EP0964997A1 - Piston engine with a pivoting disk transmission - Google Patents

Piston engine with a pivoting disk transmission

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Publication number
EP0964997A1
EP0964997A1 EP98949199A EP98949199A EP0964997A1 EP 0964997 A1 EP0964997 A1 EP 0964997A1 EP 98949199 A EP98949199 A EP 98949199A EP 98949199 A EP98949199 A EP 98949199A EP 0964997 A1 EP0964997 A1 EP 0964997A1
Authority
EP
European Patent Office
Prior art keywords
driver
reciprocating piston
sliding body
machine shaft
machine according
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
EP98949199A
Other languages
German (de)
French (fr)
Other versions
EP0964997B1 (en
Inventor
Peter Kuhn
Roland Cäsar
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.)
Obrist Engineering GmbH
Mercedes Benz Group AG
Original Assignee
Obrist Engineering GmbH
Daimler Benz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Obrist Engineering GmbH, Daimler Benz AG filed Critical Obrist Engineering GmbH
Publication of EP0964997A1 publication Critical patent/EP0964997A1/en
Application granted granted Critical
Publication of EP0964997B1 publication Critical patent/EP0964997B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1072—Pivot mechanisms

Definitions

  • the invention relates to a reciprocating piston machine with a swivel disk which is adjustable in its inclination to the machine shaft and is driven by the machine shaft, in that it is connected in an articulated manner both to a sliding body guided axially on the machine shaft and at a distance from the machine shaft to a driver transmitting the driving force.
  • the pistons each have a joint arrangement on which the swivel plate is in sliding engagement.
  • a reciprocating piston machine of this type is known from DE-A-44 11 926 (JP-Note No. 081944).
  • the driver is in two parts, a first driver part fastened to the machine shaft being arranged at a considerable distance from the swivel disk and a second driver part engaging in the first articulated manner forming a lateral extension of the swivel disk.
  • the disadvantage of this design is that it significantly determines the minimum axial length of the machine.
  • the swivel disk having a thickened hub part has a relatively large moment of inertia due to its lateral extension, with a center of gravity far away from the axis of rotation, so that a sudden change in the rotational speed with corresponding inertia leads to an inclination adjustment of the swivel disk.
  • the invention has for its object to find a reciprocating piston machine of the type mentioned, which allows a particularly compact design with little effort for its manufacture, which opposes an adjustment movement of the swivel plate, low inertia and frictional forces and which prevents harmful spaces, exact compliance with internal dead center position of the reciprocating pistons guaranteed.
  • This object is achieved according to the invention in that the swivel disk has the shape of an annular disk and, at one point on its circumference, has an at least radially inwardly open engagement space into which the head of a driver firmly connected to the machine shaft engages.
  • Fig.l shows an axial section of an embodiment of the reciprocating piston machine, wherein the annular disc has its greatest inclination
  • FIG. 2 shows a representation corresponding to FIG. 1 with the smallest inclination of the ring disk.
  • FIG. 3 shows a separate illustration of the annular disk with its driver, corresponding to part of FIG. 2,
  • 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 and are guided in cylinder bores 3 of the machine housing.
  • the lifting movement of the pistons 2 takes place through the engagement of an annular disk 6, which extends obliquely to the machine shaft 5, into an engagement chamber 7, which is provided adjacent to the closed cavity 8 of the piston 2.
  • an annular disk 6, which extends obliquely to the machine shaft 5
  • an engagement chamber 7 which is provided adjacent to the closed cavity 8 of the piston 2.
  • the drive transmission from the machine shaft 5 to the ring disk 6 takes place by means of a driving pin 13 fastened in the machine shaft 5, the spherical head 15 of which engages, for example, in a radial bore 16 of the ring disk 6.
  • the position of the driver head 15 is selected such that its center 17 coincides with that of the ball of the ball segments 11, 12.
  • this center lies on a circular line that connects the geometric axes of the seven pistons to one another and also on a circular line that connects the center points of the spherical shape of the joint bodies 11, 12 of the pistons 2.
  • the head shape of the free driver end enables the inclination of the ring disk 6 to be changed by the driver head 15 forming a bearing body for the pivoting movement of the ring disk 6 which changes the stroke width of the pistons 2.
  • the shape of the engagement space 16 and / or the head 15 of the driver 13 can also be selected differently to achieve a different type of kinematics.
  • a further prerequisite for pivoting the ring disk 6 is the displaceability of its bearing axis 20 in the direction of the machine shaft 5.
  • the bearing axis 20 is formed by two bearing pins 22, 23 mounted on both sides of a sliding sleeve 21, which are also in radial bores 24, 25 of the ring disk 6 are stored.
  • the sliding sleeve 21 preferably has bearing sleeves 26, 27 on both sides, which bridge the annular space 28 between the sliding sleeve 21 and the annular disk 6 in a spoke-like manner.
  • the force for the angular adjustment of the annular disc 6 and thus for a control of the machine 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 33.
  • a flow connection to an external compressed gas source can be provided to regulate this pressure. The higher the pressure on the drive chamber side of the pistons 2 or in the drive chamber 33 relative to the pressure on the opposite side of the pistons 2, the smaller the stroke length of the pistons 2 and thus the delivery rate of the machine.
  • the setting of the position of the sliding sleeve 21 and thus the stroke length of the pistons for regulating the delivery capacity of the machine can also be carried out by at least one spring 34, 35 which interacts with the sliding sleeve 21.
  • the sliding sleeve 21 is preferably enclosed between two helical springs 34, 35 which are arranged on the circumference of the machine shaft 5.
  • the position of the sliding sleeve 21, which is decisive for the delivery capacity, is also determined by inertial forces acting on the ring disk 6, in that the ring disk 6 rises with increasing rotational speed in the direction of the position according to FIG. 2, corresponding to a reduction in the stroke length of the pistons 2 and thus the delivery rate.
  • This mode of operation is significantly favored on the basis of the invention, since the mass of the annular disk 6 is arranged peripherally outwards in comparison to previously known swivel disks, by avoiding a massive design and avoiding a laterally formed driver.
  • Swivel plate 6 results from its limited to the ring shape

