Maschinenwelle orientierten Scharnierachse an einem als Schiebehülse ausgebildeten Schiebekörper gelagert. Beim Betrieb der Hubkolbenmaschine umfasst das mit Hilfe der Kolben zu verdichtende, gasförmige Arbeitsmedium im allgemeinen auch weitere, insbesondere flüssige Substanzen wie Schmieröl und/oder Wasser. Daraus kann sich in einem Triebraum der Hubkolbenmaschine in unerwünschter Weise ein Gemisch aus dem Arbeitsmedium und den weiteren Substanzen ergeben. Der Schiebekörper weist daher auf seiner der Maschinenwelle zugewandten Innenseite einen Hohlraum zur Trennung der festen bzw. flüssigen von den gasförmigen Bestandteilen des Arbeitsmediums auf, in welchem eine durch die Maschinenwelle geführte Bohrung mündet. Über eine Öffnung steht der Hohlraum mit dem Triebraum der Hubkolbenmaschine in Wirkverbindung, wobei die Öffnung in Abhängigkeit einer Position des Schiebekörpers bzw. einer damit verbundenen Auslenkung der Schwenkscheibe in einem Abstand in Richtung der Drehachse der Maschinenwelle zur Mündung der durch die Maschinenwelle geführten Bohrung angeordnet ist. Die Bohrung kann dabei grundsätzlich als Abflußleitung zum Entfernen von abgetrennten festen oder flüssigen Bestandteilen des Arbeitsmediums mit entsprechendem Druckausgleich verwendet werden.From the EP 0 896 153 A2 is to be taken as a refrigerant compressor for a motor vehicle air conditioning reciprocating engine, which comprises a machine shaft, a plurality of circularly arranged around the machine shaft pistons, and a driven by the machine shaft swash plate which engages via a hinge assembly to the piston. The swash plate is pivotally connected via a driver for transmitting the drive forces to the machine shaft and pivotally mounted about a transversely oriented to the machine shaft hinge axis on a slider designed as a sliding body. During operation of the reciprocating engine, the gaseous working medium to be compressed by means of the pistons generally also comprises further, in particular liquid substances, such as lubricating oil and / or water. This may result in a drive chamber of the reciprocating engine undesirably a mixture of the working fluid and the other substances. The sliding body therefore has, on its inner side facing the machine shaft, a cavity for separating the solid or liquid from the gaseous components of the working medium, in which a bore guided through the machine shaft opens. About an opening of the cavity with the drive chamber of the reciprocating engine is in operative connection, wherein the opening is arranged in dependence on a position of the sliding body or an associated deflection of the swash plate at a distance in the direction of the axis of rotation of the machine shaft to the mouth of the guided through the machine shaft bore , The bore can basically as a drain line for removing separated solid or liquid components of the Working medium can be used with appropriate pressure compensation.

Als nachteilig an der bekannten Hubkolbenmaschine ist dabei der Umstand anzusehen, dass die Abtrennung bzw. Entfernung der festen bzw. flüssigen Bestandteile vom gasförmigen Arbeitsmedium nur im Bereich eines minimalen Auslenkungszustands der Schwenkscheibe in nennenswertem Umfang erfolgen kann, wodurch das Betriebsverhalten der Hubkolbenmaschine entsprechend nachteilig beeinflusst wird.A disadvantage of the known reciprocating engine is the fact to be considered that the separation or removal of the solid or liquid components of the gaseous working fluid can be made to a significant extent only in the range of a minimum deflection state of the swash plate, whereby the performance of the reciprocating engine is adversely affected accordingly ,

Aufgabe der Erfindung ist es, eine Hubkolbenmaschine mit einem verbesserten Betriebsverhalten bereitzustellen.The object of the invention is to provide a reciprocating engine with improved performance.

Diese Aufgabe wird durch eine Hubkolbenmaschine mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved by a reciprocating engine having the features of claim 1.

Die erfindungsgemäße Hubkolbenmaschine zeichnet sich dadurch aus, daß der vom Schiebekörper umschlossene Hohlraum durch eine ringförmige Nut gebildet ist, die sich entlang des gesamten Umfangs des Schiebekörpers über einen Großteil seiner Innenseite erstreckt. Mit Hilfe der erfindungsgemäßen Nut und der Bohrung können insbesondere flüssige und/oder feste Substanzen aus dem Arbeitsmedium der Hubkolbenmaschine abgeschieden werden. Hierdurch ermöglicht die erfindungsgemäße Hubkolbenmaschine mit dem die Nut umfassenden Schiebekörper in Verbindung mit der Abflußleitung bzw. der Bohrung in der Maschinenwelle eine Abscheidung von unerwünschten Substanzen aus dem Arbeitsmedium der Hubkolbenmaschine unter Ausnutzung von Flieh- und Schwerkrafteinflüssen. Der im Schiebekörper vorgesehene Hohlraum bzw. die Nut dienen mit anderen Worten zur Umlenkung und Führung der in die Bohrung bzw. die Abflußleitung gelangenden Strömung. Infolge der gemeinsamen Rotation des Schiebekörpers mit der Maschinenwelle wird auf das in der Nut bzw. im Hohlraum befindliche Arbeitsmedium eine Zentrifugalkraft ausgeübt. Innerhalb der Nut bzw. des Hohlraumes kann eine Phasentrennung eines durchströmenden Stoffgemisches erfolgen. Somit kann reines Arbeitsmedium aus dem Triebraum abgeführt werden, wodurch sich eine verbesserte Steuerbarkeit und somit ein verbessertes Betriebsverhalten der Hubkolbenmaschine ergibt.The reciprocating piston engine according to the invention is characterized in that the cavity enclosed by the sliding body is formed by an annular groove which extends over the entire circumference of the sliding body over a large part of its inner side. In particular, liquid and / or solid substances can be separated from the working medium of the reciprocating piston engine with the aid of the groove and the bore according to the invention. In this way, the reciprocating engine according to the invention with the slide comprising the groove in conjunction with the drain line or the bore in the machine shaft allows separation of undesirable substances from the working fluid of the reciprocating engine by utilizing centrifugal and gravitational forces. The space provided in the sliding body cavity or the groove are in other words for deflecting and guiding the reaching into the bore or the drain line flow. As a result of the joint rotation of the Sliding body with the machine shaft is applied to the located in the groove or in the cavity working fluid a centrifugal force. Within the groove or the cavity, a phase separation of a flowing mixture of substances can take place. Thus, pure working fluid can be removed from the engine room, resulting in improved controllability and thus improved performance of the reciprocating engine.

