EP1553291B1 - Reciprocating piston engine - Google Patents

Reciprocating piston engine Download PDF

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Publication number
EP1553291B1
EP1553291B1 EP04405737A EP04405737A EP1553291B1 EP 1553291 B1 EP1553291 B1 EP 1553291B1 EP 04405737 A EP04405737 A EP 04405737A EP 04405737 A EP04405737 A EP 04405737A EP 1553291 B1 EP1553291 B1 EP 1553291B1
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EP
European Patent Office
Prior art keywords
piston
control ring
reciprocating engine
pistons
engine according
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EP04405737A
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German (de)
French (fr)
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EP1553291A3 (en
EP1553291A2 (en
Inventor
Peter Kuhn
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Obrist Engineering GmbH
ixetic Bad Homburg GmbH
Visteon Global Technologies Inc
Original Assignee
Obrist Engineering GmbH
ixetic Bad Homburg GmbH
Visteon Global Technologies Inc
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Publication of EP1553291A2 publication Critical patent/EP1553291A2/en
Publication of EP1553291A3 publication Critical patent/EP1553291A3/en
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Publication of EP1553291B1 publication Critical patent/EP1553291B1/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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders

Definitions

  • the invention relates to a reciprocating engine with annularly arranged side by side, radially directed piston-cylinder units and with an eccentric shaft which extends through a cylinder enclosing the housing body of a machine housing and the eccentric controls the Ausinerhub the piston, wherein the inward stroke of the piston by a common, in the piston engaging control ring is controlled.
  • a reciprocating piston engine whose pistons are moved radially outwardly by an eccentric is through the EP 0088677 known.
  • the outward stroke of the piston is mechanically controlled by an eccentric and a rolling bearing enclosing this, while the inward stroke is effected by the force of a spring deformed by the lifting movement, so that it keeps the piston in contact with the outer ring of the rolling bearing.
  • a spring has the disadvantage, inter alia, that its arrangement adversely affects the size of the machine.
  • For your arrangement in the cylinder chamber also a space is needed, which acts as a dead space by an almost complete ejection of the medium is prevented during the Aus detailhub.
  • the machine size co-determining size of the coupling ring is obtained by its inclusion in a over the entire circumference of the cylinder block extending, also required for its assembly large annular channel.
  • This annular channel also serves to receive a stop, which is a lateral ejection of the coupling ring from the annular groove of the piston should prevent.
  • a stop which is a lateral ejection of the coupling ring from the annular groove of the piston should prevent.
  • the radial piston machine 1 has a preferably odd number of, for example, five piston-cylinder units 2,3, which are arranged side by side in a ring, in a common, relatively flat housing body 4 of a machine housing 5 by five radially directed, the piston 2 leading cylinder bores in the solid material 3 are incorporated.
  • the housing body 4 as shown in FIG Fig.2 preferably star-shaped and has five outer flange surfaces 6 for the tight assembly of exhaust valves 7 and a discharge line 8 enclosing cylinder heads.
  • the cylinder bores 3 end in a centric to the eccentric shaft 12 arranged as small as possible, circular gear chamber 10 in which the eccentric 11 of the eccentric shaft 12 with a rolling bearing 13 enclosing it performs a circulating movement.
  • the outer ring 14 of the example designed as a needle bearing roller bearing 13 is in constant contact with the facing him, inner end face 15 of the piston 2, so that the orbital motion of the eccentric 11, the piston 2 consecutively pushes radially outward to perform their Aus detailhub.
  • the five pistons 2 are coupled together by a polygonal control ring 16 by each engaging in a lateral recess 17 of the piston 2.
  • This coupling causes the control ring 16 to be pulled outward by the outward stroke of each piston 2 in order according to the orbital motion of the eccentric 11, and thus entraining the diametrically opposed pistons 2, pulling them inwardly to make their inward stroke.
  • the recess 17 of the piston has the shape of a guided in the direction of a secant and the cross-sectional shape of the control ring 16 adapted incision, thus having mutually parallel surfaces.
  • the recess 17 of the inner end face 15 of the piston 2 has the smallest possible distance, which corresponds to the thickness of a bottom wall 18 of the preferably designed as a hollow body piston 2 and it is on a limited peripheral region of the piston (2) as a lateral interruption of his in the cylinder 3 sliding cylindrical sliding surface executed.