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Transmission Devices (AREA)

Abstract

The piston engine has an annular pivoting disk (6) driven by an engine shaft (5) and is adjustably inclined thereto. Said disk drives adjacent pistons (2) arranged in a peripheral direction and is connected in an articulated manner to a sliding sleeve (21) which is axially guided on the engine shaft (5) and is also connected to a driver (13) which transmits driving force and is located at a distance from said engine shaft (5). The annular shape of the pivoting disk (6) is advantageous in terms of dynamics and production. It enables the driver (13) to engage in a radial bore hole (16) of the pivoting disk in an articulated manner, thus saving space.

Description

Hubkolbenmaschine mit Schwenkscheibengetriebe Reciprocating piston machine with swivel plate gear
Die Erfindung betrifft eine Hubkolbenmaschine mit einer in ihrer Nei- gung zur Mascliinenwelle verstellbaren, von der Maschinenwelle angetriebenen Schwenkscheibe, indem sie sowohl mit einem auf der Maschjnenwelle axial geführten Schiebekörper als auch mit Abstand von der Maschinenwelle mit einem die Antriebskraft übertragenden Mitnehmer gelenkig verbunden ist, wobei die Kolben jeweils eine Ge- lenkanordnung aufweisen, an der die Schwenkscheibe in Gleiteingriff steht.The invention relates to a reciprocating piston machine with a swivel disk which is adjustable in its inclination to the machine shaft and is driven by the machine shaft, in that it is connected in an articulated manner both to a sliding body guided axially on the machine shaft and at a distance from the machine shaft to a driver transmitting the driving force. wherein the pistons each have a joint arrangement on which the swivel plate is in sliding engagement.
Eine Hubkolbenmaschine dieser Art ist bekannt durch die DE-A-44 11 926 (JP-Anm. Nr. 081944). Bei dieser Maschine ist der Mitnehmer zweiteilig, wobei ein an der Maschinenwelle befestigter erster Mitnehmerteil mit erheblichem Abst.and neben der Schwenkscheibe angeordnet ist und ein zweiter, in den ersten gelenkig eingreifender Mitnehmerteil einen seitlichen Fortsatz der Schwenkscheibe bildet. Diese Bauweise hat den Nachteil, dass sie die axiale Mindestlänge der Ma- schine wesentlich mitbestimmt. Ausserdem hat die einen verdickten Nabenteil aufweisende Schwenkscheibe durch ihren seitlichen Fortsatz ein verhältnismässig grosses Trägheitsmoment mit einem erheblich von der Drehachse entfernten Schwerpunkt, so dass eine plötzliche Veränderung der Drehgeschwindigkeit mit entsprechender Trägheit zu einer Neigungsverstellung der Schwenkscheibe fuhrt.A reciprocating piston machine of this type is known from DE-A-44 11 926 (JP-Note No. 081944). In this machine, the driver is in two parts, a first driver part fastened to the machine shaft being arranged at a considerable distance from the swivel disk and a second driver part engaging in the first articulated manner forming a lateral extension of the swivel disk. The disadvantage of this design is that it significantly determines the minimum axial length of the machine. In addition, the swivel disk having a thickened hub part has a relatively large moment of inertia due to its lateral extension, with a center of gravity far away from the axis of rotation, so that a sudden change in the rotational speed with corresponding inertia leads to an inclination adjustment of the swivel disk.