In Ausgestaltung der Erfindung weist der Hohlraum eine Öffnung zu einem Triebraum der Hubkolbenmaschine auf, wobei die Öffnung mit einem Abstand in Richtung der Drehachse der Maschinenwelle zur Mündung der in der Maschinenwelle vorgesehenen Bohrung bzw. Abflußleitung angeordnet ist. Das der Abflußleitung zugeführte Arbeitsmedium gelangt über die Öffnung zunächst in den Hohlraum, wird in diesem eine gewisse Wegstrecke parallel zur Drehachse der Maschinenwelle geführt und gelangt nachfolgend in die Abflußleitung. In dem Hohlraum werden flüssige und gasförmige Bestandteile des Arbeitsmediums voneinander getrennt, insbesondere werden Schmierstoffe und andere Flüssigkeiten aus einem gasförmigen Arbeitsmedium abgeschieden und bei einer entsprechenden Anordnung durch Schwerkrafteinflüsse in den Triebraum zurückgeführt.In an embodiment of the invention, the cavity has an opening to a drive chamber of the reciprocating engine, wherein the opening is arranged at a distance in the direction of the axis of rotation of the machine shaft to the mouth of the provided in the machine shaft bore or discharge line. The working fluid supplied to the discharge line first passes through the opening into the cavity, is guided in this a certain distance parallel to the axis of rotation of the machine shaft and subsequently passes into the discharge line. In the cavity, liquid and gaseous components of the working medium are separated from each other, in particular lubricants and other liquids are separated from a gaseous working fluid and returned in a corresponding arrangement by gravity in the drive chamber.

In weiterer Ausgestaltung der Erfindung ist die Öffnung im Bereich einer Ausnehmung des Schiebekörpers angeordnet. Dadurch ist auf einfache Weise eine relativ große Öffnung geschaffen, die in ausreichender Entfernung zur Mündung der Abflußleitung angeordnet ist.In a further embodiment of the invention, the opening in the region of a recess of the sliding body is arranged. As a result, a relatively large opening is provided in a simple manner, which is arranged at a sufficient distance from the mouth of the discharge line.

In weiterer Ausgestaltung der Erfindung ist vorgesehen, dass die Bohrung geneigt und/oder senkrecht und/oder koaxial zur Drehachse verläuft. Durch eine senkrecht bzw. koaxial zur Drehachse verlaufende Bohrung kann eine besonders effektive Abtrennung bzw. Entfernung der festen bzw. flüssiges Bestandteile vom gasförmigen Arbeitsmedium erzielt werden. Eine Separierung erfolgt besonders effektiv auch in einer Bohrung, die gegenüber der Drehachse geneigt angeordnet ist.In a further embodiment of the invention, it is provided that the bore is inclined and / or perpendicular and / or coaxial with the axis of rotation. By a vertical or coaxial to Rotary axis extending bore a particularly effective separation or removal of solid or liquid components can be achieved by the gaseous working medium. A separation is particularly effective in a bore which is arranged inclined relative to the axis of rotation.

Zur einfachen Montage der Hubkolbenmaschine trägt erläuternd bei, dass die Schwenkscheibe, die zum einen über einen Mitnehmer zur Übertragung der Antriebskräfte gelenkig mit der Maschinenwelle verbunden und zum anderen schwenkbar um eine quer zur Maschinenwelle orientierte Scharnierachse an einem Schiebekörper gelagert ist, wobei der Schiebekörper eine in Richtung der Drehachse der Maschinenwelle geöffnete Ausnehmung aufweist, die den Mitnehmer wenigstens teilweise umgreift. Der Schiebekörper ist vorzugsweise als Hülse mit einer Ausnehmung in Form eines einseitig offenen Langloches gestaltet. Damit lässt sich die Hülse über Maschinenwelle und Mitnehmer stecken, auch wenn diese fest miteinander verbunden sind. Der Mitnehmer ragt dabei im montierten Zustand durch das Langloch und ist somit an mehreren Seiten von der Hülse umgeben. Maschinenwelle, Schwenkscheibe und Schiebekörper sind vorzugsweise wenigstens teilweise im Triebraum innerhalb des Gehäuses der Hubkolbenmaschine angeordnet, in dem das zu verdichtende Arbeitsmedium vorliegt.For ease of assembly of the reciprocating engine contributes explanatory in that the swash plate, which is connected via a driver for transmitting the drive forces articulated to the machine shaft and the other pivotally mounted about a transverse to the machine shaft hinge axis on a sliding body, wherein the sliding body in a Direction of the axis of rotation of the machine shaft has open recess which surrounds the driver at least partially. The sliding body is preferably designed as a sleeve with a recess in the form of a one-sided open slot. Thus, the sleeve can be stuck on the machine shaft and driver, even if they are firmly connected. The driver protrudes in the assembled state through the slot and is thus surrounded on several sides of the sleeve. Machine shaft, swivel disk and sliding body are preferably at least partially disposed in the drive chamber within the housing of the reciprocating engine in which the working medium to be compressed is present.