  • the recesses 17 of the piston (2) and corresponding to the control ring 16, in deviation from the illustrated embodiment, also on the housing space 45 facing the other side of the housing body 4 may be provided. Also may be provided for the control ring 16, depending on the manufacturing cost and the forces occurring on it, other cross-sectional shapes, as corresponding to the disc-shaped design of the control ring 16 of the illustrated embodiment, such as square, so that a wider inner control surface 20 results.
  • five inner control surfaces 20 of the control ring 16 extend at least approximately and go over a small, provided for better distribution of forces acting on the control ring 16 forces rounding 22 in the circumferentially following inner control surface 20, so that the control ring 16 is a polygonal inner Contour has.
  • a slight convex curvature of these control surfaces 20 in the circumferential direction may be advantageous in order to counteract a load on the boundary surfaces 61, 62 of the contact surfaces which are transverse to the piston axis.
  • the control ring 16 can extend transversely through the piston 2 and in this direction relative to the piston unhindered perform a transverse movement, which results from the in-phase control of the orbital movement of the eccentric 11 control movement.
  • the laterally open recesses 17 allow the piston 2 during assembly of the machine, a simple assembly of the movable components.
  • control ring 16 In order to secure the control ring 16 in the direction of laterally outward in the recesses 17 of the piston (2), it slides in its circumferential movement in a circumferentially extending recess 65 of the housing body 4, which is designed for example as a radial incision.
  • the smallest possible executed gear housing 10 of the solid housing body 4 has laterally adjacent to the control ring 16 has a circular circumferential extension 66 corresponding to the size of the control ring 16, which allows its insertion into the one-piece housing body 4.
  • control ring 16 has five circular arc-shaped parts 21 of a cylindrical surface which are each bounded by a recess 23 of the control ring 16. These five recesses 23 each form an inflow opening to the laterally open through the recess 17, cylindrical interior 24 of the piston 2.
  • the recesses 23 are arranged such that they are shown in FIG Figure 3 extend over a lateral part of the respective engagement region of the control ring 16, and the inflow into the piston recess 17 corresponding to the side and thereby tangentially into the cylindrical interior 24 of the piston 2 takes place.
  • the diaphragm 33 of a check valve 31 is closed by means of its edge 35, e.g. fixed by welding.
  • the membrane 33 has a central closing part 32 and three web parts 34 extending from the latter in an arcuate manner to the membrane edge 35, so that the web parts 34 form spring elements for the lifting movement of the closing part 32.
  • the cylinder bores 3 are bounded by a plate-shaped part 36 of the cylinder head 9, which encloses a central outflow channel 37 against which the membrane 38 of a check valve rests on the outside, correspondingly the representation in Figure 4 is carried out the same as the diaphragm 33 of the valve 2 provided on the check valve.
  • connection blocks 39 which connect via connecting channels 40 to a connection to the machine housing 5 enclosing manifold 41.
  • the eccentric shaft 12 is mounted in the machine housing 5 or its bell-shaped housing body 50 by two roller bearings 42,43.
  • a drive-side sealing arrangement 44 seals the housing interior 45 axially to the outside, while the free, the eccentric 11 and a balance weight 46 supporting shaft end 47 ends in a housing space 48 which is closed by a flanged housing cover 49.
  • a compensation channel may extend through the eccentric shaft in a manner not shown.
  • the reciprocating piston engine 1 is particularly suitable as a compressor of a CO 2 air conditioning system for installation in the engine compartment of a motor vehicle. Furthermore, the essential components of the invention of the machine are designed so that they can be produced in a simple manner and mounted to each other.
  • the pistons 2 consist of two telescopically intermeshed parts, and prior to their combination, one of these parts, i. attached to the piston head 29 having part, the valve diaphragm 33 and the other part of the recess 17 made by a lateral milled recess. When joined by a press fit they take between them a piston ring 58.
  • a reciprocating piston engine 1 according to the invention is suitable for high rotational speeds of more than 10,000 revs / min, so that the balancing of the eccentric shaft 12 and the components rotating with it, i.a. by the balance weight 46 and e.g. a recess 60 on the co-rotating baffle plate 55 is of particular importance.

