EP0752530A1 - Reciprocating piston machine with swash plate mechanism - Google Patents

Reciprocating piston machine with swash plate mechanism Download PDF

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Publication number
EP0752530A1
EP0752530A1 EP96810373A EP96810373A EP0752530A1 EP 0752530 A1 EP0752530 A1 EP 0752530A1 EP 96810373 A EP96810373 A EP 96810373A EP 96810373 A EP96810373 A EP 96810373A EP 0752530 A1 EP0752530 A1 EP 0752530A1
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EP
European Patent Office
Prior art keywords
piston
swash plate
guide
reciprocating piston
ball
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.)
Granted
Application number
EP96810373A
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German (de)
French (fr)
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EP0752530B1 (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
TES WANKEL TECHNISCHE FORSCHUNGS- und ENTWICKLUNGSSTELLE LINDAU GmbH
Daimler Benz AG
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Publication of EP0752530A1 publication Critical patent/EP0752530A1/en
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Publication of EP0752530B1 publication Critical patent/EP0752530B1/en
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    • 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 mechanism, wherein a first part of the swash plate is in drive connection with the machine shaft via a swivel joint and its second part is in drive connection with the piston, and the wobble movement is transmitted from the first to the second swash plate part via a rotary bearing.
  • Reciprocating machines of this type are widely known from the patent literature, e.g. by US-A-5,205,718 or DE-A-42 34 989. Since the wobble movement used for driving the piston has components in the direction of the piston movement as well as components directed radially thereto, it was previously considered necessary to have the wobble movement on To transmit the circumferential area of the swash plate to the pistons guided in a cylinder by connecting rods mounted on both sides via ball heads. The minimum length of the connecting rods determined by the maximum inclination of the swash plate and their arrangement between the swash plate and the pistons leads to a relatively large overall length of the reciprocating piston machine. The size of the reciprocating piston machine has a particularly disadvantageous effect if it is to be arranged in the engine compartment as a compressor for a vehicle air conditioning system.
  • the invention has for its object to find a reciprocating piston machine of the type mentioned, which has a small size, which can be manufactured with less effort or less expensive and which has low friction losses in the transmission of the drive from the swash plate to the piston.
  • connecting rods and two ball joint bearings are avoided on each connecting rod.
  • the combination of a ball head / transverse guide results in a significantly smaller contact area for the drive transmission compared to the ball joints previously used. so that there are considerably lower frictional resistances.
  • the invention also shows that the pistons arranged next to one another in the circumferential direction of the machine enclose the swash plate and the axial overall length of the machine is shortened accordingly.
  • the reciprocating piston machine 1 has, for example, seven pistons 2 which are arranged next to one another in the circumferential direction of the machine.
  • the swash plate 3 has a disk part 5 rotating with the machine shaft 4 and a disk part 6 which is in drive connection with the pistons 2 and consequently does not rotate.
  • a rotary bearing 9 equipped with bearing balls 7, 8 is provided between the two disk parts 5, 6, the axial and absorbs radial forces to transmit the wobble movement serving the piston drive.
  • the connection between the machine shaft 4 and the rotating disk part 5 takes place by means of a driver pin 10, which engages in a recess 11 of a driver body 12 formed laterally on the rotating disk part 5, which enables the angular adjustment of the swash plate 3.
  • the swashplate carries a spherical body 13 which is encompassed by a correspondingly shaped spherical surface 14 of the rotating disk part 5.
  • the force for the angular adjustment of the swash plate 3 results from the sum of the pressures acting against each other on both sides of the pistons 2, so that this force is dependent on the pressure in the drive chamber 15.
  • a flow connection can be provided with an external compressed gas flow, which is present when the machine is used as a compressor.
  • This connection can have channels 16 which lead to the sealing and storage space 17 provided for the machine shaft 4 and then into the drive space 15, so that cooling is also achieved.
  • the bottom dead center of the piston movement changes, while the top dead center remains unchanged or largely remains unchanged.
  • each connection between a location of the swash plate 3 and a piston 2 has only one ball joint 20, in that the type of mounting of the ball head 21 permits its movement transversely to the axis of the piston 2 or radially to the swash plate 3.
  • the piston 2 has a piston shaft 22, which rigidly connects its piston head 24, which carries the piston rings 23, to a guide head 26 sliding in the cylinder bore 25.
  • the swash plate 3 has for each piston 2 a short ball pin 27 which extends radially away from it and which engages with the ball head 21 in a transverse bore 28 of the guide head 26.
  • the ball head 21 is preferably surrounded by a slide ring 29 with a spherical inner surface 30, based on the outer rings of radial spherical plain bearings.
  • the engagement of the ball head 21 in the slide ring 29 causes it to slide in the transverse bore 28 of the guide head 26 during the radial movement of the ball head 21.
  • FIG. 5 illustrates that the ball joint 20 'between a piston 2 and the swash plate 3 can also be carried out in the reverse arrangement to that described above, in that a ball head 21' is rigidly fastened to the guide head 26 'of the piston 2 and receives it Cross bore 28 'extends radially into the swash plate 3.
  • the ball head 21 ' can be of a sliding sleeve, not shown, may be included.
  • an anti-rotation device is provided on at least one piston 2, so that rotation is prevented by the articulated connection between the swash plate 3 and the piston 2.
  • a guide pin 33 provided with two flats 32 extends through the wall 34 of the machine housing 35 and engages in an axially parallel guide groove 36 of the piston, so that a sliding contact is present between the flats 32 and the side walls of the guide groove 36.
  • the shaft 22 of the piston 2 in question is provided with a suitable cross section, which deviates from the slim cross section shown in the lower part of FIG.
  • each piston 2 is guided against rotation about its axis by a guide pin engaging in a guide groove 36.
  • the guide pin 33 is enclosed with a certain play between the side walls of the guide groove 36. Since the seven pistons 2 perform a phase-shifting, oscillating, limited rotary movement, in each wobble position of the swash plate 3, that piston assures the rotation of the disk 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 is. Consequently, the guide contact changes in the circumferential direction of the machine from one piston 2 to the other, so that the stress caused by 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)