Weiterhin kann der Schiebekörper eine gegen den Mitnehmer wirkende erste Anschlagfläche im Bereich seiner Ausnehmung und eine gegen ein Halteelement seitens der Maschinenwelle wirkende zweite Anschlagfläche an einer axialen Stirnseite aufweisen. Die Anschlagflächen dienen zur Begrenzung der Bewegung des Schiebekörpers auf der Maschinenwelle; sie sind bezüglich des Mitnehmers in axialer Richtung jeweils auf der gleiche Seite des Schiebekörpers angeordnet. Mit Hilfe der Anschlagflächen sind die Extrempositionen des Schiebekörpers definiert, wobei die erste Extremposition dann erreicht sein soll, wenn Schwenkscheibe und Maschinenwelle einen minimalen Winkel einschließen und die Kolben bei einer Rotation der Schwenkscheibe einen maximalen Hub ausführen. In diesem Fall stößt die erste Anschlagfläche gegen den Mitnehmer. Die zweite Extremposition soll erreicht sein, wenn die Schwenkscheibe mit der Maschinenwelle wenigstens näherungsweise einen rechten Winkel einschließt und somit eine "Neutralposition" einnimmt, in der die Kolben der Hubkolbenmaschine durch die Schwenkscheibe nicht bewegt werden. In diesem Fall stößt die zweite Anschlagfläche gegen das Halteelement seitens der Maschinenwelle. Das Halteelement ist vorzugsweise als von der Maschinenwelle lösbarer Sicherungsring gestaltet.Furthermore, the sliding body may have a first abutment surface acting against the driver in the region of its recess and a second abutment surface acting against a holding element on the part of the machine shaft on an axial end side. The stop surfaces serve to limit the movement of the sliding body on the machine shaft; they are arranged with respect to the driver in the axial direction respectively on the same side of the sliding body. With the help of the stop surfaces are the extreme positions of the sliding body defined, wherein the first extreme position to be achieved when the swash plate and machine shaft include a minimum angle and the piston perform a maximum stroke during rotation of the swash plate. In this case, the first stop surface abuts against the driver. The second extreme position is to be achieved when the swash plate with the machine shaft at least approximately encloses a right angle and thus assumes a "neutral position" in which the pistons of the reciprocating engine are not moved by the swash plate. In this case, the second stop surface abuts against the holding member from the machine shaft. The holding element is preferably designed as releasable from the machine shaft locking ring.

Als weiteres Erläuterungsbeispiel ist zwischen dem Halteelement und der zweiten Anschlagfläche des Schiebekörpers ein Federelement, insbesondere eine schwache Tellerfeder, angeordnet. Vorzugsweise ist das Federelement dem Halteelement derart zugeordnet, daß wenn der Schiebekörper mit seiner zweiten Anschlagfläche das Federelement vollständig zusammendrückt, die Schwenkscheibe ihre "Neutralposition" einnimmt. Das Federelement ist vorzugsweise lediglich dann aktiv, wenn sich der Schiebekörper in der Nähe seiner zweiten Extremposition befindet. In einem modifizierten Beispiel dient das Federelement kontinuierlich zur Ausbalancierung von Kräften am Schiebekörper.As a further illustrative example, a spring element, in particular a weak plate spring, is arranged between the holding element and the second stop surface of the sliding body. Preferably, the spring element is assigned to the holding element such that when the sliding body with its second stop surface completely compresses the spring element, the swash plate assumes its "neutral position". The spring element is preferably only active when the sliding body is in the vicinity of its second extreme position. In a modified example, the spring element continuously serves to balance forces on the sliding body.

Weitere Merkmale und Merkmalskombinationen ergeben sich aus der Beschreibung sowie den Zeichnungen. Konkrete Ausführungsbeispiele der Erfindung sind in den Zeichnungen vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
einen Längsschnitt durch eine Hubkolbenmaschine,
Fig. 2
eine Prinzipskizze zur Funktion der Hubkolbenmaschine gemäss Fig.1,
Fig. 3
ein Schiebekörper der Hubkolbenmaschine in einer räumlichen Garstellung,
Fig. 4
eine Querschnitt durch Schiebekörper und Maschinenwelle der Hubkolbenmaschine gemäss Fig.1 sowie
Fig. 5
einen Querschnitt durch einen Schiebekörper und eine gegenüber Fig. 4 modifizierte Maschinenwelle der Hubkolbenmaschine.
Further features and combinations of features result from the description and the drawings. Concrete embodiments of the invention are shown in simplified form in the drawings and explained in more detail in the following description. Show it:
Fig. 1
a longitudinal section through a reciprocating engine,
Fig. 2
a schematic diagram of the function of the reciprocating engine according to Fig.1 .
Fig. 3
a sliding body of the reciprocating engine in a spatial cooking position,
Fig. 4
a cross section through sliding body and machine shaft of the reciprocating engine according to Fig.1 such as
Fig. 5
a cross section through a sliding body and a opposite Fig. 4 modified machine shaft of the reciprocating engine.

In Fig.1 ist ein Längsschnitt durch eine Hubkolbenmaschine 1 in Form eines Kältemittelkompressors für eine Kraftfahrzeug Klimaanlage dargestellt. Die Hubkolbenmaschine 1 weist mehrere in einem Maschinengehäuse 3 angeordnete Kolben 4 auf. Sämtliche Kolbenachsen 12 sind in einem festen Abstand zur Drehachse 11, d. h. geometrisch auf einem Zylindermantel um die Maschinenwelle 2 herum angeordnet. Die Kolben 4 sind in zylindrischen Laufbuchsen 10 geführt, in denen zylindrische Verdichtungsräume 13 gebildet sind, wobei die Kolben 4 die Verdichtungsräume 13 von einem sogenannten Triebraum 14 ("Kurbelgehäuse") abtrennen. Alle Kolbenachsen 12 sind parallel zur Drehachse 11 der Maschinenwelle 2 ausgerichtet. Über eine nachfolgend näher erläuterte Kraftübertragungsanordnung wird die Rotationsbewegung der Maschinenwelle 2 in eine Translationsbewegung der Kolben 4 übergeführt. Auf der Maschinenwelle 2 ist ein Schiebekörper in Form einer Schiebehülse 9 geführt. An der Schiebehülse 9 ist wiederum eine kreisringförmige Schwenkscheibe 5 gelagert, wobei die Schwenkscheibe 5 gemeinsam mit der Schiebehülse 9 parallel zur Richtung der Drehachse 11 verschiebbar ist. An der Schiebehülse 9 sind beidseitig zwei kurze Zapfen angebracht, die eine quer zur Drehachse 11 der Maschinenwelle 2 ausgerichtete Scharnierachse 8 definieren, um die die Schwenkscheibe 5 schwenkbar ist.In Fig.1 is a longitudinal section through a reciprocating engine 1 in the form of a refrigerant compressor for a motor vehicle air conditioner shown. The reciprocating piston engine 1 has a plurality of pistons 4 arranged in a machine housing 3. All piston axes 12 are arranged at a fixed distance from the axis of rotation 11, ie geometrically on a cylinder jacket about the machine shaft 2 around. The pistons 4 are guided in cylindrical bushings 10, in which cylindrical compression chambers 13 are formed, the pistons 4 separating the compression chambers 13 from a so-called drive chamber 14 ("crankcase"). All piston axes 12 are aligned parallel to the axis of rotation 11 of the machine shaft 2. About a subsequently explained in more detail power transmission arrangement, the rotational movement of the machine shaft 2 is converted into a translational movement of the piston 4. On the machine shaft 2, a sliding body is guided in the form of a sliding sleeve 9. On the sliding sleeve 9 is in turn an annular swash plate 5 is mounted, wherein the swash plate 5 is displaceable together with the sliding sleeve 9 parallel to the direction of the axis of rotation 11. On the sliding sleeve 9, two short pins are mounted on both sides, which define a transverse to the axis of rotation 11 of the machine shaft 2 aligned hinge axis 8 about which the swash plate 5 is pivotable.

