EP0752530B1 - Reciprocating piston machine with swash plate mechanism - Google Patents

Reciprocating piston machine with swash plate mechanism Download PDF

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Publication number
EP0752530B1
EP0752530B1 EP96810373A EP96810373A EP0752530B1 EP 0752530 B1 EP0752530 B1 EP 0752530B1 EP 96810373 A EP96810373 A EP 96810373A EP 96810373 A EP96810373 A EP 96810373A EP 0752530 B1 EP0752530 B1 EP 0752530B1
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EP
European Patent Office
Prior art keywords
piston
pistons
swash plate
guide
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
EP96810373A
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German (de)
French (fr)
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EP0752530A1 (en
Inventor
Peter Kuhn
Frank Obrist
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.)
Bayerische Motoren Werke AG
Audi AG
Mercedes Benz Group AG
Original Assignee
Bayerische Motoren Werke AG
DaimlerChrysler AG
Audi AG
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Application filed by Bayerische Motoren Werke AG, DaimlerChrysler AG, Audi AG filed Critical Bayerische Motoren Werke AG
Publication of EP0752530A1 publication Critical patent/EP0752530A1/en
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Publication of EP0752530B1 publication Critical patent/EP0752530B1/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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18296—Cam and slide
    • Y10T74/18336—Wabbler type