Abstract

The drive connection between the second part (6) of the swash plate (3) and the piston (2) takes place via a ball head (21) which engages in a guide running transversely to the axis of the piston. The ball heads are rigidly attached to the circumference of the swash plate and the ball guide extends transversely through the drive side end (26) of the piston. The rotation of the piston about its longitudinal axis is closely restricted.

Description

Die Erfindung betrifft eine Hubkolbenmaschine mit Taumelscheibengetriebe, wobei ein erster Teil der Taumelscheibe über ein Schwenkgelenk mit der Maschinenwelle und ihr zweiter Teil mit den Kolben in Antriebsverbindung steht und die Taumelbewegung über eine Drehlagerung vom ersten auf den zweiten Taumelscheibenteil übertragen wird.The invention relates to a reciprocating piston machine with a swash plate mechanism, wherein a first part of the swash plate is in drive connection with the machine shaft via a swivel joint and its second part is in drive connection with the piston, and the wobble movement is transmitted from the first to the second swash plate part via a rotary bearing.

Hubkolbenmaschinen dieser Art sind durch die Patentliteratur vielfach bekannt, wie z.B. durch die US-A-5,205,718 oder die DE-A-42 34 989. Da die für den Antrieb der Kolben ausgenutzte Taumelbewegung neben einer Komponente in Richtung der Kolbenbewegung auch radial dazu gerichtete Komponenten hat, wurde es bisher für erforderlich angesehen, die Taumelbewegung am Umfangsbereich der Taumelscheibe durch beidseitig über Kugelköpfe gelagerte Pleuelstangen auf die in einem Zylinder geführten Kolben zu übertragen. Die durch die maximale Schrägstellung der Taumelscheibe mitbestimmte Mindestlänge der Pleuelstangen und ihre Anordnung zwischen der Taumelscheibe und den Kolben führt zu einer relativ grossen Gesamtlänge der Hubkolbenmaschine. Die Grösse der Hubkolbenmaschine wirkt sich besonders nachteilig aus, wenn sie als Kompressor einer Fahrzeug-Klimaanlage im Motorraum angeordnet werden soll.Reciprocating machines of this type are widely known from the patent literature, e.g. by US-A-5,205,718 or DE-A-42 34 989. Since the wobble movement used for driving the piston has components in the direction of the piston movement as well as components directed radially thereto, it was previously considered necessary to have the wobble movement on To transmit the circumferential area of the swash plate to the pistons guided in a cylinder by connecting rods mounted on both sides via ball heads. The minimum length of the connecting rods determined by the maximum inclination of the swash plate and their arrangement between the swash plate and the pistons leads to a relatively large overall length of the reciprocating piston machine. The size of the reciprocating piston machine has a particularly disadvantageous effect if it is to be arranged in the engine compartment as a compressor for a vehicle air conditioning system.

