EP1387957B1 - Reciprocating engine with an articulation arrangement - Google Patents

Reciprocating engine with an articulation arrangement Download PDF

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Publication number
EP1387957B1
EP1387957B1 EP02742856A EP02742856A EP1387957B1 EP 1387957 B1 EP1387957 B1 EP 1387957B1 EP 02742856 A EP02742856 A EP 02742856A EP 02742856 A EP02742856 A EP 02742856A EP 1387957 B1 EP1387957 B1 EP 1387957B1
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EP
European Patent Office
Prior art keywords
piston
machine shaft
sliding
swash plate
sub
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
EP02742856A
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German (de)
French (fr)
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EP1387957A1 (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
DaimlerChrysler AG
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Publication of EP1387957A1 publication Critical patent/EP1387957A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—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
    • F04B27/0873—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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • F04B27/0886—Piston shoes

Definitions

  • the invention relates to a reciprocating engine according to the preamble of claim 1.
  • a power transmission center is provided, which is arranged in extension of the respectively associated piston axis and forms the geometric center of the spherical sliding surfaces of the sliding blocks.
  • Machine shaft, driver, swivel disk and the joint assemblies and are arranged in a so-called drive chamber, in the gaseous working fluid of the reciprocating engine is present at a certain pressure.
  • the delivery volume and thus the stroke of the piston and the inclination of the swash plate relative to the machine shaft are dependent on the pressure ratio between the suction side and pressure side of the piston or depending on the pressures in the cylinders on the one hand and in the drive chamber on the other.
  • JP 05-306678 A is a reciprocating engine with a machine shaft which has a plurality of equally spaced around the machine shaft around the piston, wherein the pistons are articulated via a respective hinge assembly of a swash plate.
  • the joint arrangements each have sections of spherical receptacles in which spaced-apart sliding elements are provided with ball-shaped sliding surfaces.
  • the object of the invention is in contrast to provide a reciprocating engine with improved performance and higher performance.
  • a reciprocating piston engine is characterized in that a first sliding element has a first spherical section-shaped sliding surface with a first geometric center and a second sliding member having a second spherical portion sliding surface with a second geometric center, wherein first and second center are spaced from each other.
  • This arrangement is preferably just relaxed and possibly executed with play when the swash plate with the machine shaft includes a right angle and thus is in a "neutral position" in which no piston stroke is generated.
  • the radius of the recording is approximately the radius of the sliding surfaces.
  • the reciprocating engine according to the invention is characterized in that the first geometric center is arranged offset from the second geometric center in the direction of rotation on the cylinder jacket. This results in a reduction of a present in the neutral position game at a pivoting of the swash plate in a first direction and an increase of the game at a pivoting of the swash plate in the opposite direction.
  • the joint arrangement is associated with an approximately lying on the cylinder jacket of the piston axes power transmission center, which is positioned with respect to the direction of rotation of the swash plate in front of the associated piston axis.
  • the power transmission center is a geometric location at which the power transmission between the swash plate and the respective piston takes place in an idealized manner.
  • the force transmission center is the pivot point of the joint assembly and possibly the common center of several sliding or rolling elements.
  • the position of the power transmission center should be moved against the direction of rotation of the swash plate in front of the piston axis, so that the force exerted on the piston due to the inclined arrangement of the swash plate rotation or tilting moment and corresponding support forces are reduced to a piston guide.
  • Fig. 1 is a longitudinal section through a reciprocating engine 1 is shown in the form of a refrigerant compressor for a motor vehicle air conditioning.
  • the reciprocating piston engine 1 has a plurality of pistons 4 arranged in a machine housing 3. All piston axes 12 are at a fixed distance from the axis of rotation 11, i. geometrically arranged on a cylinder jacket (not shown) around the machine shaft 2 and aligned parallel to the axis of rotation 11 of the machine shaft.
  • the pistons 4 are guided in cylindrical bushings 10 (piston guides) in which cylindrical compression chambers 13 are formed (compare FIGS. 2 to 4).
  • the pistons 4 separate the compression chambers 13 from a so-called drive chamber 14 ("crankcase").
  • the rotational movement of the machine shaft is converted into a translational movement of the piston 4.
  • a sliding body is guided in the form of a sliding sleeve 9.
  • a sliding sleeve 9 On the sliding sleeve 9, in turn, a preferably annular swash plate 5 is mounted, wherein the swash plate 5 together with the sliding sleeve 9 in the direction of the axis of rotation 11 is displaceable.
  • two short pins are mounted on both sides, which define a transverse to the axis of rotation 11 of the machine shaft 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 and engages with a spherical articulation section in a radially open receptacle 15 on the part of the swash plate (see Fig. 2). Since the driver 7 is fixed to the machine shaft, a pivoting of the swash plate about the hinge axis 8 is coupled to the displacement of the sliding sleeve 9. About the driver 7, the rotation of the machine shaft 2 is transmitted to the swash plate during operation of the reciprocating piston (rotational movement in the direction of the arrow w).
  • Perpendicular to the hinge axis 8 is defined by the axis of rotation 11 main center plane which separates a suction side of a pressure side of the reciprocating engine.
  • the main center plane rotates with the machine shaft.
  • the swash plate 5 is encompassed at its periphery in the region of each piston 4 by a hinge assembly 6 which slides over the swash plate when it carries out its rotational movement w. With an inclination of the swash plate 5 relative to the machine shaft 2, causes the swash plate in the course of its rotation, the piston located on the pressure side to a compression movement and lying on the suction side of the piston to a suction movement.
  • Fig. 2 is a simplified schematic diagram for power transmission between the machine shaft 2 and piston 4 is shown.
  • FIGS. 3 and 4 show a view in the radial direction from the machine shaft 2 to the outside again, the swivel disk 5 moving in the direction of the arrow w in FIG. 3 showing a suction stroke of the piston 4 (arrow s) and in Fig. 4 causes a compression stroke of the piston 4 (arrow v).
  • the joint assembly 6 has a receptacle with two identical, approximately spherical guide and sliding surfaces 6a, in which two spherical cap-shaped sliding elements 16, 17 are mounted.
  • the recording and the sliding elements 16, 17 is associated with a common geometric center M, which also forms a power transmission center K of the joint assembly 6.
  • the sliding surfaces 6a of the receptacle and the spherical surfaces of the sliding elements 16, 17 have the same radius and the same curvature.
  • the sliding elements 16, 17 sit with a small clearance on the swash plate 5.
  • the power transmission center K is positioned counter to the direction of rotation w in front of the piston axis 12 of the associated piston 4 on the cylinder jacket containing all piston axes.
  • the distance of the power transmission center M to the piston axis 12 is preferably 10% to 20% of the piston stroke.
  • the force application point K s for the suction stroke is thus further away from the piston 4 and the piston guide 10 than the power transmission center K of the joint assembly, while the force application point K v for the compression stroke closer to the piston 4th is located as the power transmission center K of the joint assembly.
  • the same applies to the supporting forces A s and A v which are approximately equal in a preferred embodiment.
  • FIG. 6 A second embodiment of the hinge arrangement 6 according to the invention is shown in FIG.
  • the joint arrangement 6 has a receptacle with two spherical sliding / guide surfaces 6a, 6b, in which a first sliding element 18 with a spherical segment-shaped sliding surface 18a and a second sliding element 19 with a spherical segment-shaped sliding surface 19a are mounted.
  • the first sliding element 18 is arranged on the side facing the associated piston, the second sliding element 19 on the side facing away from the piston side of the swash plate 5, so that the swash plate 5 is encompassed by the sliding elements 18, 19.
  • the geometric center M 1 of the first sliding element 18 is arranged between the median plane 5 a of the swash plate 5 and the piston (not shown), while the geometric center M 2 of the second sliding element 19 lies on the median plane 5 a.
  • the power transmission center of the joint assembly 6 is in the state of bias between the two geometric centers M 1 , M 2 , so that the force is introduced into the piston (relative to arrangements with a power transmission center on the center plane 5 a) generally closer to the piston guide and a smaller overturning moment is exerted on the piston.
  • the geometric Midpoints M 1 , M 2 are arranged approximately mirror-symmetrically with respect to the center plane 5a and the power transmission center on the center plane 5a.
  • FIG. 6 A third embodiment of the joint arrangement 6 according to the invention is shown in FIG.
  • the hinge assembly 6 comprises two sliding members 20, 21 corresponding to those in the previously described embodiments.
  • the sliding elements 20, 21 each have ball-section-shaped sliding surfaces 20a, 21a, which slide in a receptacle 6c, 6d.
  • the sliding surfaces 20a, 21a have geometric centers M 3 , M 4 , which lie approximately on the center plane 5a of the swash plate 5 and the other on the cylinder jacket, on which all piston axes 12 (see Fig. 1 to 3) of the reciprocating engine are positioned.
  • the geometric center M 3 of the closer lying on the piston guide slide 20 is seen in the direction of rotation of the swash plate (arrow w) behind the center M 4 of the opposite sliding element 21.
  • a joint arrangement of a piston is provided, the sliding blocks having spherical portion sliding surfaces positioned their centers according to a combination of the present in the aforementioned embodiments features in front of the associated piston axis, spaced apart in a direction parallel to the piston axis and / or in the rotational direction the swash plate are offset from each other.
  • reciprocating engines can be designed which can withstand substantially greater dynamic loads in the region of the power transmission between the swivel disk and the piston with essentially the same dimensions as compared with reciprocating engines of the prior art. At the same time there are reduced or evened balance of power in the area of the piston guides and on the joint arrangements. This results in higher performance with a smoother running and lower operating noise.