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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)
  • Details Of Reciprocating Pumps (AREA)
  • Valve Device For Special Equipments (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

The engine (1) has a control ring (16) engaged in the lateral recess formed on each piston (2) running in the direction of a secant, and adapted to a cross-sectional shape of the control ring. The lateral recess bounds a base wall of the piston. The control ring is arranged in controlling sliding contact via an inner control face with the base wall. The inward stroke of the pistons is controlled by the control ring. A cam (11) of an eccentric shaft controls the outward stroke of the pistons. The shaft extends through a casing body (4) of an engine casing which encloses the cylinders (3).

Description

Die Erfindung betrifft eine Hubkolbenmaschine mit ringförmig nebeneinander angeordneten, radial gerichteten Kolben-Zylindereinheiten und mit einer Exzenterwelle , die sich durch einen die Zylinder einschließenden Gehäusekörper eines Maschinengehäuses erstreckt und deren Exzenter den Auswärtshub der Kolben steuert, wobei der Einwärtshub der Kolben durch einen gemeinsamen, in die Kolben eingreifenden Steuerring gesteuert wird.The invention relates to a reciprocating engine with annularly arranged side by side, radially directed piston-cylinder units and with an eccentric shaft which extends through a cylinder enclosing the housing body of a machine housing and the eccentric controls the Auswärtshub the piston, wherein the inward stroke of the piston by a common, in the piston engaging control ring is controlled.

Eine Hubkolbenmaschinen deren Kolben durch einen Exzenter radial auswärts bewegt werden, ist durch die EP 0088677 bekannt. Bei dieser wird nur der Auswärtshub der Kolben durch einen Exzenter und über ein diesen umschließendes Wälzlager mechanisch gesteuert, während der Einwärtshub durch die Kraft einer durch die Hubbewegung verformten Feder erfolgt, so dass sie den Kolben in Kontakt mit dem Außenring des Wälzlagers hält. Eine solche Feder hat u.a. den Nachteil, dass ihre Anordnung die Baugröße der Maschine nachteilig beeinflusst. Für Ihre Anordnung im Zylinderraum wird außerdem ein Raum benötigt, der als Totraum wirkt, indem beim Auswärtshub ein nahezu vollständiger Ausschub des Mediums verhindert wird.A reciprocating piston engine whose pistons are moved radially outwardly by an eccentric is through the EP 0088677 known. In this, only the outward stroke of the piston is mechanically controlled by an eccentric and a rolling bearing enclosing this, while the inward stroke is effected by the force of a spring deformed by the lifting movement, so that it keeps the piston in contact with the outer ring of the rolling bearing. Such a spring has the disadvantage, inter alia, that its arrangement adversely affects the size of the machine. For your arrangement in the cylinder chamber also a space is needed, which acts as a dead space by an almost complete ejection of the medium is prevented during the Auswärtshub.