Der Erfindung liegt die Aufgabe zugrunde, eine Hubkolbenmaschine der eingangs genannten Art zu finden, die bei geringem Aufwand für ihre Herstellung eine besonders kompakte Bauweise zulässt, die einer Verstellbewegung der Schwenkscheibe geringe Trägheits- und Reibungskräfte entgegensetzt und die eine schädliche Räume verhindernde, exakte Einhaltung der inneren Totpunktposition der Hubkolben gewährleistet. Die Lösung dieser Aufgabe erfolgt erfindungsgemäss dadurch, dass die Schwenkscheibe die Form einer Ringscheibe hat und an einer Stelle ihres Umfanges einen zumindest radial nach innen offenen Eingriffsraum aufweist, in den der Kopf eines mit der Maschinenwelle fest verbundenen Mitnehmers eingreift.The invention has for its object to find a reciprocating piston machine of the type mentioned, which allows a particularly compact design with little effort for its manufacture, which opposes an adjustment movement of the swivel plate, low inertia and frictional forces and which prevents harmful spaces, exact compliance with internal dead center position of the reciprocating pistons guaranteed. This object is achieved according to the invention in that the swivel disk has the shape of an annular disk and, at one point on its circumference, has an at least radially inwardly open engagement space into which the head of a driver firmly connected to the machine shaft engages.
Auf diese Weise wird ein seitlich angeordneter Mitnehmer, der grösse- re Trägheitskräfte, eine grössere Baulänge und einen grösseren Herstellungsaufwand zur Folge hat, vermieden.In this way, a laterally arranged driver is avoided, which results in greater inertial forces , a greater overall length and a greater manufacturing outlay.
Vorteilhafte Ausfuhrungsformen der Erfindung und ihre Vorteile werden durch die folgende Beschreibung .anhand der Zeichnungen deutlich. Es zeigt:Advantageous embodiments of the invention and their advantages will become clear from the following description with reference to the drawings. It shows:
Fig.l einen Axialschnitt einer Ausfuhrungsform der Hubkolbenmaschine, wobei die Ringscheibe ihre grösste Neigung aufweist,Fig.l shows an axial section of an embodiment of the reciprocating piston machine, wherein the annular disc has its greatest inclination,
Fig.2 eine Darstellung entsprechend Fig.l bei kleinster Neigung der Ringscheibe.2 shows a representation corresponding to FIG. 1 with the smallest inclination of the ring disk.
Fig.3 eine separate Darstellung der Ringscheibe mit ihrem Mitnehmer, entsprechend einem Teil der Fig.2,3 shows a separate illustration of the annular disk with its driver, corresponding to part of FIG. 2,
Fig.4 einen Querschnitt entlang der Linie IV-IV der Fig.3 und4 shows a cross section along the line IV-IV of Figure 3 and
Fig.5 eine perspektivische D.arstellung der Anordnung Fig.3 und 4.5 shows a perspective view of the arrangement of FIGS. 3 and 4.
Die Hubkolbenmaschine 1 hat beispielsweise sieben Kolben 2, die in Umf.angsrichtung der Maschine nebeneinander angeordnet sind und in Zylinderbohrungen 3 des Maschinengehäuses geführt sind. Die Hubbewegung der Kolben 2 erfolgt durch den Eingriff einer zur Maschinenwelle 5 schräg verlaufenden Ringscheibe 6 in eine Eingriffskammer 7, die angrenzend an den geschlossenen Hohlraum 8 des Kolbens 2 vorgesehen ist. Für einen im wesentlichen spielfreien Gleiteingriff in jeder Schräglage der Ringscheibe 6 sind zwischen ihr und der kugel- förmig gekrümmten Innenwand 10 der Eingriffskammer 7 beidseitig Kugelsegmente 11,12 vorgesehen, so dass die Schrägscheibe 6 bei ihrem Umlauf zwischen ihnen gleitet.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 and are guided in cylinder bores 3 of the machine housing. The lifting movement of the pistons 2 takes place through the engagement of an annular disk 6, which extends obliquely to the machine shaft 5, into an engagement chamber 7, which is provided adjacent to the closed cavity 8 of the piston 2. For an essentially play-free sliding engagement in any inclined position of the annular disc 6, between it and the spherical spherical segments 11, 12 are provided on both sides, so that the swash plate 6 slides between them as it rotates.