Abstract

In a reciprocating-piston machine, in particular a refrigerant compressor for a motor vehicle air-conditioning system, including a machine shaft, a plurality of pistons are arranged, at the same distance from the machine shaft, on a cylinder envelope defined by the axes of the pistons and extending around the machine shaft, and an annular pivoting disc which is driven by the machine shaft and which engages the pistons via a joint arrangement, the joint arrangement has an at least partially spherical receptacle, in which at least one sliding element structure is arranged moveably relative to the associated piston and relative to the pivoting disc, including a first sliding element having a first sliding face in the form of a spherical segment with a first geometric center (M<SUB>1</SUB>, M<SUB>3</SUB>), and a second sliding element having a second sliding face in the form of a spherical segment with a second geometric center (M<SUB>2</SUB>, M<SUB>4</SUB>) arranged at a distance from the first geometric center.

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 Offenlegungsschrift DE 197 49 727 A1 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 über eine Gelenkanordnung auf die parallel zur Maschinenwelle translatorisch verschiebbaren Kolben übertragen. Dabei ist die Schwenkscheibe einerseits an einer linear verschieblich an der Maschinenwelle befestigten Schiebehülse schwenkbar gelagert; sie gleitet andererseits an der Gelenkanordnung entlang, welche die Schwenkscheibe mit zwei kugelkappenförmigen Gleitsteinen umgreift. In der Gelenkanordnung ist ein Kraftübertragungsmittelpunkt vorgesehen, der in Verlängerung der jeweils zugehörigen Kolbenachse angeordnet ist und den geometrischen Mittelpunkt der kugeligen Gleitflächen der Gleitsteine bildet. Maschinenwelle, Mitnehmer, Schwenkscheibe und die Gelenkanordnungen und sind in einem sogenannten Triebraum angeordnet, in dem gasförmiges Arbeitsmedium der Hubkolbenmaschine mit einem bestimmten Druck vorliegt. Das Fördervolumen und damit der Hub der Kolben und die Neigung der Schwenkscheibe gegenüber der Maschinenwelle 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 publication DE 197 49 727 A1 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 pivot plate and from this in turn via a hinge assembly on the parallel to the machine shaft translationally displaceable piston. In this case, the swash plate is pivotally mounted on the one hand on a linearly displaceable attached to the machine shaft sliding sleeve; on the other hand, it slides along the joint arrangement, which surrounds the swivel disk with two spherical cap-shaped sliding blocks. In the joint arrangement, a power transmission center is provided, which is arranged in extension of the respectively associated piston axis and forms the geometric center of the spherical sliding surfaces of the sliding blocks. Machine shaft, driver, swivel disk and the joint assemblies and are arranged in a so-called drive chamber, in the gaseous working fluid of the reciprocating engine is present at a certain pressure. The delivery volume and thus the stroke of the piston and the inclination of the swash plate relative to the machine shaft are dependent on the pressure ratio between the suction side and pressure side of the piston or depending on the pressures in the cylinders on the one hand and in the drive chamber on the other.