In einer Ausnehmung 2a der Maschinenwelle 2 ist ein Mitnehmer 7 festgelegt. Der Mitnehmer 7 ragt in etwa rechtwinklig von der Maschinenwelle 2 ab und greift mit einem kugelförmigen Anlenkabschnitt in eine radial geöffnete Aufnahme 15 seitens der Schwenkscheibe 5 ein (vgl. Fig. 2). Da der Mitnehmer 7 an der Maschinenwelle 2 festgelegt ist, ist das Verschwenken der Schwenkscheibe 5 um die Scharnierachse 8 an das Verschieben der Schiebehülse 9 gekoppelt. Über den Mitnehmer 7 wird im Betrieb der Hubkolbenmaschine 1 die Rotation der Maschinenwelle 2 auf die Schwenkscheibe 5 übertragen (Drehbewegung in Richtung des Pfeils w).In a recess 2a of the machine shaft 2, a driver 7 is fixed. The driver 7 protrudes approximately at right angles from the machine shaft 2 and engages with a spherical articulation section in a radially open receptacle 15 on the part of the swash plate 5 (see. Fig. 2 ). Since the driver 7 is fixed to the machine shaft 2, the pivoting of the swash plate 5 is coupled to the hinge axis 8 to the sliding of the sliding sleeve 9. During operation of the reciprocating piston engine 1, the rotation of the machine shaft 2 is transmitted to the swashplate 5 via the driver 7 (rotational movement in the direction of the arrow w).

Senkrecht zur Scharnierachse 8 ist eine durch die Drehachse 11 verlaufende Hauptmittelebene definiert, die eine Saugseite von einer Druckseite der Hubkolbenmaschine 1 trennt. Die Hauptmittelebene rotiert mit der Maschinenwelle 2. Die Schwenkscheibe 5 ist an ihrem Umfang im Bereich eines jeden Kolbens 4 von einer Gelenkanordnung 6 umgriffen, die über die Schwenkscheibe 5 gleitet, wenn diese ihre Rotationsbewegung w ausführt. Bei einer (in den Fig. 1 und 2 dargestellten) Neigung der Schwenkscheibe 5 gegenüber der Maschinenwelle 2, veranlasst die Schwenkscheibe 5 im Verlauf ihrer Rotationsbewegung die auf der Druckseite befindlichen Kolben 4 zu einer Kompressionsbewegung und die auf der Saugseite liegenden Kolben 4 zu einer Ansaugbewegung.Perpendicular to the hinge axis 8, a main center plane extending through the axis of rotation 11 is defined, which separates a suction side from a pressure side of the reciprocating piston engine 1. The main center plane rotates with the machine shaft 2. The swash plate 5 is encompassed on its circumference in the region of each piston 4 by a joint arrangement 6 which slides over the swash plate 5 when it executes its rotational movement w. At one (in the Fig. 1 and 2 shown) inclination of the swash plate 5 relative to the machine shaft 2, causes the swash plate 5 in the course of its rotation, the piston located on the pressure side 4 to a compression movement and lying on the suction side of the piston 4 to a suction movement.

In Fig. 2 ist eine vereinfachte Prinzipskizze zur Kraftübertragung zwischen der Maschinenwelle 2 und dem Kolben 4 dargestellt. Weitere Angaben zum Aufbau und zur Funktion der Hubkolbenmaschine 1 sind aus der DE 197 49 727 A1 zu entnehmen, auf die hiermit ausdrücklich Bezug genommen wird. Bei der aus der DE 197 49 727 A1 bekannten Ausführungsvariante der Hubkolbenmaschine wird der Schiebeweg der Schiebehülse durch Anschlag eines Langlochs am Mitnehmer nach beiden Seiten begrenzt. Dies bedeutet, daß der Mitnehmer durch das Langloch hindurch ragt und erst nach Aufschieben der Schiebehülse auf die Maschinenwelle in diese eingepresst werden kann. Dies verursacht erhebliche Montageprobleme.In Fig. 2 is a simplified schematic diagram for power transmission between the machine shaft 2 and the piston 4 shown. Further information on the structure and function of the reciprocating engine 1 are from the DE 197 49 727 A1 to which reference is expressly incorporated herein by reference. At the time of the DE 197 49 727 A1 known variant of the reciprocating engine, the sliding path of the sliding sleeve is limited by abutment of a slot on the driver to both sides. This means that the driver protrudes through the slot and can be pressed into the machine shaft into this only after pushing the sliding sleeve. This causes considerable assembly problems.