Die Antriebsübertragung von der Maschinenwelle 5 zu der Ringscheibe 6 erfolgt durch einen in der Maschinenwelle 5 befestigten Mitnehmerbolzen 13, dessen beispielsweise kugelförmiger Kopf 15 in eine Radialbohrung 16 der Ringscheibe 6 eingreift. Dabei ist die Position des Mitnehmerkopfes 15 so gewählt, dass sein Mittelpunkt 17 mit demje- nigen der Kugel der Kugelsegmente 11,12 übereinstimmt. Ausserdem liegt dieser Mittelpunkt auf einer Kreislinie, die die geometrischen Achsen der sieben Kolben miteinander verbindet und weiterhin auf einer Kreislinie, die die Mittelpunkte der Kugelform der Gelenkkörper 11,12 der Kolben 2 verbindet. Auf diese Weise ist die im oberen Be- reich der Darstellungen der Fig.1 und 2 sichtbare Totpunktposition der Kolben 2 exakt bestimmt und ein minimaler schädlicher Raum gewährleistet. Die Kopfform des freien Mitnehmerendes ermöglicht die Veränderung der Neigung der Ringscheibe 6, indem der Mitnehmerkopf 15 einen Lagerkörper für die die Hubweite der Kolben 2 verändernde Schwenkbewegung der Ringscheibe 6 bildet. Die Form des Eingriffsraumes 16 und/oder des Kopfes 15 des Mitnehmers 13 können zur Erzielung einer andersartigen Kinematik auch anders gewählt werden.The drive transmission from the machine shaft 5 to the ring disk 6 takes place by means of a driving pin 13 fastened in the machine shaft 5, the spherical head 15 of which engages, for example, in a radial bore 16 of the ring disk 6. The position of the driver head 15 is selected such that its center 17 coincides with that of the ball of the ball segments 11, 12. In addition, this center lies on a circular line that connects the geometric axes of the seven pistons to one another and also on a circular line that connects the center points of the spherical shape of the joint bodies 11, 12 of the pistons 2. In this way, the dead center position of the pistons 2, which is visible in the upper area of the illustrations in FIGS. 1 and 2, is exactly determined and a minimum of harmful space is ensured. The head shape of the free driver end enables the inclination of the ring disk 6 to be changed by the driver head 15 forming a bearing body for the pivoting movement of the ring disk 6 which changes the stroke width of the pistons 2. The shape of the engagement space 16 and / or the head 15 of the driver 13 can also be selected differently to achieve a different type of kinematics.
Weitere Voraussetzung für ein Verschwenken der Ringscheibe 6 ist die Verschiebbarkeit ihrer Lagerachse 20 in Richtung der Maschinenwelle 5. Hierzu ist die Lagerachse 20 durch zwei gleichachsig beidseitig einer Schiebehülse 21 gelagerte Lagerbolzen 22,23 gebildet, die ausserdem in radialen Bohrungen 24,25 der Ringscheibe 6 gelagert sind. Die Schiebehülse 21 hat hierzu vorzugsweise beidseitig Lagerhülsen 26,27, die den Ringraum 28 zwischen der Schiebehülse 21 und der Ringscheibe 6 speichenartig überbrücken. Die Begrenzung der Verschiebbarkeit der Lagerachse 20 und damit die maximale Schrägstellung der Ringscheibe 6 ergibt sich durch den Mitnehmerbolzen 13, indem dieser ein in der Schiebehülse 21 vorgesehenes Langloch 3 durchdringt, so dass die Schiebehülse 21 an den Enden des Langloches 30 Anschläge findet.A further prerequisite for pivoting the ring disk 6 is the displaceability of its bearing axis 20 in the direction of the machine shaft 5. For this purpose, the bearing axis 20 is formed by two bearing pins 22, 23 mounted on both sides of a sliding sleeve 21, which are also in radial bores 24, 25 of the ring disk 6 are stored. For this purpose, the sliding sleeve 21 preferably has bearing sleeves 26, 27 on both sides, which bridge the annular space 28 between the sliding sleeve 21 and the annular disk 6 in a spoke-like manner. The limitation of the displaceability of the bearing axis 20 and thus the maximum inclination of the washer 6 results from the driving pin 13 by penetrating an elongated hole 3 provided in the sliding sleeve 21, so that the sliding sleeve 21 finds 30 stops at the ends of the elongated hole.