Aus der Patentschrift US 4,762,468 ist eine Hubkolbenmaschine in Form eines Taumelscheibenkompressors mit einer rotierenden Antriebswelle bekannt, auf der mit fixer Position eine Taumelscheibe befestigt ist. Über die Taumelscheibe werden mehrere Kolben angelenkt, deren Kolbenachsen mit jeweils gleichem Abstand zur Maschinenwelle auf einem Zylindermantel um die Maschinenwelle herum angeordnet sind. Zur Kopplung von Taumelscheibe und Kolben sind jedem Kolben zwei Gleitelemente zugeordnet, die in einer kugelabschnittförmigen Aufnahme seitens des zugehörigen Kolbens gelagert sind und auf der Taumelscheibe gleiten. Die Gleitelemente sind zylindrisch mit einem halbkugeligen Endabschnitt ausgeführt. Aufgrund des konstanten Winkels zwischen Taumelscheibe und Antriebswelle ändern sich im Betrieb des Kompressors die Positionen der Gleitelemente nicht, so dass ein Spiel zwischen Gleitelementen und Taumelscheibe konstant einstellbar ist.From the patent US 4,762,468 is a reciprocating engine in the form of a swash plate compressor with a rotating drive shaft known on the fixed position with a swash plate is fixed. About the swash plate a plurality of pistons are articulated, the piston axes are arranged in each case the same distance from the machine shaft on a cylinder jacket around the machine shaft around. For coupling of the swash plate and the piston, two sliding elements are associated with each piston, which are mounted in a spherical segment-like receptacle on the part of the associated piston and slide on the swash plate. The sliding elements are cylindrical with a hemispherical end portion. Due to the constant angle between the swash plate and the drive shaft, the positions of the sliding elements do not change during operation of the compressor, so that a clearance between the sliding elements and the swash plate is constantly adjustable.

Aus der JP 05-306678 A ist eine Hubkolbenmaschine mit einer Maschinenwelle bekannt, die mehrere mit gleichem Abstand um die Maschinenwelle herum angeordnete Kolben aufweist, wobei die Kolben über jeweils eine Gelenkanordnung von einer Schwenkscheibe anlenkbar sind. Die Gelenkanordnungen weisen jeweils abschnittsweise kugelförmige Aufnahmen auf, in denen voneinander beabstandete Gleitelemente mit kugelabschnittsförmigen Gleitflächen vorgesehen sind.From the JP 05-306678 A is a reciprocating engine with a machine shaft is known which has a plurality of equally spaced around the machine shaft around the piston, wherein the pistons are articulated via a respective hinge assembly of a swash plate. The joint arrangements each have sections of spherical receptacles in which spaced-apart sliding elements are provided with ball-shaped sliding surfaces.

Aufgabe der Erfindung ist es demgegenüber, eine Hubkolbenmaschine mit einem verbesserten Betriebsverhalten und höheren Leistungen bereitzustellen.The object of the invention is in contrast to provide a reciprocating engine with improved performance and higher 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.

Eine erfindungsgemäße Hubkolbenmaschine zeichnet sich dadurch aus, daß ein erstes Gleitelement eine erste kugelabschnittsförmige Gleitfläche mit einem ersten geometrischen Mittelpunkt und ein zweites Gleitelement eine zweite kugelabschnittsförmige Gleitfläche mit einem zweiten geometrischen Mittelpunkt aufweist, wobei erster und zweiter Mittelpunkt voneinander beabstandet angeordnet sind. Diese Anordnung ist vorzugsweise genau dann entspannt und ggf. mit Spiel ausgeführt, wenn die Schwenkscheibe mit der Maschinenwelle einen rechten Winkel einschließt und sich somit in einer "Neutralposition" befindet, in der kein Kolbenhub erzeugt wird. Dabei beträgt der Radius der Aufnahme in etwa dem Radius der Gleitflächen. Bei einer Verstellung der Schwenkscheibe in eine Arbeitsposition, in der sie mit der Maschinenwelle einen Winkel von weniger als 90° einnimmt, werden die Gleitelemente durch die Aufnahme gegen die Schwenkscheibe gedrückt. Dadurch ergibt sich eine besonders einfache Möglichkeit zur Vorspannung der Gelenkanordnung bei zunehmender Abweichung der Schwenkscheibe von ihrer Neutralposition. Dabei ist der erste geometrische Mittelpunkt auf der der Kolbenführung zugewandten Seite der Mittelebene der Schwenkscheibe und der zweite geometrische Mittelpunkt näherungsweise auf der Mittelebene der Schwenkscheibe oder ebenfalls auf der der Kolbenführung zugewandten Seite der Mittelebene der Schwenkscheibe angeordnet. Insgesamt ergibt sich eine Verlagerung des Kraftübertragungsmittelpunktes in Richtung des Kolbens bzw. in Richtung der Kolbenführung. Dadurch ergeben sich besonders geringe, auf den Kolben eingeleitete Momente und besonders geringe Abstützkräfte an der Kolbenführung.A reciprocating piston engine according to the invention is characterized in that a first sliding element has a first spherical section-shaped sliding surface with a first geometric center and a second sliding member having a second spherical portion sliding surface with a second geometric center, wherein first and second center are spaced from each other. This arrangement is preferably just relaxed and possibly executed with play when the swash plate with the machine shaft includes a right angle and thus is in a "neutral position" in which no piston stroke is generated. The radius of the recording is approximately the radius of the sliding surfaces. In an adjustment of the swash plate in a working position in which it assumes an angle of less than 90 ° with the machine shaft, the sliding elements are pressed by the receptacle against the swash plate. This results in a particularly simple way of biasing the hinge assembly with increasing deviation of the swash plate from its neutral position. In this case, the first geometric center point on the side facing the piston guide side of the center plane of the swash plate and the second geometric center approximately on the center plane of the swash plate or also on the piston guide facing side of the median plane of the swash plate. Overall, there is a shift of the power transmission center in the direction of the piston or in the direction of the piston guide. This results in particularly low, initiated on the piston moments and very low support forces on the piston guide.