Definitions

  • the invention relates to a reciprocating piston machine with a swash plate gear with the features of the preamble of the claim 1.
  • a reciprocating piston machine of this type is known from FR-A-563 879.
  • pin-shaped drivers engage in bearing bushes one whose diameter is larger than that of Pistons so that they connect to each other in a two pistons Housing part of the piston are stored, which over extends the circumference of the piston.
  • Such driver designs is with relatively large frictional forces connected.
  • the pin engagement limits the possible change in the stroke length of the working piston.
  • US-A-2,405,006 is a through a swash plate powered reciprocating piston machine known in which a driver pin with a head with a spherical surface into a engages bore transverse to the piston.
  • the given one Line contact between the ball head and the bore leads to increased wear, especially since such Pistons are usually made of light metal.
  • GB-A-196 158 has a constant stroke length Reciprocating machine with swash plate gear known in the the swashplate is disc-shaped up to a driving space the piston extends.
  • the drive transmission takes place from the disc to the pistons through four half-shell-shaped ones Guide parts that are curved on both sides of the disc Guide ribs held in a form-fitting and sliding manner are. Because of the alternating high forces on it The drive transmission is subject to wear and tear and requires high dimensional accuracy, with correspondingly high Production costs.
  • the invention has for its object a reciprocating piston machine of the type mentioned at the beginning, which is a minor one Has size that can be done with less effort or cheaper can be produced and the low friction losses in the drive transmission from the swash plate to the pistons having.
  • the reciprocating piston engine 1 has, for example, seven pistons 2 which arranged side by side in the circumferential direction of the machine are.
  • the swash plate 3 has one with the machine shaft 4 rotating disc part 5 and one in drive connection with the piston 2 standing and therefore not rotating Disc part 6.
  • a rotary bearing 9 equipped with bearing balls 7, 8 provided that absorbs axial and radial forces to which the To transfer piston drive serving wobble.
  • connection between the machine shaft 4 and the rotating one Disk part 5 is carried out by a driving pin 10, which enables the angular adjustment of the swash plate 3 Recess 11 of a laterally on the rotating disc part 5 molded driver body 12 engages.
  • a driving pin 10 which enables the angular adjustment of the swash plate 3 Recess 11 of a laterally on the rotating disc part 5 molded driver body 12 engages.
  • this carries a spherical body 13 which from a correspondingly shaped spherical surface 14 of the rotating Disk part 5 is included.
  • the force for the angular adjustment of the swash plate 3 results from the sum of the pistons 2 on both sides against each other acting pressures so that this force from the pressure in the Drive room 15 is dependent.
  • This pressure can be a flow connection with an external compressed gas flow be provided when using the machine as a compressor is available.
  • This connection can have channels 16 that are connected to the sealing and storage space provided for the machine shaft 4 17 lead and then in the drive room 15, so that too cooling is achieved.
  • the bottom dead center of the piston movement changes, while top dead center remains unchanged or largely remains unchanged.
  • the seven pistons are 2 for the execution of their stroke movement connected to the circumference of the swash plate 3.
  • the piston 2 has a piston shaft 22, the piston head 24 carrying the piston rings 23 rigid with a guide head sliding in the cylinder bore 25 26 connects.
  • the swash plate has 3 for each piston 2 a radially extending from it, short ball pin 27 which with the ball head 21 in a transverse bore 28 of the guide head 26 engages.
  • Line contact leading to excessive pressure loads between the ball head 21 and a cylindrical transverse bore 28 to avoid, is preferably the ball head 21, according to the Model of the outer rings of radial spherical plain bearings, from one Includes slide ring 29 with a spherical inner surface 30.
  • the Engagement of the ball head 21 in the slide ring 29 causes this during the radial movement of the ball head 21 in the transverse bore 28 of the guide head 26 slides.
  • FIG. 5 illustrates that the ball joint 20 'between a piston 2 and the swash plate 3 can also be carried out with the reverse arrangement as described above is by a ball head 21 'rigidly on the guide head 26' of the Piston 2 is attached and the transverse bore 28 'receiving it extends radially into the swash plate 3. Also at In this embodiment, the ball head 21 'of a sliding sleeve, not shown, may be included.
  • At least one piston 2 is provided with an anti-rotation device that the pivoting through the articulation between Swash plate 3 and piston 2 is prevented.
  • a guide pin 33 provided with two flats 32 through the wall 34 of the machine housing 35 and engages in one axially parallel guide groove 36 of the piston, so that between the flats 32 and the side walls of the Guide groove 36 is a sliding contact.
  • the shaft 22 is the relevant one Provide piston 2 with a suitable cross section, that of the slim shown in the lower part of Fig.1 Cross section deviates.
  • each piston 2 by a guide pin engaging in a guide groove 36 is guided against rotation about its axis.
  • the Guide pin 33 with a certain play between the side walls the guide groove 36 included. Because the seven pistons 2 an oscillating, phase-shifted, perform limited rotation, takes over in any wobble position the swash plate 3 that piston the anti-rotation of the disc part 6 of the swash plate 3, in which the contact between the guide pin 33 and a side wall of the associated guide groove 36 is closest. Consequently changes the guide contact in the circumferential direction of the machine from one Piston 2 to the other, so that the stress through the guide is distributed accordingly.

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

Description

Die Erfindung betrifft eine Hubkolbenmaschine mit Taumelscheibengetriebe mit den Merkmalen des Oberbegriffs des Patentanspruchs 1.The invention relates to a reciprocating piston machine with a swash plate gear with the features of the preamble of the claim 1.

Eine Hubkolbenmaschine dieser Art ist bekannt durch die FR-A-563 879. Bei ihr greifen zapfenförmige Mitnehmer in Lagerbuchsen ein, deren Durchmesser grösser ist als derjenige der Kolben, so dass sie in einem zwei Kolben miteinander verbindenden Gehäuseteil des Kolbens gelagert sind, der sich über den Umfang des Kolbens hinaus erstreckt. Eine solche Mitnehmerkonstruktionen ist mit verhältnismässig grossen Reibungskräften verbunden. Ausserdem begrenzt der Zapfeneingriff die mögliche Veränderung der Hubweite der Arbeitskolben.A reciprocating piston machine of this type is known from FR-A-563 879. With it, pin-shaped drivers engage in bearing bushes one whose diameter is larger than that of Pistons so that they connect to each other in a two pistons Housing part of the piston are stored, which over extends the circumference of the piston. Such driver designs is with relatively large frictional forces connected. In addition, the pin engagement limits the possible change in the stroke length of the working piston.