Die Kraft für die Winkelverstellung der Ringscheibe 6 und damit für eine Regelung der Maschine, ergibt sich aus der Summe der jeweils beidseitig der Kolben 2 gegenein.ander wirkenden Drücke, so dass diese Kraft vom Druck im Triebraum 33 abhängig ist. Für die Regelung dieses Druckes kann eine Strömungsverbindung mit einer äusseren Druckgasquelle vorgesehen sein. Je höher der Druck an der Triebraum- seite der Kolben 2 bzw. im Triebraum 33 relativ zum Druck auf der gegenüberliegender Seite der Kolben 2, um so kleiner wird die Hubweite der Kolben 2 und damit die Förderleistung der Maschine.The force for the angular adjustment of the annular disc 6 and thus for a control of the machine 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 33. A flow connection to an external compressed gas source can be provided to regulate this pressure. The higher the pressure on the drive chamber side of the pistons 2 or in the drive chamber 33 relative to the pressure on the opposite side of the pistons 2, the smaller the stroke length of the pistons 2 and thus the delivery rate of the machine.
Die Einstellung der Position der Schiebehülse 21 und damit der Hub- weite der Kolben zur Regelung der Förderleistung der Maschine kann ausserdem durch mindestens eine mit der Schiebehülse 21 zusammenwirkende Feder 34,35 erfolgen. Vorzugsweise ist die Schiebehülse 21 zwischen zwei Schraubenfedern 34,35 eingeschlossen, die auf dem Umfang der Maschinenwelle 5 angeordnet sind.The setting of the position of the sliding sleeve 21 and thus the stroke length of the pistons for regulating the delivery capacity of the machine can also be carried out by at least one spring 34, 35 which interacts with the sliding sleeve 21. The sliding sleeve 21 is preferably enclosed between two helical springs 34, 35 which are arranged on the circumference of the machine shaft 5.
Weiterhin wird die für die Förderleistung massgebliche Position der Schiebehülse 21 durch auf die Ringscheibe 6 einwirkende Trägheitskräfte mitbestimmt, indem sich die Ringscheibe 6 bei steigender Drehgeschwindigkeit in Richtung zu der Position nach Fig.2 aufrichtet, ent- sprechend einer Verringerung der Hubweite der Kolben 2 und damit der Förderleistung. Diese Wirkungsweise wird aufgrund der Erfindung wesentlich begünstigt, da die Masse der Ringscheibe 6 im Vergleich zu vorbekannten Schwenkscheiben, durch Vermeidung einer massiven Ausführung und Vermeidung eines seitlich angeformten Mitnehmers, peripher nach aussen angeordnet ist.Furthermore, the position of the sliding sleeve 21, which is decisive for the delivery capacity, is also determined by inertial forces acting on the ring disk 6, in that the ring disk 6 rises with increasing rotational speed in the direction of the position according to FIG. 2, corresponding to a reduction in the stroke length of the pistons 2 and thus the delivery rate. This mode of operation is significantly favored on the basis of the invention, since the mass of the annular disk 6 is arranged peripherally outwards in comparison to previously known swivel disks, by avoiding a massive design and avoiding a laterally formed driver.
Neben der für das dynamische Verhalten vorteilhaften Gestaltung derIn addition to the advantageous design of the dynamic behavior
Schwenkscheibe 6 ergibt sich durch ihre auf die Ringform begrenzteSwivel plate 6 results from its limited to the ring shape
Gestaltung der weitere Vorteil einer wesentlich vereinfachten Herstel- hing, insbesondere bei der Feinbearbeitung ihrer Seitenflächen durch Läppen. Schliesslich beansprucht die Ringscheibe im Maschinengehäu- se nur einen begrenzten Raum, so dass auch in axialer Richtung der Maschine eine besonders kompakte Bauweise möglich ist und ihr Einbau als Kompressor einer Fahrzeugklimaanlage begünstigt wird. Design the further advantage of a significantly simplified production, especially when finishing your side surfaces Lapping. Finally, the washer in the machine housing only takes up a limited space, so that a particularly compact design is also possible in the axial direction of the machine and its installation as a compressor in a vehicle air conditioning system is favored.