In Ausgestaltung der Erfindung zeichnet sich die erfindungsgemäße Hubkolbenmaschine dadurch aus, dass der erste geometrische Mittelpunkt gegenüber dem zweiten geometrischen Mittelpunkt in Drehrichtung auf dem Zylindermantel versetzt angeordnet ist. Dadurch ergibt sich eine Reduzierung eines in der Neutralposition vorhandenen Spiels bei einer Verschwenkung der Schwenkscheibe in eine erste Richtung und einer Vergrößerung des Spiels bei einer Verschwenkung der Schwenkscheibe in die entgegengesetzte Richtung. In an embodiment of the invention, the reciprocating engine according to the invention is characterized in that the first geometric center is arranged offset from the second geometric center in the direction of rotation on the cylinder jacket. This results in a reduction of a present in the neutral position game at a pivoting of the swash plate in a first direction and an increase of the game at a pivoting of the swash plate in the opposite direction.

In weiterer Ausgestaltung der Erfindung ist der Gelenkanordnung ein näherungsweise auf dem Zylindermantel der Kolbenachsen liegender Kraftübertragungsmittelpunkt zugeordnet, welcher bezüglich der Drehrichtung der Schwenkscheibe vor der zugehörigen Kolbenachse positioniert ist. Der Kraftübertragungsmittelpunkt ist ein geometrischer Ort, an dem in idealisierter Weise die Kraftübertragung zwischen Schwenkscheibe und dem jeweiligen Kolben erfolgt. Ferner stellt der Kraftübertragungsmittelpunkt den Drehpunkt der Gelenkanordnung und ggf. den gemeinsamen Mittelpunkt mehrerer Gleit- bzw. Rollelemente dar. Durch eine Verschiebung des Kraftübertragungsmittelpunkt auf dem durch die Kolbenachsen definierten Zylindermantel kann die Krafteinleitung in den entsprechenden Kolben beeinflußt werden. Ausgehend von bekannten Lösungen, bei denen der Kraftübertragungsmittelpunkt in Verlängerung der Kolbenachse angeordnet ist, soll die Lage des Kraftübertragungsmittelpunktes entgegen der Drehrichtung der Schwenkscheibe vor die Kolbenachse verschoben sein, so daß das wegen der geneigten Anordnung der Schwenkscheibe auf den Kolben ausgeübte Dreh- bzw. Kippmoment und entsprechende Abstützkräfte an einer Kolbenführung reduziert sind.In a further embodiment of the invention, the joint arrangement is associated with an approximately lying on the cylinder jacket of the piston axes power transmission center, which is positioned with respect to the direction of rotation of the swash plate in front of the associated piston axis. The power transmission center is a geometric location at which the power transmission between the swash plate and the respective piston takes place in an idealized manner. Further, the force transmission center is the pivot point of the joint assembly and possibly the common center of several sliding or rolling elements. By a displacement of the power transmission center on the cylinder jacket defined by the piston axes, the force can be influenced in the corresponding piston. Based on known solutions in which the power transmission center is arranged in extension of the piston axis, the position of the power transmission center should be moved against the direction of rotation of the swash plate in front of the piston axis, so that the force exerted on the piston due to the inclined arrangement of the swash plate rotation or tilting moment and corresponding support forces are reduced to a piston guide.

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 erfindungsgemäße Hubkolbenmaschine,
Fig. 2
eine Prinzipskizze zur Funktion der Hubkolbenmaschine gemäß Fig. 1,
Fig. 3 und 4
Prinzipskizzen zur Funktion eines ersten Ausführungsbeispiels einer erfindungsgemäßen Gelenkanordnung,
Fig. 5
eine Prinzipskizze zur Funktion eines zweiten Ausführungsbeispiels der Gelenkanordnung sowie
Fig. 6
eine Prinzipskizze zur Funktion eines dritten Ausführungsbeispiels der Gelenkanordnung.
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 piston engine according to the invention,
Fig. 2
a schematic diagram of the function of the reciprocating engine of FIG. 1,
3 and 4
Schematic diagrams for the function of a first embodiment of a joint arrangement according to the invention,
Fig. 5
a schematic diagram of the function of a second embodiment of the hinge assembly and
Fig. 6
a schematic diagram of the function of a third embodiment of the hinge assembly.

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 (nicht dargestellt) um die Maschinenwelle 2 herum angeordnet und parallel zur Drehachse 11 der Maschinenwelle ausgerichtet. Die Kolben 4 sind in zylindrischen Laufbuchsen 10 (Kolbenführungen) geführt, in denen zylindrische Verdichtungsräume 13 gebildet sind (vgl. Fig. 2 bis 4). Die Kolben 4 trennen die Verdichtungsräume 13 von einem sogenannten Triebraum 14 ("Kurbelgehäuse") ab. Über eine nachfolgend näher erläuterte Kraftübertragungsanordnung wird die Rotationsbewegung der Maschinenwelle in eine Translationsbewegung der Kolben 4 übergeführt.In Fig. 1 is a longitudinal section through a reciprocating engine 1 is shown in the form of a refrigerant compressor for a motor vehicle air conditioning. The reciprocating piston engine 1 has a plurality of pistons 4 arranged in a machine housing 3. All piston axes 12 are at a fixed distance from the axis of rotation 11, i. geometrically arranged on a cylinder jacket (not shown) around the machine shaft 2 and aligned parallel to the axis of rotation 11 of the machine shaft. The pistons 4 are guided in cylindrical bushings 10 (piston guides) in which cylindrical compression chambers 13 are formed (compare FIGS. 2 to 4). The pistons 4 separate the compression chambers 13 from a so-called drive chamber 14 ("crankcase"). About a subsequently explained in more detail power transmission arrangement, the rotational movement of the machine shaft is converted into a translational movement of the piston 4.