Durch die US-A- 2,405,006 ist eine durch eine Schwenkscheibe angetriebene Hubkolbenmaschine bekannt, bei der ein Mitnehmerzapfen mit einem eine Kugelfläche aufweisenden Kopf in eine quer zum Kolben verlaufende Bohrung eingreift. Der somit gegebene Linienkontakt zwischen dem Kugelkopf und der Bohrung führt zu erhöhtem Verschleiss, insbesondere da solche der Kolben meist aus Leichtmetall hergestellt werden.By US-A-2,405,006 is a through a swash plate powered reciprocating piston machine known in which a driver pin with a head with a spherical surface into a engages bore transverse to the piston. The given one Line contact between the ball head and the bore leads to increased wear, especially since such Pistons are usually made of light metal.

Durch die GB-A-196 158 ist eine in ihrer Hubweite konstante Hubkolbenmaschine mit Taumelscheibengetriebe bekannt, bei der die Taumelscheibe sich scheibenförmig bis in einen Mitnehmerraum der Kolben erstreckt. Dabei erfolgt die Antriebsübertragung von der Scheibe auf die Kolben durch vier halbschalenförmige Führungsteile, die beidseitig der Scheibe mittels bogenförmiger Führungsrippen formschlüssig und gleitend gehalten sind. Aufgrund der wechselnd wirkenden hohen Kräfte an dieser Antriebsübertragung ist die Konstruktion verschleissanfällig und erfordert eine hohe Massgenauigkeit, mit entsprechend hohen Herstellungskosten. GB-A-196 158 has a constant stroke length Reciprocating machine with swash plate gear known in the the swashplate is disc-shaped up to a driving space the piston extends. The drive transmission takes place from the disc to the pistons through four half-shell-shaped ones Guide parts that are curved on both sides of the disc Guide ribs held in a form-fitting and sliding manner are. Because of the alternating high forces on it The drive transmission is subject to wear and tear and requires high dimensional accuracy, with correspondingly high Production costs.

Der Erfindung liegt die Aufgabe zugrunde, eine Hubkolbenmaschine der eingangs genannten Art zu finden, die eine geringe Baugrösse hat, die sich mit geringerem Aufwand bzw. kostengünstiger herstellen lässt und die geringe Reibungsverluste in der Antriebsübertragung von der Taumelscheibe zu den Kolben aufweist.The invention has for its object a reciprocating piston machine of the type mentioned at the beginning, which is a minor one Has size that can be done with less effort or cheaper can be produced and the low friction losses in the drive transmission from the swash plate to the pistons having.

Die Lösung dieser Aufgabe erfolgt erfindungsgemäss aufgrund der kennzeichnenden Merkmale des Patentanspruchs 1.According to the invention, this object is achieved on the basis of of the characterizing features of claim 1.

Durch die Kombination Kugelkopf/Querführung ergeben sich kleine Kontaktfläche der Antriebsübertragung, so dass nur geringe Reibungswiderstände auftreten. Durch die Vermeidung eines Linienkontaktes ist auch eine geringe Verschleissanfälligkeit gegeben. Ausserdem ergeben sich Vorteile bei der Herstellung und kompakten Gestaltung der Maschine.The combination of a ball head / transverse guide results in small contact area of the drive transmission, so only low frictional resistance occur. By avoiding it a line contact is also less prone to wear given. There are also advantages in manufacturing and compact design of the machine.

Vorteilhafte Ausführungsformen der Erfindung sind Gegenstand der abhängigen Patentansprüche und der folgenden Beschreibung anhand der Zeichnungen zu entnehmen.Advantageous embodiments of the invention are the subject of the dependent claims and the following description can be seen from the drawings.