Claims

Patentansprüche claims
1. Hubkolbenmaschine mit einer in ihrer Neigung zur Maschinenwelle verstellbaren, von der Maschinenwelle (5) angetriebenen Schwenk- scheibe (6), indem sie sowohl mit einem auf der Maschinenwelle (5) axial geführten Schiebekörper (21) als auch mit Abstand von der Maschinenwelle (5) mit einem die Antriebskraft übertragenden Mitnehmer (13) gelenkig verbunden ist, wobei die Kolben (2) jeweils eine Gelenkanordnung (10,11,12) aufweisen, an der die Schwenkscheibe (6) in Gleiteingriff steht, dadurch gekennzeichnet, dass die Schwenkscheibe die Form einer Ringscheibe (6) hat und an einer Stelle ihres Umfanges einen zumindest radial nach innen offenen Eingriffsraum (16) aufweist, in den der Kopf (15) eines mit der Maschinenwelle (5) fest verbundenen Mitnehmers (13) eingreift.1. Reciprocating piston machine with a tilting disc (6) adjustable in its inclination to the machine shaft and driven by the machine shaft (5), both with a sliding body (21) axially guided on the machine shaft (5) and at a distance from the machine shaft (5) is connected in an articulated manner to a driver (13) transmitting the driving force, the pistons (2) each having an articulated arrangement (10, 11, 12) on which the swivel disk (6) is in sliding engagement, characterized in that the Swivel disc has the shape of an annular disc (6) and at one point on its circumference has an at least radially inwardly open engagement space (16) into which the head (15) of a driver (13) firmly connected to the machine shaft (5) engages.
2. Hubkolbenmaschine nach Anspruch 1, dadurch gekennzeichnet, dass der Kopf (15) des Mitnehmers (13) am freien Ende eines von der Maschinenwelle (5) wegragenden Bolzens (13) vorgesehen ist.2. Reciprocating piston machine according to claim 1, characterized in that the head (15) of the driver (13) is provided at the free end of a pin (13) projecting from the machine shaft (5).
3. Hubkolbenmaschine nach Anspruch 2, dadurch gekennzeichnet, dass der Bolzen (13) schräg von der Maschinenwelle (5) wegragt, so dass bei einer mittleren Neigungsposition der Ringscheibe (6) die Bolzenachse radial zur Ringscheibe (6) gerichtet ist.3. Reciprocating piston machine according to claim 2, characterized in that the bolt (13) projects obliquely from the machine shaft (5), so that the bolt axis is directed radially to the annular disc (6) at an average inclined position of the annular disc (6).
4. Hubkolbenmaschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Ringscheibe (6) eine den Eingriffsraum bildende Radialbohrung (16) hat und der Kopf 15 des Mitnehmers (13) die Form einer Kugel aufweist..4. Reciprocating piston machine according to one of claims 1 to 3, characterized in that the annular disc (6) has a radial bore (16) forming the engagement space and the head 15 of the driver (13) has the shape of a ball.
5. Hubkolbenmaschine nach Anspruch 4, dadurch gekennzeichnet, dass der Mittelpunkt (17) des Kopfes (15) des Mitnehmers (13) auf einer Kreislinie liegt, die die Mittelpunkte der Kugelform von kugelseg- mentförmigen Gelenkkörpern (11,12) der Kolben verbindet. 5. Reciprocating piston machine according to claim 4, characterized in that the center (17) of the head (15) of the driver (13) lies on a circular line which connects the centers of the spherical shape of spherical segment-shaped joint bodies (11, 12) of the pistons.
6. Hubkolbenmaschine nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass der Mittelpunkt (17) des Kopfes (15) des Mitnehmers (13) auf einer Kreislinie liegt, die die geometrischen Achsen der sieben Kolben (2) miteinander verbindet.6. Reciprocating piston machine according to claim 4 or 5, characterized in that the center point (17) of the head (15) of the driver (13) lies on a circular line which connects the geometric axes of the seven pistons (2) to one another.