Auf der Maschinenwelle 2 ist ein Schiebekörper in Form einer Schiebehülse 9 geführt. An der Schiebehülse 9 ist wiederum eine vorzugsweise kreisringförmige Schwenkscheibe 5 gelagert, wobei die Schwenkscheibe 5 gemeinsam mit der Schiebehülse 9 in Richtung der Drehachse 11 verschiebbar ist. An der Schiebehülse 9 sind beidseitig zwei kurze Zapfen angebracht, die eine quer zur Drehachse 11 der Maschinenwelle ausgerichtete Scharnierachse 8 definieren, um die die Schwenkscheibe 5 schwenkbar ist.On the machine shaft 2, a sliding body is guided in the form of a sliding sleeve 9. On the sliding sleeve 9, in turn, a preferably annular swash plate 5 is mounted, wherein the swash plate 5 together with the sliding sleeve 9 in the direction of the axis of rotation 11 is displaceable. 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 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 ab und greift mit einem kugelförmigen Anlenkabschnitt in eine radial geöffnete Aufnahme 15 seitens der Schwenkscheibe ein (vgl. Fig. 2). Da der Mitnehmer 7 an der Maschinenwelle festgelegt ist, ist ein Verschwenken der Schwenkscheibe um die Scharnierachse 8 an das Verschieben der Schiebehülse 9 gekoppelt. Über den Mitnehmer 7 wird im Betrieb der Hubkolbenmaschine die Rotation der Maschinenwelle 2 auf die Schwenkscheibe 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 and engages with a spherical articulation section in a radially open receptacle 15 on the part of the swash plate (see Fig. 2). Since the driver 7 is fixed to the machine shaft, a pivoting of the swash plate about the hinge axis 8 is coupled to the displacement of the sliding sleeve 9. About the driver 7, the rotation of the machine shaft 2 is transmitted to the swash plate during operation of the reciprocating piston (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 trennt. Die Hauptmittelebene rotiert mit der Maschinenwelle.Perpendicular to the hinge axis 8 is defined by the axis of rotation 11 main center plane which separates a suction side of a pressure side of the reciprocating engine. The main center plane rotates with the machine shaft.

Die Schwenkscheibe 5 ist an ihrem Umfang im Bereich eines jeden Kolbens 4 von einer Gelenkanordnung 6 umgriffen, die über die Schwenkscheibe gleitet, wenn diese ihre Rotationsbewegung w ausführt. Bei einer Neigung der Schwenkscheibe 5 gegenüber der Maschinenwelle 2, veranlaßt die Schwenkscheibe im Verlauf ihrer Rotationsbewegung die auf der Druckseite befindlichen Kolben zu einer Verdichtungsbewegung und die auf der Saugseite liegenden Kolben zu einer Ansaugbewegung. In Fig. 2 ist eine vereinfachte Prinzipskizze zur Kraftübertragung zwischen Maschinenwelle 2 und Kolben 4 dargestellt.The swash plate 5 is encompassed at its periphery in the region of each piston 4 by a hinge assembly 6 which slides over the swash plate when it carries out its rotational movement w. With an inclination of the swash plate 5 relative to the machine shaft 2, causes the swash plate in the course of its rotation, the piston located on the pressure side to a compression movement and lying on the suction side of the piston to a suction movement. In Fig. 2 is a simplified schematic diagram for power transmission between the machine shaft 2 and piston 4 is shown.

Weitere Angaben zum Aufbau und zur Funktion der Hubkolbenmaschine 2 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 sind der Kraftübertragungsmittelpunkt einer Gelenkanordnung jeweils exakt in Verlängerung der zugehörigen Kolbenachse auf dem Zylindermantel angeordnet.Further information on the structure and function of the reciprocating engine 2 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 power transmission center of a hinge assembly are each arranged exactly in extension of the associated piston axis on the cylinder jacket.

Ein erstes Ausführungsbeispiel der Gelenkanordnung 6 ist in den Fig. 3 und 4 schematisch näher dargestellt. Die Fig. 3 und 4 (wie auch die Fig. 5 und 6) geben dabei eine Ansicht in radialer Richtung von der Maschinenwelle 2 nach außen wieder, wobei die sich in Richtung des Pfeils w bewegende Schwenkscheibe 5 in Fig. 3 einen Saughub des Kolbens 4 (Pfeil s) und in Fig. 4 einen Verdichtungshub des Kolbens 4 (Pfeil v) bewirkt.A first embodiment of the joint arrangement 6 is shown schematically in FIGS. 3 and 4 in more detail. FIGS. 3 and 4 (as well as FIGS. 5 and 6) show a view in the radial direction from the machine shaft 2 to the outside again, the swivel disk 5 moving in the direction of the arrow w in FIG. 3 showing a suction stroke of the piston 4 (arrow s) and in Fig. 4 causes a compression stroke of the piston 4 (arrow v).

Die Gelenkanordnung 6 weist eine Aufnahme mit zwei gleichen, in etwa kugelförmigen Führungs- und Gleitflächen 6a auf, in der zwei kugelkappenförmige Gleitelemente 16, 17 gelagert sind. Der Aufnahme sowie den Gleitelementen 16, 17 ist ein gemeinsamer geometrischer Mittelpunkt M zugeordnet, der zugleich einen Kraftübertragungsmittelpunkt K der Gelenkanordnung 6 bildet. Die Gleitflächen 6a der Aufnahme und die kugeligen Flächen der Gleitelemente 16, 17 weisen den gleichen Radius und die gleiche Krümmung auf. Die Gleitelemente 16, 17 sitzen mit einem geringen Spiel auf der Schwenkscheibe 5 auf. Der Kraftübertragungsmittelpunkt K ist entgegen der Drehrichtung w vor der Kolbenachse 12 des zugehörigen Kolbens 4 auf dem alle Kolbenachsen beinhaltenden Zylindermantel positioniert. Der Abstand des Kraftübertragungsmittelpunktes M zur Kolbenachse 12 beträgt vorzugsweise 10% bis 20% des Kolbenhubs.The joint assembly 6 has a receptacle with two identical, approximately spherical guide and sliding surfaces 6a, in which two spherical cap-shaped sliding elements 16, 17 are mounted. The recording and the sliding elements 16, 17 is associated with a common geometric center M, which also forms a power transmission center K of the joint assembly 6. The sliding surfaces 6a of the receptacle and the spherical surfaces of the sliding elements 16, 17 have the same radius and the same curvature. The sliding elements 16, 17 sit with a small clearance on the swash plate 5. The power transmission center K is positioned counter to the direction of rotation w in front of the piston axis 12 of the associated piston 4 on the cylinder jacket containing all piston axes. The distance of the power transmission center M to the piston axis 12 is preferably 10% to 20% of the piston stroke.