Gemäß der vorliegenden Ausführungsvariante ist in der Schiebehülse 9 anstelle eines Langloches eine in Richtung der Drehachse 11 der Maschinenwelle 2 geöffnete Ausnehmung 9a vorgesehen, die im montierten Zustand den Mitnehmer 7 teilweise umgreift. An der Schiebehülse 9 ist im Bereich der Ausnehmung 9a eine erste Anschlagfläche 21 vorgesehen, die wie in den Fig. 2 und 3 dargestellt gegen den Mitnehmer 7 stößt, wenn sich die Schiebehülse 9 in ihrer ersten, unteren Extremposition befindet. Die erste, untere Extremposition der Schiebehülse 9 korrespondiert mit einer Ausrichtung der Schwenkscheibe 5, in der die Schwenkscheibe 5 einen minimalen Winkel mit der Maschinenwelle 2 einschließt und die Kolben 4 bei einer Rotation der Schwenkscheibe 5 einen maximalen Hub ausführen.According to the present embodiment variant, a recess 9a which is open in the direction of the axis of rotation 11 of the machine shaft 2 is provided in the sliding sleeve 9 instead of an oblong hole, which recess partially surrounds the driver 7 in the mounted state. On the sliding sleeve 9, a first stop surface 21 is provided in the region of the recess 9 a, which, as in the FIGS. 2 and 3 shown against the driver 7 abuts when the sliding sleeve 9 is in its first, lower extreme position. The first, lower extreme position of the sliding sleeve 9 corresponds to an orientation of the swash plate 5, in which the swash plate 5 encloses a minimum angle with the machine shaft 2 and the pistons 4 perform a maximum stroke during rotation of the swash plate 5.

Im Bereich einer Stirnseite 9b der Schiebehülse 9 ist ferner eine zweite Anschlagfläche 22 vorgesehen, dem als Gegenstück seitens der Maschinenwelle 2 ein Halteelement in Form eines Sicherungsringes 20 zugeordnet ist. In bevorzugter Weise ist zwischen Sicherungsring 20 und Anschlagfläche 22 ein Federelement in Form einer schwachen Tellerfeder 23 vorgesehen. Wenn sich die Sicherungshülse 9 in ihrer zweiten, oberen Extremposition befindet, stößt sie gegen die Tellerfeder 23 und drückt diese näherungsweise vollständig zusammen. In einer Ausgestaltung ohne Federelement stößt die Schiebehülse direkt gegen den Sicherungsring 20. Wenn die Schiebehülse 9 die zweite Extremposition erreicht, schließt die Schwenkscheibe mit der Maschinenwelle wenigstens näherungsweise einen rechten Winkel ein und befindet sich somit in einer "Neutralposition", in der die Kolben 4 der Hubkolbenmaschine 1 durch die Schwenkscheibe nicht bewegt werden. Durch Zwischenschaltung der Tellerfeder 23 kann die Schwenkscheibe 5 im druckausgeglichenen Zustand des Kompressors in einer gewissen Entfernung von ihrer "Neutralposition" gehalten werden, so daß die Förderwirkung sofort nach Ingangsetzung beginnt. In Fig. 3 ist die erfindungsgemäße Schiebehülse 9 perspektivisch dargestellt. Die Anschlagflächen 21, 22 sind im montierten Zustand in Richtung der Drehachse 11 auf derselben Seite des Mitnehmers 7 angeordnet.In the region of an end face 9b of the sliding sleeve 9, a second stop surface 22 is further provided, which is assigned as a counterpart on the part of the machine shaft 2, a holding element in the form of a securing ring 20. Preferably, between spring ring 20 and stop surface 22, a spring element in the form of a weak plate spring 23 is provided. When the locking sleeve 9 is in its second, upper extreme position, it abuts against the plate spring 23 and presses it approximately completely together. In one embodiment without spring element, the sliding sleeve abuts directly against the locking ring 20. When the sliding sleeve 9 reaches the second extreme position, the swash plate with the machine shaft includes at least approximately a right angle and is thus in a "neutral position", in which the piston. 4 the reciprocating engine 1 are not moved by the swash plate. By interposing the plate spring 23, the swash plate 5 can be kept in the pressure-balanced state of the compressor at a certain distance from its "neutral position", so that the conveying effect begins immediately after initiation. In Fig. 3 the sliding sleeve 9 according to the invention is shown in perspective. The stop surfaces 21, 22 are arranged in the mounted state in the direction of the axis of rotation 11 on the same side of the driver 7.

Der Kolbenhub und damit das Fördervolumen der Hubkolbenmaschine 1 wird durch Veränderung des Schwenkwinkels der Schwenkscheibe 5 bewirkt. Der Schwenkwinkel ändert sich vorzugsweise mit dem Druck im Triebraum 14, der direkt auf die Unterseite der Kolben 4 wirkt. Das Fördervolumen kann also durch Änderung des Druckes im Triebraum geregelt werden. Dies geschieht beispielsweise dadurch, daß dem Triebraum 14 durch eine kleine Drossel (nicht dargestellt) ständig eine kleine Menge des von der Hubkolbenmaschine 1 geförderten Arbeitsmediums von der Hochdruckseite zugeführt und daß die Menge des aus dem Triebraum (ggf. zur Saugseite hin) abströmenden Arbeitsmediums durch ein Regelventil bestimmt wird. Innerhalb der Maschinenwelle ist hierzu eine Abflußleitung vorgesehen - gebildet aus den Bohrungen 24, 25, über die das Medium aus dem Triebraum 14 abgeführt werden kann. In Fig. 2 ist schematisch eine weitere Ausführungsform einer Abflußleitung in Form der Bohrungen 24, 26 dargestellt. Im Detail sind die Bohrungen 24, 25, 26 nochmals aus den Fig. 4 und 5 ersichtlich. In einem mittleren Bereich der Innenseite der Schiebehülse 9 ist eine ringförmige Nut 18 vorgesehen, die sich entlang des gesamten Umfangs über einen Großteil der Innenseite der Schiebehülse erstreckt. In der eingebauten Position (Fig. 1, 2, 4 und 5) ist zwischen der Schiebehülse 9 und der Maschinenwelle 2 ein Hohlraum 17 gebildet. Der Hohlraum 17 ist mit dem Triebraum 14 durch die Ausnehmung 9a und ggf. durch weitere Öffnungen verbunden. Axial versetzt zur Ausnehmung 9a führen die Bohrungen 25, 26 durch die Maschinenwelle 2 radial nach innen zur koaxialen Abflussbohrung 24, so daß der Triebraum 14 über die Bohrungen 25, 26 mit der Abflussbohrung 24 verbunden ist. Die Bohrung 25 in der Welle 2 ist derart angeordnet, daß sie senkrecht zur Drehachse 11 verläuft, während die Bohrung 26 zur Drehachse 11 geneigt verläuft.The piston stroke and thus the delivery volume of the reciprocating engine 1 is effected by changing the pivot angle of the swash plate 5. The pivot angle preferably changes with the pressure in the drive chamber 14, which acts directly on the underside of the piston 4. The delivery volume can therefore be regulated by changing the pressure in the drive chamber. This happens, for example, in that the drive chamber 14 through a small throttle (not shown) constantly fed a small amount of funded by the reciprocating engine 1 working medium from the high pressure side and that the amount of the drive from the drive (possibly to the suction side) flowing through the working medium a control valve is determined. Within the machine shaft for this purpose a drain line is provided - formed from the bores 24, 25, over which the medium from the drive chamber 14 can be removed. In Fig. 2 schematically another embodiment of a drain line in the form of holes 24, 26 is shown. In detail, the holes 24, 25, 26 again from the 4 and 5 seen. In a central region of the inside of the sliding sleeve 9, an annular groove 18 is provided which extends over the entire circumference over a large part of the inside of the sliding sleeve. In the installed position ( Fig. 1 . 2 . 4 and 5 ) is formed between the sliding sleeve 9 and the machine shaft 2, a cavity 17. The cavity 17 is connected to the drive chamber 14 through the recess 9a and possibly through further openings. Axially offset from the recess 9a, the bores 25, 26 lead through the machine shaft 2 radially inwardly to the coaxial drain hole 24, so that the drive chamber 14 is connected via the bores 25, 26 with the drain hole 24. The bore 25 in the shaft 2 is arranged so that it is perpendicular to the axis of rotation 11, while the bore 26 is inclined to the axis of rotation 11.