Es zeigt:

Fig.1
einen Axialschnitt einer ersten Ausführungsform der Hubkolbenmaschine,
Fig.2
einen Schnitt entlang der Linie II-II der Fig.1,
Fig.3
eine vergrösserte Darstellung eines Bereichs der Fig.2,
Fig.4
eine Schnittdarstellung entsprechend Fig.2, einer Ausführungsform, bei der jeder Kolben eine Verdrehsicherung hat und
Fig.5
einen Axialschnitt einer zweiten Ausführungsform der Hubkolbenmaschine.
It shows:
Fig.1
3 shows an axial section of a first embodiment of the reciprocating piston machine,
Fig.2
2 shows a section along the line II-II of FIG. 1,
Figure 3
2 shows an enlarged representation of an area in FIG. 2,
Figure 4
a sectional view corresponding to Figure 2, an embodiment in which each piston has an anti-rotation and
Figure 5
an axial section of a second embodiment of the reciprocating piston machine.

Der grundsätzliche Aufbau und die Wirkungsweise einer Hubkolbenmaschine mit Taumelscheibengetriebe ist durch die Fachliteratur bekannt, wie z.B. durch die US-A-5,205,718 oder die DE-A-4139186.The basic structure and mode of operation of a reciprocating piston machine with swashplate gear is through the specialist literature known, e.g. by US-A-5,205,718 or DE-A-4139186.

Die Hubkolbenmaschine 1 hat beispielsweise sieben Kolben 2, die in Umfangsrichtung der Maschine nebeneinander angeordnet sind. Die Taumelscheibe 3 hat einen sich mit der Maschinenwelle 4 drehenden Scheibenteil 5 und einen in Antriebsverbindung mit den Kolben 2 stehenden und folglich nicht mitdrehenden Scheibenteil 6. Hierfür ist zwischen beiden Scheibenteilen 5,6 eine mit Lagerkugeln 7,8 ausgerüstete Drehlagerung 9 vorgesehen, die axiale und radiale Kräfte aufnimmt, um die dem Kolbenantrieb dienende Taumelbewegung zu übertragen.The reciprocating piston engine 1 has, for example, seven pistons 2 which arranged side by side in the circumferential direction of the machine are. The swash plate 3 has one with the machine shaft 4 rotating disc part 5 and one in drive connection with the piston 2 standing and therefore not rotating Disc part 6. For this there is 5.6 between the two disc parts a rotary bearing 9 equipped with bearing balls 7, 8 provided that absorbs axial and radial forces to which the To transfer piston drive serving wobble.

Die Verbindung zwischen der Maschinenwelle 4 und dem mitdrehenden Scheibenteil 5 erfolgt durch einen Mitnehmerbolzen 10, der in eine die Winkelverstellung der Taumelscheibe 3 ermöglichende Ausnehmung 11 eines seitlich am mitdrehenden Scheibenteil 5 angeformten Mitnehmerkörpers 12 eingreift. Für die eine Schwenkbewegung zulassende Lagerung der Taumelscheibe 3 auf der Maschinenwelle 4 trägt diese einen Kugelkörper 13, der von einer entsprechend geformten Kugelfläche 14 des mitdrehenden Scheibenteils 5 umfasst ist.The connection between the machine shaft 4 and the rotating one Disk part 5 is carried out by a driving pin 10, which enables the angular adjustment of the swash plate 3 Recess 11 of a laterally on the rotating disc part 5 molded driver body 12 engages. For the a swiveling mounting of the swash plate 3 on the machine shaft 4 this carries a spherical body 13 which from a correspondingly shaped spherical surface 14 of the rotating Disk part 5 is included.