Beim Saughub (gem. Fig. 3) ist die von der Schwenkscheibe 5 auf den Kolben 4 übertragene Kraft Fs im allgemeinen deutlich kleiner als die beim Verdichtungshub (gem. Fig. 4) übertragene Kraft Fv. Daraus ergeben sich ebenfalls stark unterschiedliche Querkräfte Qs und Qv. Diese Querkräfte Qs und Qv erzeugen jeweils Momente auf den Kolben, die von der Kolbenführung 10 ausgeglichen werden müssen und schließlich auf Abstützkräfte As und Av führen. Die Abstützkräfte As und Av sind idealisiert im Bereich des unteren Endes der Kolbenführung 10 dargestellt. Durch den seitlichen Versatz des Kraftübertragungsmittelpunktes M ergeben sich idealisierte Krafteinleitungspunkte Ks und Kv auf der Kolbenachse 12. Der Krafteinleitungspunkt Ks für den Saughub liegt somit weiter entfernt vom Kolben 4 und von der Kolbenführung 10 als der Kraftübertragungsmittelpunkt K der Gelenkanordnung, während der Krafteinleitungspunkt Kv für den Verdichtungshub näher am Kolben 4 liegt als der Kraftübertragungsmittelpunkt K der Gelenkanordnung. Für den Saughub (gem. Fig. 3) bedeutet dies, daß die Querkraft Qs weiter von der Kolbenführung 10 entfernt eingeleitet wird, während beim Verdichtungshub (gem. Fig. 4) die Querkraft Qv näher an der Kolbenführung 10 eingeleitet wird als ohne einen Versatz zwischen Kraftübertragungsmittelpunkt K und Kolbenachse 12. Dadurch ergibt sich für den Saughub ein gegenüber einer Anordnung ohne Versatz vergleichsweise erhöhtes Moment auf den Kolben und für den Verdichtungshub ein vergleichsweise reduziertes Moment. Entsprechend verhält es sich mit den Abstützkräften As und Av, die in einer bevorzugten Ausführungsform näherungsweise gleich groß sind.In the intake stroke (acc. Fig. 3) transmitted from the swash plate 5 to the piston 4 force F s, in general, is significantly smaller than that in the compression stroke (acc. Fig. 4) transmitted force F v. This also results in very different transverse forces Q s and Q v . These transverse forces Q s and Q v respectively generate torques on the pistons, which must be compensated by the piston guide 10 and finally lead to supporting forces A s and A v . The supporting forces A s and A v are idealized in the region of the lower end of the piston guide 10. Due to the lateral offset of the power transmission center M arise Idealized force application points K s and K v on the piston axis 12. The force application point K s for the suction stroke is thus further away from the piston 4 and the piston guide 10 than the power transmission center K of the joint assembly, while the force application point K v for the compression stroke closer to the piston 4th is located as the power transmission center K of the joint assembly. For the suction stroke (according to Fig. 3) this means that the transverse force Q s is introduced farther away from the piston guide 10, while during the compression stroke (according to Fig. 4) the transverse force Q v is introduced closer to the piston guide 10 than without an offset between the power transmission center K and the piston axis 12. This results for the suction stroke compared to an arrangement without offset comparatively increased moment on the piston and for the compression stroke a comparatively reduced moment. The same applies to the supporting forces A s and A v , which are approximately equal in a preferred embodiment.

Ein zweites Ausführungsbeispiel der erfindungsgemäßen Gelenkanordnung 6 ist in Fig. 5 dargestellt. Die Gelenkanordnung 6 weist eine Aufnahme mit zwei kugeligen Gleit-/Führungsflächen 6a, 6b auf, in der ein erstes Gleitelement 18 mit einer kugelabschnittsförmigen Gleitfläche 18a und ein zweites Gleitelement 19 mit einer kugelabschnittsförmigen Gleitfläche 19a gelagert sind. Das erste Gleitelement 18 ist auf der dem zugehörigen Kolben zugewandten Seite, das zweite Gleitelement 19 auf der von dem Kolben abgewandten Seite der Schwenkscheibe 5 angeordnet, so daß die Schwenkscheibe 5 von den Gleitelementen 18, 19 umgriffen ist.A second embodiment of the hinge arrangement 6 according to the invention is shown in FIG. The joint arrangement 6 has a receptacle with two spherical sliding / guide surfaces 6a, 6b, in which a first sliding element 18 with a spherical segment-shaped sliding surface 18a and a second sliding element 19 with a spherical segment-shaped sliding surface 19a are mounted. The first sliding element 18 is arranged on the side facing the associated piston, the second sliding element 19 on the side facing away from the piston side of the swash plate 5, so that the swash plate 5 is encompassed by the sliding elements 18, 19.