In dem Triebraum 14 befindet sich beim Betrieb der Hubkolbenmaschine 1 im allgemeinen nicht nur das von der Hubkolbenmaschine 1 zu verdichtende Arbeitsmedium, sondern auch weitere, insbesondere flüssige Substanzen wie Schmieröl und/oder Wasser. Daraus kann sich in unerwünschter Weise ein im Triebraum 14 vorliegendes Gemisch aus dem Arbeitsmedium und den weiteren Substanzen ergeben. Mit Hilfe der ringförmigen Nut 18 bzw. des ringförmigen Hohlraumes 17 und der Bohrungen 25 bzw. 26 können insbesondere flüssige und/oder feste Substanzen aus dem Arbeitsmedium der Hubkolbenmaschine 1 abgeschieden werden. In den Fig. 4 und 5 sind die Funktionen näher erläutert. Der Pfeil A mit durchgezogener Linie kennzeichnet den Weg des Gemisches, auf welchem zunehmend unerwünschte flüssige und/oder feste Substanzen abgeschieden werden, die insbesondere unter Schwerkrafteinfluss auf einem durch den gestrichelt gezeichneten Pfeil B bezeichneten Weg in den Triebraum 14 zurückkehren.In the drive chamber 14 is located during operation of the reciprocating engine 1 in general, not only to be compressed by the reciprocating engine 1 working fluid, but also other, especially liquid substances such as lubricating oil and / or water. This may result in an unwanted manner present in the drive chamber 14 mixture of the working fluid and the other substances. With the help of the annular groove 18 and the annular cavity 17 and the bores 25 and 26, in particular liquid and / or solid substances from the working medium of the reciprocating engine 1 can be deposited. In the 4 and 5 the functions are explained in more detail. The arrow A with a solid line indicates the path of the mixture, on which increasingly undesirable liquid and / or solid substances are deposited, which in particular return to the drive chamber 14 under the influence of gravity on a path indicated by the dashed arrow B.

Damit bereits im Hohlraum 17 unerwünschte Substanzen abgeschieden werden, muss sich das Gemisch eine gewisse Zeit lang in diesem Hohlraum 17 aufhalten. Daraus ergibt sich das Merkmal des axialen Versatzes der Bohrungen 25, 26 gegenüber der Einströmstelle in den Hohlraum 17 bei der Ausnehmung 9a. Hin- und Rückströmung sind im Hohlraum 17 durch Fliehkraft in eine innere Hinströmung und eine äußere Rückströmung separiert.So that 17 unwanted substances are already deposited in the cavity, the mixture must remain for a certain time in this cavity 17. This results in the feature of the axial offset of the holes 25, 26 with respect to the inflow into the cavity 17 at the recess 9a. Forward and backward flow are separated in the cavity 17 by centrifugal force into an inner outflow and an outer backflow.

Eine derartige Separierung erfolgt besonders effektiv auch in der Bohrung 26, die gegenüber der Drehachse 11 geneigt angeordnet ist. In einem Ausführungsbeispiel gemäss Fig. 5 kann die Bohrung 24 kürzer, d. h. weniger tief sein als im Ausführungsbeispiel gemäss Fig.4.Such a separation is particularly effective in the bore 26 which is arranged inclined relative to the axis of rotation 11. In an embodiment according to Fig. 5 the bore 24 may be shorter, ie less deep than in the embodiment according to Figure 4 ,

Der vorgeschlagene, als Schiebehülse ausgebildete Schiebekörper 9 läßt sich über die Maschinenwelle 2 und den Mitnehmer 7 stecken, auch wenn diese fest miteinander verbunden sind. Es besteht daher die Möglichkeit, in einem ersten Montageschritt ein Einpressen des Mitnehmers 7 in die Maschinenwelle 2 vorzunehmen oder die Maschinenwelle 2 und den Mitnehmer 7 einstückig auszuführen. Da sich die Biegebeanspruchung des Mitnehmers 7 bis in die zugehörige Ausnehmung 9a in der Maschinenwelle 2 fortsetzt, so daß bei einer Presspassung zwischen dem Mitnehmer 7 und der Maschinenwelle 2 Mikroverschiebungen in der Pressfuge auftreten, kann die Biegesteifigkeit des Mitnehmers 7 erhöht und damit eine Biegung verringert werden, wenn der Mitnehmer 7 und die Maschinenwelle 2 aus einem Stück bestehen. Es ergibt sich eine höhere Belastbarkeit von Mitnehmer 7 und Maschinenwelle 2, woraus ein verbessertes Betriebsverhalten der Hubkolbenmaschine 1 resultiert.The proposed, designed as a sliding sleeve sliding body 9 can be stuck on the machine shaft 2 and the driver 7, even if they are firmly connected. It is therefore possible to carry out a pressing in of the driver 7 in the machine shaft 2 or to perform the machine shaft 2 and the driver 7 in one piece in a first assembly step. Since the bending stress of the driver 7 continues into the associated recess 9a in the machine shaft 2, so that micro-displacements occur in the press joint during an interference fit between the driver 7 and the machine shaft 2, the flexural rigidity of the carrier 7 can be increased, thereby reducing bending are when the driver 7 and the machine shaft 2 consist of one piece. It results in a higher load capacity of driver 7 and machine shaft 2, resulting in an improved performance of the reciprocating engine 1 results.