Die Kraft für die Winkelverstellung der Taumelscheibe 3 ergibt sich aus der Summe der jeweils beidseitig der Kolben 2 gegeneinander wirkenden Drücke, so dass diese Kraft vom Druck im Triebraum 15 abhängig ist. Für die Regelung dieses Druckes kann eine Strömungsverbindung mit einem äusseren Druckgasstrom vorgesehen sein, der bei Anwendung der Maschine als Verdichter vorhanden ist. Diese Verbindung kann Kanäle 16 aufweisen, die zu dem für die Maschinenwelle 4 vorgesehenen Dicht- und Lagerraum 17 führen und anschliessend in den Triebraum 15, so dass auch eine Kühlung erzielt wird. Entsprechend der Neigung der Taumelscheibe 3 ändert sich der untere Totpunkt der Kolbenbewegung, während der obere Totpunkt unverändert oder weitgehend unverändert bleibt. Je höher der Druck an der Unterseite der Kolben 2 bzw. im Triebraum 15 relativ zum Druck auf der Oberseite der Kolben 2 bzw. auf der Saugseite des Verdichters, umso kleiner wird die Hubweite der Kolben 2 und damit die Förderleistung des Verdichters .The force for the angular adjustment of the swash plate 3 results from the sum of the pistons 2 on both sides against each other acting pressures so that this force from the pressure in the Drive room 15 is dependent. For the regulation of this pressure can a flow connection with an external compressed gas flow be provided when using the machine as a compressor is available. This connection can have channels 16 that are connected to the sealing and storage space provided for the machine shaft 4 17 lead and then in the drive room 15, so that too cooling is achieved. According to the inclination of the swashplate 3 the bottom dead center of the piston movement changes, while top dead center remains unchanged or largely remains unchanged. The higher the pressure at the bottom of the Piston 2 or in the drive chamber 15 relative to the pressure on the top the piston 2 or on the suction side of the compressor, all the more the stroke length of the pistons 2 becomes smaller and thus the delivery rate of the compressor.

Für die Ausführung ihrer Hubbewegung sind die sieben Kolben 2 mit dem Umfang der Taumelscheibe 3 verbunden. Im Gegensatz zu vorbekannten Konstruktionen hat jede Verbindung zwischen einer Stelle der Taumelscheibe 3 und einem Kolben 2 nur ein Kugelgelenk 20, indem die Art der Lagerung des Kugelkopfes 21 dessen Bewegung quer zur Achse des Kolbens 2 bzw. radial zu der Taumelscheibe 3 zulässt. Hierfür hat der Kolben 2 einen Kolbenschaft 22, der seinen die Kolbenringe 23 tragenden Kolbenkopf 24 starr mit einem in der Zylinderbohrung 25 gleitenden Führungskopf 26 verbindet.The seven pistons are 2 for the execution of their stroke movement connected to the circumference of the swash plate 3. In contrast to previously known constructions has any connection between one Place the swash plate 3 and a piston 2 only a ball joint 20 by changing the type of storage of the ball head 21 Movement transverse to the axis of the piston 2 or radially to the swash plate 3 allows. For this, the piston 2 has a piston shaft 22, the piston head 24 carrying the piston rings 23 rigid with a guide head sliding in the cylinder bore 25 26 connects.

Bei den Ausführungsbeispielen nach Fig.1 bis 4 hat die Taumelscheibe 3 für jeden Kolben 2 einen sich radial von ihr wegerstreckenden, kurzen Kugelzapfen 27, der mit dem Kugelkopf 21 in eine Querbohrung 28 des Führungskopfes 26 eingreift.In the exemplary embodiments according to FIGS. 1 to 4, the swash plate has 3 for each piston 2 a radially extending from it, short ball pin 27 which with the ball head 21 in a transverse bore 28 of the guide head 26 engages.