7. Hubkolbenmaschine nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass die gelenkige Verbindung mit einem hülsenförmig die Maschinenwelle umschliessenden Schiebekörper (21) durch zwei Lagerbolzen (22,23) gegeben ist, die auf radial einander gegenüberlie- genden Seiten einerseits in der Ringscheibe (6) und anderseits in dem Schiebekörper (21) gleichachsig gelagert sind.7. Reciprocating piston engine according to one of claims 1 to 6, characterized in that the articulated connection with a sleeve-shaped sliding body (21) surrounding the machine shaft is provided by two bearing bolts (22, 23) which on the one hand on radially opposite sides in the Ring disc (6) and on the other hand are mounted coaxially in the sliding body (21).
8. Hubkolbenmaschine nach Anspruch 7, dadurch gekennzeichnet, dass die Lagerbolzen (22,23) in gleichachsig von dem hülsenförmigen Schiebeköφer (21) radial abstehenden Lagerhülsen (26,27) gelagert sind, die den Radialraum zwischen dem Schiebeköφer (21) und der Ringscheibe (6) überbrücken.8. Reciprocating piston machine according to claim 7, characterized in that the bearing bolts (22, 23) are mounted in bearing sleeves (26, 27) projecting radially from the sleeve-shaped sliding body (21), which define the radial space between the sliding body (21) and the annular disc (6) bridge.
9. Hubkolbenmaschine nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass der Schiebeköφer (21) hülsenförmig auf der Maschinenwelle (5) axial geführt ist, wobei der sich von der Maschinenwelle (5) zur Ringscheibe (6) erstreckende Mitnehmer (13) sich durch ein Langloch (30) des Schiebeköφers (21) erstreckt, so dass der Schiebeköφer (21) an dem Mitnehmer (13) beidseitig einen Anschlag findet (Fig.l und 2).9. Reciprocating piston machine according to one of claims 1 to 8, characterized in that the sliding body (21) is axially sleeve-shaped on the machine shaft (5), the driver (13) extending from the machine shaft (5) to the annular disc (6). extends through an elongated hole (30) of the sliding body (21), so that the sliding body (21) finds a stop on both sides of the driver (13) (FIGS. 1 and 2).
10. Hubkolbenmaschine nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass an beiden Enden des Schiebeköφers (21) Federelemente (34,35) angeordnet sind. 10. Reciprocating piston machine according to one of claims 1 to 8, characterized in that spring elements (34, 35) are arranged at both ends of the sliding body (21).
EP98949199A 1997-11-11 1998-11-03 Piston engine with a pivoting disk transmission Expired - Lifetime EP0964997B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19749727A DE19749727C2 (en) 1997-11-11 1997-11-11 Reciprocating piston machine with swivel plate gear
DE19749727 1997-11-11
PCT/IB1998/001759 WO1999024715A1 (en) 1997-11-11 1998-11-03 Piston engine with a pivoting disk transmission

Publications (2)

Publication Number Publication Date
EP0964997A1 true EP0964997A1 (en) 1999-12-22
EP0964997B1 EP0964997B1 (en) 2003-04-02

Family

ID=7848239

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98949199A Expired - Lifetime EP0964997B1 (en) 1997-11-11 1998-11-03 Piston engine with a pivoting disk transmission

Country Status (6)

Country Link
US (1) US6164252A (en)
EP (1) EP0964997B1 (en)
JP (1) JP3188716B2 (en)
DE (2) DE19749727C2 (en)
ES (1) ES2196608T3 (en)
WO (1) WO1999024715A1 (en)

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Also Published As

Publication number Publication date
DE19749727A1 (en) 1999-06-10
EP0964997B1 (en) 2003-04-02
DE19749727C2 (en) 2001-03-08
DE59807739D1 (en) 2003-05-08
JP3188716B2 (en) 2001-07-16
JP2000510549A (en) 2000-08-15
WO1999024715A1 (en) 1999-05-20
US6164252A (en) 2000-12-26
ES2196608T3 (en) 2003-12-16

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