Ferner ermöglicht die erfindungsgemäße Hubkolbenmaschine 1 mit der die Nut 18 umfassenden Schiebehülse 9 in Verbindung mit der Abflußleitung bzw. den Bohrungen 24, 25, 26 in der Maschinenwelle 2 eine Abscheidung von unerwünschten Substanzen aus dem Arbeitsmedium der Hubkolbenmaschine 1 unter Ausnutzung von Flieh- und Schwerkrafteinflüssen. Somit kann reines Arbeitsmedium aus dem Triebraum 14 abgeführt werden, wodurch sich eine verbesserte Steuerbarkeit und somit ein verbessertes Betriebsverhalten der Hubkolbenmaschine 1 ergibt.Further, the reciprocating engine 1 according to the invention with the groove 18 comprising the sliding sleeve 9 in conjunction with the drain line or bores 24, 25, 26 in the machine shaft 2 allows separation of undesirable substances from the working fluid of the reciprocating engine 1 by utilizing centrifugal and gravitational forces , Thus, pure working fluid can be removed from the drive chamber 14, resulting in improved controllability and thus improved performance of the reciprocating engine 1.

Claims (3)

  1. Reciprocating piston motor (1), in particular refrigerant compressor for a motor vehicle air conditioning system, comprising
    - a machine shaft (2),
    - several pistons (4) arranged around the machine shaft (2) in a circle,
    - an in particular annular adjustable-angle swashplate (5) driven by the machine shaft (2) and acting on the pistons (4) via a joint arrangement (6), wherein
    - the adjustable-angle swashplate (5) is pin-connected to the machine shaft (2) via a driver (7) for transmitting the drive forces, and
    - mounted on a sliding body (9) for pivoting about a hinge axis (8) oriented at right angles to the machine shaft (2), wherein
    - the sliding body (9) encloses on its inside facing the machine shaft (2) a cavity (17) for separating solid and/or liquid substances from gaseous substances of an operating medium,
    - a bore (24, 25, 26) extending through the machine shaft (2) terminating in said cavity (17),
    - wherein the cavity (17) has an opening (16) towards a drive chamber (14) of the reciprocating piston motor, and wherein
    - the opening (16) is arranged at a distance in the direction of the axis of rotation (11) of the machine shaft (2) towards the termination of the bore (24, 25, 26) extending through the machine shaft (2),
    characterised in that
    the cavity (17) enclosed by the sliding body (9) is represented by an annular groove (18) which extends along the entire circumference of the sliding body (9) across a major part of its inside.
  2. Reciprocating piston motor (1) according to claim 1,
    characterised in that
    the opening (16) is situated in the region of a recess (9a) of the sliding body (9).
  3. Reciprocating piston motor (1) according to claim 1,
    characterised in that
    the bore (26) extends at an angle to and/or perpendicular to (25) and/or coaxial with (24) the axis of rotation (11).
EP02704758A 2001-05-16 2002-03-15 Reciprocating piston motor comprising a sliding sleeve Expired - Lifetime EP1438504B8 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10124033 2001-05-16
DE10124033A DE10124033B4 (en) 2001-05-16 2001-05-16 Reciprocating engine with a sliding sleeve
PCT/EP2002/002891 WO2002093010A2 (en) 2001-05-16 2002-03-15 Reciprocating piston motor comprising a sliding sleeve

Publications (3)

Publication Number Publication Date
EP1438504A2 EP1438504A2 (en) 2004-07-21
EP1438504B1 true EP1438504B1 (en) 2011-10-26
EP1438504B8 EP1438504B8 (en) 2012-02-29

Family

ID=7685135

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02704758A Expired - Lifetime EP1438504B8 (en) 2001-05-16 2002-03-15 Reciprocating piston motor comprising a sliding sleeve

Country Status (9)

Country Link
US (1) US7179063B2 (en)
EP (1) EP1438504B8 (en)
JP (1) JP4060193B2 (en)
KR (1) KR100875343B1 (en)
CN (1) CN100359166C (en)
AT (1) ATE530767T1 (en)
AU (1) AU2002238586A1 (en)
DE (1) DE10124033B4 (en)
WO (1) WO2002093010A2 (en)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7470116B2 (en) * 2002-12-18 2008-12-30 Bosch Rexroth Ag Axial piston machine
EP1844233B1 (en) * 2004-11-05 2008-02-27 ixetic MAC GmbH Reciprocating piston machine
EP2165075B1 (en) 2007-07-13 2011-04-20 Ixetic Bad Homburg GmbH Reciprocating piston engine
DE112008002022A5 (en) * 2007-08-25 2010-07-22 Ixetic Mac Gmbh reciprocating engine
JP5140402B2 (en) * 2007-12-06 2013-02-06 カルソニックカンセイ株式会社 Swash plate compressor
ATE544951T1 (en) * 2008-02-21 2012-02-15 Ixetic Bad Homburg Gmbh RECIPIENT ENGINE
JP4974927B2 (en) * 2008-02-26 2012-07-11 カルソニックカンセイ株式会社 Swash plate compressor
US8348632B2 (en) * 2009-11-23 2013-01-08 Denso International America, Inc. Variable displacement compressor shaft oil separator
DE102010052508A1 (en) 2010-11-26 2012-05-31 Daimler Ag Waste heat recovery device
US9163620B2 (en) 2011-02-04 2015-10-20 Halla Visteon Climate Control Corporation Oil management system for a compressor
US20140308139A1 (en) * 2013-04-10 2014-10-16 Medhat Kamel Bahr Khalil Double swash plate pump with adjustable valve ring concept
KR101421961B1 (en) * 2013-08-27 2014-07-22 현대자동차주식회사 Structure of variable swash plate type compressor
WO2015090880A1 (en) * 2013-12-18 2015-06-25 Magna Powertrain Bad Homburg GmbH Refrigerant compressor
DE102016105756B3 (en) * 2016-03-30 2017-08-31 Hanon Systems Device for compressing refrigerant with variable displacement with a stop in a sliding sleeve for determining the inclination angle of a drive element