Um einen zu starken Druckbelastungen führenden Linienkontakt zwischen dem Kugelkopf 21 und einer zylindrischen Querbohrung 28 zu vermeiden, ist vorzugsweise der Kugelkopf 21, nach dem Vorbild der Aussenringe von Radialgelenklagern, von einem Gleitring 29 mit kugelförmiger Innenfläche 30 umfasst. Der Eingriff des Kugelkopfes 21 in den Gleitring 29 bewirkt, dass dieser bei der Radialbewegung des Kugelkopfes 21 in der Querbohrung 28 des Führungskopfes 26 gleitet.Line contact leading to excessive pressure loads between the ball head 21 and a cylindrical transverse bore 28 to avoid, is preferably the ball head 21, according to the Model of the outer rings of radial spherical plain bearings, from one Includes slide ring 29 with a spherical inner surface 30. The Engagement of the ball head 21 in the slide ring 29 causes this during the radial movement of the ball head 21 in the transverse bore 28 of the guide head 26 slides.

Das Ausführungsbeispiel der Fig.5 veranschaulicht, dass das Kugelgelenk 20' zwischen einem Kolben 2 und der Taumelscheibe 3 auch mit umgekehrter Anordnung als zuvor beschrieben ausführbar ist, indem ein Kugelkopf 21' starr am Führungskopf 26' des Kolbens 2 befestigt ist und die ihn aufnehmende Querbohrung 28' sich radial in die Taumelscheibe 3 hinein erstreckt. Auch bei diesem Ausführungsbeispiel kann der Kugelkopf 21' von einer nichtdargestellten Gleithülse umfasst sein.The embodiment of Figure 5 illustrates that the ball joint 20 'between a piston 2 and the swash plate 3 can also be carried out with the reverse arrangement as described above is by a ball head 21 'rigidly on the guide head 26' of the Piston 2 is attached and the transverse bore 28 'receiving it extends radially into the swash plate 3. Also at In this embodiment, the ball head 21 'of a sliding sleeve, not shown, may be included.

Um zu verhindern, dass sich der Scheibenteil 6 der Taumelscheibe 3 durch die Reibungskräfte der Lagerung 9 mitdreht, ist an zumindest einem Kolben 2 eine Verdrehsicherung vorgesehen, so dass das Mitdrehen durch die Gelenkverbindung zwischen Taumelscheibe 3 und Kolben 2 verhindert wird. Hierfür erstreckt sich ein mit zwei Abflachungen 32 versehener Führungszapfen 33 durch die Wand 34 des Maschinengehäuses 35 und greift in eine achsparallel verlaufenden Führungsnut 36 des Kolbens ein, so dass zwischen den Abflachungen 32 und den Seitenwänden der Führungsnut 36 ein Gleitkontakt vorhanden ist.To prevent the disc part 6 of the swash plate 3 rotates by the frictional forces of the bearing 9 is on At least one piston 2 is provided with an anti-rotation device that the pivoting through the articulation between Swash plate 3 and piston 2 is prevented. For this extends a guide pin 33 provided with two flats 32 through the wall 34 of the machine housing 35 and engages in one axially parallel guide groove 36 of the piston, so that between the flats 32 and the side walls of the Guide groove 36 is a sliding contact.

Für die Aufnahme der Führungsnut 36 ist der Schaft 22 des betreffenden Kolbens 2 mit einem geeigneten Querschnitt versehen, der von dem im unteren Teil der Fig.1 gezeigten schlanken Querschnitt abweicht.For receiving the guide groove 36, the shaft 22 is the relevant one Provide piston 2 with a suitable cross section, that of the slim shown in the lower part of Fig.1 Cross section deviates.