Der geometrische Mittelpunkt M1 des ersten Gleitelementes 18 ist zwischen der Mittelebene 5a der Schwenkscheibe 5 und dem (nicht dargestellten) Kolben angeordnet, während der geometrische Mittelpunkt M2 des zweiten Gleitelementes 19 auf der Mittelebene 5a liegt. Somit ergeben sich für eine gleiche Winkelbeweglichkeit unterschiedliche Krümmungsradien der Gleitflächen 18a und 19a, wobei der kleinere Radius bei dem auf Seiten der Kolbenführung angeordneten Gleitelement 18 vorgesehen ist. In der "Neutralstellung" der Schwenkscheibe 5, d.h. wenn Schwenkscheibe und Maschinenwelle einen Winkel von 90° einschließen, sitzen die Gleitelemente 18, 19 mit einem gewissen Spiel auf der Schwenkscheibe 5, so daß beim Anlauf der Hubkolbenmaschine geringe Reibungskräfte zwischen den Gleitelementen und der Schwenkscheibe auftreten und sich rasch ein Schmierfilm bilden kann. Das genannte Spiel reduziert sich bei einer Neigung der Schwenkscheibe 5 (zunehmender Schwenkwinkel) aus Gründen der Geometrie, so daß sich schließlich bei einer in Fig. 5 gezeigten Neigung der Schwenkscheibe im lastfreien Zustand eine Verspannung der Gelenkanordnung ergibt (Vorspannung). Diese Vorspannung wird dadurch kompensiert, daß die Gelenkanordnung 6 durch im Betrieb der Hubkolbenmaschine auftretende Kräfte aufgebogen wird. Im Idealfall neutralisieren sich im Lastzustand die statische Vorspannung und die dynamischen Betriebskräfte an der Gelenkanordnung.The geometric center M 1 of the first sliding element 18 is arranged between the median plane 5 a of the swash plate 5 and the piston (not shown), while the geometric center M 2 of the second sliding element 19 lies on the median plane 5 a. Thus arise for a same angular mobility different radii of curvature of Sliding surfaces 18a and 19a, wherein the smaller radius is provided in the arranged on the side of the piston guide slide 18. In the "neutral position" of the swash plate 5, ie when the swash plate and machine shaft enclose an angle of 90 °, the sliding elements 18, 19 sit with a certain play on the swash plate 5, so that during start-up of the reciprocating engine low frictional forces between the sliding elements and the swash plate occur and can quickly form a lubricating film. Said game is reduced with an inclination of the swash plate 5 (increasing swivel angle) for reasons of geometry, so that finally results in a tilt of the swash plate shown in Fig. 5 in the load-free state, a tension of the joint assembly (bias). This bias is compensated by the fact that the joint assembly 6 is bent by occurring during operation of the reciprocating engine forces. Ideally, the static preload and the dynamic operating forces at the joint arrangement are neutralized in the load condition.

Da mit zunehmendem Schwenkwinkel der Schwenkscheibe 5 die von der Gelenkanordnung 6 aufzunehmende Belastung in beide Richtungen der Kolbenbewegung steigt, ergibt sich eine zunehmende, schwellende elastische Aufbiegung der Gelenkanordnung 6 mit entsprechender Geräuschentwicklung. Diese kann durch die vorgeschlagene Anordnung sowohl bei der Saug- als auch bei der. Verdichtungsbewegung gleichermaßen stark vermindert bzw. eliminiert werden.Since with increasing pivot angle of the swash plate 5, the load to be absorbed by the joint assembly 6 increases in both directions of the piston movement, there is an increasing, swelling elastic bending of the joint assembly 6 with corresponding noise. This can be achieved by the proposed arrangement both in the suction and in the. Compression movement equally greatly reduced or eliminated.

Der Kraftübertragungsmittelpunkt der Gelenkanordnung 6 befindet sich im Zustand der Vorspannung zwischen den beiden geometrischen Mittelpunkten M1, M2, so daß die Krafteinleitung in den Kolben (gegenüber Anordnungen mit einem Kraftübertragungsmittelpunkt auf der Mittelebene 5a) generell näher an der Kolbenführung erfolgt und ein kleineres Kippmoment auf den Kolben ausgeübt wird. Dennoch sind Ausführungsbeispiele vorsehbar, bei denen die geometrischen Mittelpunkte M1, M2 in etwa spiegelsymmetrisch bezüglich der Mittelebene 5a und der Kraftübertragungsmittelpunkt auf der Mittelebene 5a angeordnet sind.The power transmission center of the joint assembly 6 is in the state of bias between the two geometric centers M 1 , M 2 , so that the force is introduced into the piston (relative to arrangements with a power transmission center on the center plane 5 a) generally closer to the piston guide and a smaller overturning moment is exerted on the piston. Nevertheless, embodiments are foreseeable, in which the geometric Midpoints M 1 , M 2 are arranged approximately mirror-symmetrically with respect to the center plane 5a and the power transmission center on the center plane 5a.

Ein drittes Ausführungsbeispiel der erfindungsgemäßen Gelenkanordnung 6 ist in Fig. 6 dargestellt. Die Gelenkanordnung 6 umfaßt zwei Gleitelemente 20, 21 entsprechend denjenigen in den zuvor beschriebenen Ausführungsbeispielen. Die Gleitelemente 20, 21 weisen jeweils kugelabschnittsförmige Gleitflächen 20a, 21a auf, die in einer Aufnahme 6c, 6d gleiten. Die Gleitflächen 20a, 21a besitzen geometrische Mittelpunkte M3, M4, die zum einen näherungsweise auf der Mittelebene 5a der Schwenkscheibe 5 und zum anderen auf dem Zylindermantel liegen, auf welchem auch sämtliche Kolbenachsen 12 (vgl. Fig. 1 bis 3) der Hubkolbenmaschine positioniert sind. Der geometrische Mittelpunkt M3 des näher an der Kolbenführung liegenden Gleitelementes 20 ist in Drehrichtung der Schwenkscheibe (Pfeil w) gesehen hinter dem Mittelpunkt M4 des gegenüberliegenden Gleitelementes 21 angeordnet. Dadurch ergibt sich aus geometrischen Gründen bei einer wie in Fig. 6 dargestellten Neigung der Schwenkscheibe 5 eine Reduzierung des in der "Neutralstellung" der Schwenkscheibe vorgesehenen Spiels. Somit erfolgt eine Verspannung der Gleitelemente 20, 21 beim Saughub entsprechend Fig. 6. Bei einer Neigung der Schwenkscheibe 5 in die entgegengesetzte Richtung (Verdichtungshub, nicht dargestellt) ergibt sich eine Vergrößerung des in der "Neutralstellung" vorgesehenen Spiels.A third embodiment of the joint arrangement 6 according to the invention is shown in FIG. The hinge assembly 6 comprises two sliding members 20, 21 corresponding to those in the previously described embodiments. The sliding elements 20, 21 each have ball-section-shaped sliding surfaces 20a, 21a, which slide in a receptacle 6c, 6d. The sliding surfaces 20a, 21a have geometric centers M 3 , M 4 , which lie approximately on the center plane 5a of the swash plate 5 and the other on the cylinder jacket, on which all piston axes 12 (see Fig. 1 to 3) of the reciprocating engine are positioned. The geometric center M 3 of the closer lying on the piston guide slide 20 is seen in the direction of rotation of the swash plate (arrow w) behind the center M 4 of the opposite sliding element 21. As a result, for geometrical reasons, a tilt of the swashplate 5 as shown in FIG. 6 results in a reduction of the clearance provided in the "neutral position" of the swashplate. Thus, a tension of the sliding elements 20, 21 during the suction stroke corresponding to Fig. 6. With an inclination of the swash plate 5 in the opposite direction (compression stroke, not shown) results in an enlargement of the provided in the "neutral position" game.