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 to find a reciprocating piston machine of the type mentioned, which has a small size, which can be manufactured with less effort or less expensive and which has low friction losses in the transmission of the drive from the swash plate to the piston.

Die Lösung dieser Aufgabe erfolgt erfindungsgemäss dadurch, dass die Antriebsverbindung zwischen dem zweiten Teil der Taumelscheibe und den Kolben jeweils über einen Kugelkopf erfolgt, der in eine quer zur Kolbenachse verlaufende Führung eingreift.This object is achieved according to the invention in that the drive connection between the second part of the swash plate and the pistons takes place in each case via a ball head which engages in a guide which runs transversely to the piston axis.

Im Gegensatz zum vorbekannten Stand der Technik werden somit Pleuelstangen und jeweils zwei Kugelgelenklager an jeder Pleuelstange vermieden. Durch die Kombination Kugelkopf/Querführung ergibt sich eine im Vergleich zu den bisher verwendeten Kugelgelenken eine wesentlich kleinere Kontaktfläche der Antriebsübertragung. so dass erheblich geringere Reibungswiderstände vorhanden sind. Aufgrund der Erfindung ergibt sich auch, dass die in Umfangsrichtung der Maschine nebeneinander angeordneten Kolben die Taumelscheibe umschliessen und die axiale Baulänge der Maschine entsprechend verkürzt ist.In contrast to the prior art, connecting rods and two ball joint bearings are avoided on each connecting rod. The combination of a ball head / transverse guide results in a significantly smaller contact area for the drive transmission compared to the ball joints previously used. so that there are considerably lower frictional resistances. The invention also shows that the pistons arranged next to one another in the circumferential direction of the machine enclose the swash plate and the axial overall length of the machine is shortened accordingly.

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 of 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,
Fig. 3
2 shows an enlarged representation of an area in FIG. 2,
Fig. 4
a sectional view corresponding to Figure 2 of an embodiment in which each piston has an anti-rotation and
Fig. 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 a swash plate gear is known from the specialist literature, such as 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 machine 1 has, for example, seven pistons 2 which are arranged next to one another in the circumferential direction of the machine. The swash plate 3 has a disk part 5 rotating with the machine shaft 4 and a disk part 6 which is in drive connection with the pistons 2 and consequently does not rotate. For this purpose, a rotary bearing 9 equipped with bearing balls 7, 8 is provided between the two disk parts 5, 6, the axial and absorbs radial forces to transmit the wobble movement serving the piston drive.

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 disk part 5 takes place by means of a driver pin 10, which engages in a recess 11 of a driver body 12 formed laterally on the rotating disk part 5, which enables the angular adjustment of the swash plate 3. For the swiveling disk 3 to be supported on the machine shaft 4, the swashplate carries a spherical body 13 which is encompassed by a correspondingly shaped spherical surface 14 of the rotating disk part 5.