Fig.4 zeigt ein Ausführungsbeispiel, bei dem jeder Kolben 2 durch einen in eine Führungsnut 36 eingreifenden Führungszapfen gegen Verdrehung um seine Achse geführt ist. Dabei ist der Führungszapfen 33 mit einem bestimmten Spiel zwischen den Seitenwänden der Führungsnut 36 eingeschlossen. Da die sieben Kolben 2 eine gegeneinander phasenverschobene, oszillierende, begrenzte Drehbewegung ausführen, übernimmt in jeder Taumelposition der Taumelscheibe 3 derjenige Kolben die Verdrehsicherung des Scheibenteils 6 der Taumelscheibe 3, bei dem der Kontakt zwischen dem Führungszapfen 33 und einer Seitenwand der zugehörigen Führungsnut 36 am nächsten ist. Folglich wechselt der Führungskontakt in Umfangsrichtung der Maschine von einem Kolben 2 zum anderen, so dass die Beanspruchung durch die Führung entsprechend verteilt wird.4 shows an exemplary embodiment in which each piston 2 by a guide pin engaging in a guide groove 36 is guided against rotation about its axis. Here is the Guide pin 33 with a certain play between the side walls the guide groove 36 included. Because the seven pistons 2 an oscillating, phase-shifted, perform limited rotation, takes over in any wobble position the swash plate 3 that piston the anti-rotation of the disc part 6 of the swash plate 3, in which the contact between the guide pin 33 and a side wall of the associated guide groove 36 is closest. Consequently changes the guide contact in the circumferential direction of the machine from one Piston 2 to the other, so that the stress through the guide is distributed accordingly.

Claims (4)

  1. Reciprocating piston machine with wobble plate gear, in which a first part (5) of the wobble plate (3) is in drive connection via a swivel joint (10,11;13,14) with the machine shaft and the second part (6) with the pistons (2), the wobble movement is transferred by means of a rotary bearing (9) from the first to the second wobble plate part and the drive connection with in each case one of the pistons (2) takes place by means of a driver (21), which is provided at the second part (6) of the wobble plate and which projects laterally into the piston (2), characterized in that the driver has the shape of a ball end (21,21') and is surrounded by a slip ring (29) with a spherical inner face (30), which is displaceably held in a guide bore (28) running transversely to the piston axis, whereby the pistons (2) are prevented from rotation.
  2. Reciprocating piston machine according to claim 1, characterized in that the ball ends (21) are rigidly fixed to the circumference of the second wobble plate part (6) and the ball guide (28) extends transversely through the drive-side end (26) of the piston (2).
  3. Reciprocating piston machine according to claim 1 or 2, characterized in that in at least one of the pistons (2) engages a guide element (33), so that the rotation of the piston (2) about its longitudinal axis is at least closely limited.
  4. Reciprocating piston machine according to one of claims 1 to 3, characterized in that the piston (2) has a piston top (24) carrying sealing rings (23) and a guide head (26), which are interconnected by means of a piston shaft(22).
EP96810373A 1995-07-05 1996-06-07 Reciprocating piston machine with swash plate mechanism Expired - Lifetime EP0752530B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH1957/95 1995-07-05
CH195795 1995-07-05
CH01957/95A CH691272A5 (en) 1995-07-05 1995-07-05 Reciprocating engine with swashplate mechanism.

Publications (2)

Publication Number Publication Date
EP0752530A1 EP0752530A1 (en) 1997-01-08
EP0752530B1 true EP0752530B1 (en) 2002-03-27

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EP96810373A Expired - Lifetime EP0752530B1 (en) 1995-07-05 1996-06-07 Reciprocating piston machine with swash plate mechanism

Country Status (5)

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US (1) US5752413A (en)
EP (1) EP0752530B1 (en)
JP (1) JP3373733B2 (en)
CH (1) CH691272A5 (en)
DE (1) DE59608940D1 (en)

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JPH10306774A (en) * 1997-03-03 1998-11-17 Luk Fahrzeug Hydraulik Gmbh & Co Kg Compressor for automobile air conditioner
US7153105B2 (en) * 2003-04-24 2006-12-26 Haldex Brake Corporation Compressor with swash plate housing inlet port
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JP3373733B2 (en) 2003-02-04
CH691272A5 (en) 2001-06-15
US5752413A (en) 1998-05-19
JPH0925872A (en) 1997-01-28
DE59608940D1 (en) 2002-05-02
EP0752530A1 (en) 1997-01-08

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