In einem modifizierten Ausführungsbeispiel ist eine Gelenkanordnung eines Kolbens vorgesehen, die Gleitsteine mit kugelabschnittsförmigen Gleitflächen aufweist, deren Mittelpunkte gemäß einer Kombination der in den zuvor genannten Ausführungsbeispielen vorliegenden Merkmale vor der zugehörigen Kolbenachse positioniert, in einer Richtung parallel zur Kolbenachse voneinander beabstandet und/oder in Drehrichtung der Schwenkscheibe zueinander versetzt sind.In a modified embodiment, a joint arrangement of a piston is provided, the sliding blocks having spherical portion sliding surfaces positioned their centers according to a combination of the present in the aforementioned embodiments features in front of the associated piston axis, spaced apart in a direction parallel to the piston axis and / or in the rotational direction the swash plate are offset from each other.

Mittels der vorgeschlagenen Gelenkanordnungen lassen sich Hubkolbenmaschinen konzipieren, die bei im wesentlichen gleicher Dimensionierung gegenüber Hubkolbenmaschinen nach dem Stand der Technik höhere dynamische Belastungen im Bereich der Kraftübertragung zwischen Schwenkscheibe und Kolben ertragen können. Gleichzeitig ergeben sich reduzierte bzw. vergleichmäßigte Kräfteverhältnisse im Bereich der Kolbenführungen sowie an den Gelenkanordnungen. Somit ergeben sich höhere Leistungen bei gleichzeitig ruhigerem Lauf und niedrigeren Betriebsgeräuschen.By means of the proposed joint arrangements, reciprocating engines can be designed which can withstand substantially greater dynamic loads in the region of the power transmission between the swivel disk and the piston with essentially the same dimensions as compared with reciprocating engines of the prior art. At the same time there are reduced or evened balance of power in the area of the piston guides and on the joint arrangements. This results in higher performance with a smoother running and lower operating noise.

Claims (3)

  1. Reciprocating-piston machine, in particular refrigerant compressor (1) for a motor vehicle air-conditioning system, with
    - a machine shaft (2),
    - a plurality of pistons (4), the piston axes of which are arranged, in each case at the same distance from the machine shaft, on a cylinder envelope around the machine shaft,
    - an, in particular, annular pivoting disc (5) which is driven by the machine shaft (2) and which
    - engages on the pistons in each case via a joint arrangement (6),
    - the joint arrangement having an at least partially spherical receptacle, in which
    - at least one sliding or rolling element is arranged moveably relative to the associated piston and relative to the pivoting disc, wherein
    - a first sliding element (18, 20) has a first sliding face (18a, 20a) in the form of a spherical segment, with a first geometrical centre (M1, M3), and
    - a second sliding element (19, 21) has a second sliding face (19a, 21a) in the form of a spherical segment, with a second geometrical centre (M2, M4), the first and the second centres being arranged at a distance from one another, characterized in that
    - the first geometrical centre (M1) is arranged on that side of the mid-plane (5a) of the pivoting disc which faces the piston guide and the second geometrical centre (M2) is arranged approximately on the mid-plane (5a) of the pivoting disc or likewise on that side of the mid-plane (5a) of the pivoting disc which faces the piston guide.
  2. Reciprocating-piston machine according to Claim 1, characterized in that
    - the first geometrical centre (M3) is arranged on the cylinder envelope so as to be offset in the direction of rotation (w) relative to the second geometrical centre (M4).
  3. Reciprocating-piston machine according to Claim 1 or 2, characterized in that
    - the joint arrangement (6) is assigned a centre of force transmission (K) which is located approximately on the cylinder envelope of the piston axes and which
    - is positioned in front of the associated piston axis (12) with respect to the direction of rotation of the pivoting disc (5).
EP02742856A 2001-05-16 2002-03-14 Reciprocating engine with an articulation arrangement Expired - Lifetime EP1387957B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10124034A DE10124034A1 (en) 2001-05-16 2001-05-16 Piston machine with pivot fitting has mean power transmission point of pivot fitting on cylinder jacket of piston axis
DE10124034 2001-05-16
PCT/EP2002/002828 WO2002093011A1 (en) 2001-05-16 2002-03-14 Reciprocating engine with an articulation arrangement

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JP (1) JP4137646B2 (en)
KR (1) KR100871262B1 (en)
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KR100871262B1 (en) 2008-11-28
CN1509375A (en) 2004-06-30
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JP2005509102A (en) 2005-04-07
DE10124034A1 (en) 2002-11-21
JP4137646B2 (en) 2008-08-20
ATE368180T1 (en) 2007-08-15
KR20040012840A (en) 2004-02-11
CN1298997C (en) 2007-02-07
US20040120831A1 (en) 2004-06-24
DE50210554D1 (en) 2007-09-06
US7201566B2 (en) 2007-04-10

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