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 pressures acting against each other on both sides of the pistons 2, so that this force is dependent on the pressure in the drive chamber 15. To regulate this pressure, a flow connection can be provided with an external compressed gas flow, which is present when the machine is used as a compressor. This connection can have channels 16 which lead to the sealing and storage space 17 provided for the machine shaft 4 and then into the drive space 15, so that cooling is also achieved. Depending on the inclination of the swash plate 3, the bottom dead center of the piston movement changes, while the top dead center remains unchanged or largely remains unchanged. The higher the pressure on the underside of the pistons 2 or in the drive chamber 15 relative to the pressure on the top of the pistons 2 or on the suction side of the compressor, the smaller the stroke length of the pistons 2 and thus the delivery capacity 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 2 are connected to the circumference of the swash plate 3 in order to carry out their lifting movement. In contrast to previously known constructions, each connection between a location of the swash plate 3 and a piston 2 has only one ball joint 20, in that the type of mounting of the ball head 21 permits its movement transversely to the axis of the piston 2 or radially to the swash plate 3. For this purpose, the piston 2 has a piston shaft 22, which rigidly connects its piston head 24, which carries the piston rings 23, to a guide head 26 sliding in the cylinder bore 25.

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 3 has for each piston 2 a short ball pin 27 which extends radially away from it and which engages with the ball head 21 in a transverse bore 28 of the guide head 26.

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.In order to avoid line contact between the ball head 21 and a cylindrical transverse bore 28, which leads to excessive pressure loads, the ball head 21 is preferably surrounded by a slide ring 29 with a spherical inner surface 30, based on the outer rings of radial spherical plain bearings. The engagement of the ball head 21 in the slide ring 29 causes it to slide in the transverse bore 28 of the guide head 26 during the radial movement of the ball head 21.

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 exemplary embodiment in FIG. 5 illustrates that the ball joint 20 'between a piston 2 and the swash plate 3 can also be carried out in the reverse arrangement to that described above, in that a ball head 21' is rigidly fastened to the guide head 26 'of the piston 2 and receives it Cross bore 28 'extends radially into the swash plate 3. In this embodiment too, the ball head 21 'can be 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.In order to prevent the disk part 6 of the swash plate 3 from rotating with the frictional forces of the bearing 9, an anti-rotation device is provided on at least one piston 2, so that rotation is prevented by the articulated connection between the swash plate 3 and the piston 2. For this purpose, a guide pin 33 provided with two flats 32 extends through the wall 34 of the machine housing 35 and engages in an axially parallel guide groove 36 of the piston, so that a sliding contact is present between the flats 32 and the side walls of the guide groove 36.

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 of the piston 2 in question is provided with a suitable cross section, which deviates from the slim cross section shown in the lower part of FIG.

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 embodiment in which each piston 2 is guided against rotation about its axis by a guide pin engaging in a guide groove 36. The guide pin 33 is enclosed with a certain play between the side walls of the guide groove 36. Since the seven pistons 2 perform a phase-shifting, oscillating, limited rotary movement, in each wobble position of the swash plate 3, that piston assures the rotation of the disk 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 is. Consequently, the guide contact changes in the circumferential direction of the machine from one piston 2 to the other, so that the stress caused by the guide is distributed accordingly.

Claims (6)