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JPH07224669A (en) * 1994-02-07 1995-08-22 Sanshin Ind Co Ltd V-type multicylinder two-cycle engine
US5647266A (en) * 1994-10-03 1997-07-15 Dynex/Rivett, Inc. Hold-down mechanism for hydraulic pump
TW353705B (en) * 1995-06-05 1999-03-01 Toyoda Automatic Loom Works Reciprocating piston compressor
JPH10238608A (en) * 1997-02-28 1998-09-08 Honda Motor Co Ltd Axial piston machine
JPH1162824A (en) * 1997-08-08 1999-03-05 Sanden Corp Variable capacity compressor
DE19749727C2 (en) * 1997-11-11 2001-03-08 Obrist Engineering Gmbh Lusten Reciprocating piston machine with swivel plate gear
JP3851971B2 (en) * 1998-02-24 2006-11-29 株式会社デンソー CO2 compressor
JP3509560B2 (en) * 1998-06-15 2004-03-22 株式会社豊田自動織機 Oil separation structure of compressor

Also Published As

Publication number Publication date
JP2004534919A (en) 2004-11-18
DE10124033B4 (en) 2009-08-20
KR100875343B1 (en) 2008-12-22
EP1438504A2 (en) 2004-07-21
DE10124033A1 (en) 2002-11-21
KR20040012839A (en) 2004-02-11
WO2002093010A2 (en) 2002-11-21
AU2002238586A1 (en) 2002-11-25
WO2002093010A3 (en) 2004-05-27
JP4060193B2 (en) 2008-03-12
ATE530767T1 (en) 2011-11-15
US7179063B2 (en) 2007-02-20
EP1438504B8 (en) 2012-02-29
CN100359166C (en) 2008-01-02
CN1617980A (en) 2005-05-18
US20040120830A1 (en) 2004-06-24

Similar Documents

Publication Publication Date Title
DE4138313C2 (en) Radial piston pump
EP1438504B1 (en) Reciprocating piston motor comprising a sliding sleeve
DE60113597T2 (en) Lubricator for swash plate compressors
EP2333336B1 (en) Reciprocating engine for use as a vacuum pump for medicinal purposes
DE69407226T2 (en) Bearing arrangement for use in a compressor
EP0057288A1 (en) Two cylinder pump for viscous materials, particularly a concrete pump with a connecting element pivoting in front of a two orifice plate beside the cylinders
WO2008077596A1 (en) Hydrostatic axial piston engine
DE3142230A1 (en) MULTI-CYLINDER COMPRESSOR
DE19650108A1 (en) Swashplate compressor for cooling system
DE19530210C2 (en) Swash plate compressor
DE19527675C2 (en) Refrigerant compressor with single-acting pistons and damping devices for fluctuations in the starting pressure
DE102004028747A1 (en) reciprocating compressor
DE69820959T2 (en) Housing seal for a swash plate compressor
DE102007004130A1 (en) Adjustable compressor for use in compressing refrigerant in positive displacement pump and in air conditioning system has oil separation device, which is provided for separating lubricant from compressed and circulated cooling agent
DE69904529T2 (en) Piston for a swash plate compressor
DE3725411C2 (en)
EP0752530A1 (en) Reciprocating piston machine with swash plate mechanism
WO2015086336A1 (en) Swashplate-type machine, swashplate and method for relieving the hydrostatic load on a control part connection of a swashplate-type machine
DE19855899B4 (en) axial piston
WO2001036823A1 (en) Axial piston compressor
EP1387957B1 (en) Reciprocating engine with an articulation arrangement
WO2008034808A1 (en) Radial piston pump
DE10017780B4 (en) piston engine
DE10351372A1 (en) Compressor, especially for air conditioning unit of motor vehicle, has housing with holder constructed as separate component after fashion of hose clamp or clamping collar
DE19702399C2 (en) Swash plate compressor

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

17P Request for examination filed

Effective date: 20031025

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

17Q First examination report despatched

Effective date: 20060905

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: OBRIST ENGINEERING GMBH

Owner name: DAIMLERCHRYSLER AG

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: DAIMLER AG

Owner name: OBRIST ENGINEERING GMBH

GRAC Information related to communication of intention to grant a patent modified

Free format text: ORIGINAL CODE: EPIDOSCIGR1

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

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: DAIMLER AG

Owner name: OBRIST ENGINEERING GMBH

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

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

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: DAIMLER AG

Owner name: OBRIST ENGINEERING GMBH

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 50215260

Country of ref document: DE

Effective date: 20111215

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20111026

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: 20120127

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: 20111026

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: 20120227

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: 20111026

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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

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: 20111026

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

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: 20111026

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: 20111026

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

Ref country code: DE

Payment date: 20120531

Year of fee payment: 11

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

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

Effective date: 20111026

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

BERE Be: lapsed

Owner name: DAIMLER A.G.

Effective date: 20120331

Owner name: OBRIST ENGINEERING GMBH

Effective date: 20120331

26N No opposition filed

Effective date: 20120727

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: 20120331

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20120315

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 50215260

Country of ref document: DE

Effective date: 20120727

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20121130

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

Ref country code: LI

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

Effective date: 20120331

Ref country code: FR

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

Effective date: 20120402

Ref country code: BE

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

Effective date: 20120331

Ref country code: GB

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

Effective date: 20120315

Ref country code: CH

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

Effective date: 20120331

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: 20120206

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 530767

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120315

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

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: 20111026

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: 20120315

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50215260

Country of ref document: DE

Effective date: 20131001

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

Ref country code: DE

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

Effective date: 20131001

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

Ref country code: TR

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: 20111026

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: 20120315