Hubkolbenmaschine mit Taumelscheibengetriebe, wobei ein erster Teil (5) der Taumelscheibe (3) über ein Schwenkgelenk (10,11;13,14) mit der Maschinenwelle und ihr zweiter Teil (6) mit den Kolben (2) in Antriebsverbindung steht und die Taumelbewegung über eine Drehlagerung (9) vom ersten auf den zweiten Taumelscheibenteil übertragen wird, dadurch gekennzeichnet, dass die Antriebsverbindung zwischen dem zweiten Teil (6) der Taumelscheibe (3) und den Kolben (2) jeweils über einen Kugelkopf (21,21') erfolgt, der in eine quer zur Kolbenachse verlaufende Führung (28,28') eingreift.Reciprocating piston machine with swash plate gear, a first part (5) of the swash plate (3) via a swivel joint (10, 11; 13, 14) with the machine shaft and its second part (6) with the piston (2) in drive connection and the wobble movement Is transmitted from the first to the second swash plate part via a rotary bearing (9), characterized in that the drive connection between the second part (6) of the swash plate (3) and the piston (2) takes place in each case via a ball head (21, 21 ') which engages in a guide (28, 28 ') running transversely to the piston axis. Hubkolbenmaschine nach Anspruch 1, dadurch gekennzeichnet, dass die Kugelköpfe (21) am Umfang des zweiten Taumelscheibenteils (6) starr befestigt sind und die Kugelführung (28) sich quer durch das antriebsseitige Ende (26) des Kolbens (2) erstreckt.Reciprocating piston machine according to claim 1, characterized in that the ball heads (21) are rigidly attached to the circumference of the second swash plate part (6) and the ball guide (28) extends transversely through the drive-side end (26) of the piston (2). Hubkolbenmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass in mindestens einen der Kolben (2) ein Führungselement (33) eingreift, so dass die Verdrehung des Kolbens (2) um seine Längsachse zumindest eng begrenzt ist.Reciprocating piston machine according to claim 1 or 2, characterized in that a guide element (33) engages in at least one of the pistons (2), so that the rotation of the piston (2) about its longitudinal axis is at least narrowly limited. Hubkolbenmaschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass jeder der Kolben (2) eine Verdrehsicherung (33,36) aufweist.Reciprocating piston machine according to one of claims 1 to 3, characterized in that each of the pistons (2) has an anti-rotation device (33, 36). Hubkolbenmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der Kugelkopf (21) von einem Gleitring (29) mit kugelförmiger Innenfläche 30 umfasst ist, der in einer Führungsbohrung (28) verschiebbar gehalten ist.Reciprocating piston machine according to one of claims 1 to 4, characterized in that the ball head (21) is surrounded by a slide ring (29) with a spherical inner surface 30 which is held displaceably in a guide bore (28). Hubkolbenmaschine nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Kolben (2) einen Dichtringe (23) tragenden Kolbenkopf (24) und einen Führungskopf (26) aufweist, die durch einen Kolbenschaft (22) miteinander verbunden sind.Reciprocating piston machine according to one of claims 1 to 5, characterized in that the piston (2) has a piston head (24) carrying sealing rings (23) and a guide head (26) which are connected to one another by 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
CH01957/95A CH691272A5 (en) 1995-07-05 1995-07-05 Reciprocating engine with swashplate mechanism.
CH195795 1995-07-05

Publications (2)

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

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Application Number Title Priority Date Filing Date
EP96810373A Expired - Lifetime EP0752530B1 (en) 1995-07-05 1996-06-07 Reciprocating piston machine with swash plate mechanism

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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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EP1577552A2 (en) * 2004-03-18 2005-09-21 Haldex Brake Corporation Fixed angle swash plate compressor
EP3269978A1 (en) * 2012-02-01 2018-01-17 YourBrook Energy Systems Ltd. Hydroelectric power system and pump

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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
US6860188B2 (en) * 2003-06-20 2005-03-01 Visteon Global Technologies, Inc. Variable displacement compressor hinge mechanism
JP4829761B2 (en) * 2006-12-05 2011-12-07 サンデン株式会社 Swing plate type variable capacity compressor
JP5164563B2 (en) * 2007-12-28 2013-03-21 サンデン株式会社 Swing plate type variable capacity compressor
US9816377B2 (en) * 2014-09-24 2017-11-14 Eaton Corporation Hydraulic axial-piston device with features to enhance efficiency and power density
ES2895933T3 (en) * 2016-07-25 2022-02-23 Caire Inc Swash plate compressor and oxygen concentrator using the same
CN112392719B (en) * 2020-11-20 2022-04-19 四川省机械技术服务中心有限责任公司 High-efficient compact plunger pump plunger device
CN112983772B (en) * 2021-03-30 2022-08-19 中航力源液压股份有限公司 Axial plunger pump return device capable of reducing wear of sliding shoe

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EP1577552A2 (en) * 2004-03-18 2005-09-21 Haldex Brake Corporation Fixed angle swash plate compressor
EP1577552A3 (en) * 2004-03-18 2006-12-13 Haldex Brake Corporation Fixed angle swash plate compressor
EP3269978A1 (en) * 2012-02-01 2018-01-17 YourBrook Energy Systems Ltd. Hydroelectric power system and pump
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Also Published As

Publication number Publication date
EP0752530B1 (en) 2002-03-27
JPH0925872A (en) 1997-01-28
US5752413A (en) 1998-05-19
JP3373733B2 (en) 2003-02-04
DE59608940D1 (en) 2002-05-02
CH691272A5 (en) 2001-06-15

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