Durch die GB 2225614 ( JP2188678 ) ist es auch bekannt, die Rückholbewegung von jeweils zwei sich gegenüberliegenden, durch einen Exzenter nach aussen bewegten Kolben durch ein Paar von seitlichen Fortsätzen eines Kuppelringes auszuführen, die gabelförmig in eine Eindrehung eines inneren, sich in den Gehäuseraum hinein erstreckenden Kolbenendes mit Federvorspannung eingreifen. Folglich werden die Kolben nicht auf ihrer gesamten Länge in den zugehörigen Zylindern geführt und der für die Aufnahme des Kuppelringes und der aus den Zylindern herausragenden Kolbenenden benötigte Raum verhindert eine kompakte Bauweise der Maschine. Auch ist die Maschine aufgrund der federnd ausgeführten seitlichen Fortsätze des Kuppelringes nur als Pumpe mit verhältnismäßig niedriger Arbeitsgeschwindigkeit geeignet.By the GB 2225614 ( JP2188678 ), it is also known to perform the return movement of two opposing, by an eccentric outwardly moving piston through a pair of lateral extensions of a coupling ring, which engage fork-shaped in a recess of an inner, extending into the housing space in the piston end with spring bias. Consequently, the pistons are not guided along their entire length in the associated cylinders and the space required to receive the coupling ring and the piston ends projecting from the cylinders prevents them from coming compact design of the machine. Also, the machine is due to the spring-designed side extensions of the coupling ring suitable only as a pump with relatively low operating speed.

Durch die AT 394892 ist es weiterhin bekannt, die Hubbewegung von ringförmig zueinander angeordneten Kolben allein durch einen Exzenter zu steuern, indem die Kolben über einen an ihrem radial inneren Ende vorgesehenen Kugelkopf in einen den Exzenter umschließenden, ringförmigen Steuerungskörper gelenkig eingreifen. Eine solche Kolbensteuerung hat für die Anordnung der mechanischen Kopplung zwischen dem den Exzenter umschließenden, z.B. ringförmigen Steuerungskörper und dem jeweiligen Kolben einen eine kompakte Bauweise verhindernden Raumbedarf, verbunden mit einer entsprechend aufwändigen Bauweise für die mechanische Kopplung mit dem Steuerungskörper.By the AT 394892 It is also known, the lifting movement of annularly arranged piston to control solely by an eccentric by the piston engage via a provided at its radially inner end ball in an eccentric enclosing annular control body articulated. Such a piston control has for the arrangement of the mechanical coupling between the eccentric enclosing, eg annular control body and the respective piston a compact design preventing space requirement, associated with a correspondingly complex design for the mechanical coupling with the control body.

Schließlich ist es durch die US 3259074 ( DE 1453663 ) bekannt, für die Rückholbewegung von paarweise einander gegenüberliegenden Kolben einen gemeinsamen Kuppelring vorzusehen, der seitlich in eine umlaufende Nut der Kolben eingreift. Diese gemeinsame Kupplung von jeweils zwei gleichachsigen, einander gegenüberliegenden Kolbenpaaren durch nur einen Kuppelring wird durch einen seine Querverschiebung in dem zweiten Kolbenpaar zulassenden Eingriff über vier im Winkel von 90° zueinander angeordnete ebene Gleitflächen des Kuppelringes ermöglicht. Für ihren Kontakt mit dem Exzenter und den seitlichen Eingriff des Kuppelringes im mittleren Bereich der Kolbenlänge haben diese Kolben eine verhältnismäßig große Länge und die Maschine eine entsprechend große radiale Ausdehnung. Die die Maschinengröße mitbestimmende Größe des Kuppelringes ergibt sich dabei durch dessen Aufnahme in einem sich über den gesamten Umfang des Zylinderblocks erstreckenden, auch für seine Montage benötigten großen Ringkanal. Dieser Ringkanal dient auch der Aufnahme eines Anschlages, der ein seitliches Herausschleudern des Kuppelringes aus der Ringnut der Kolben verhindern soll. Auch durch die verhältnismäßig erhebliche Größe des Kuppelringes, für den auch eine Ausführung aus Draht vorgesehen ist, ist eine solche Maschine für hohe Arbeitsgeschwindigkeiten ungeeignet.Finally it is through the US 3259074 ( DE 1453663 ) is known to provide for the return movement of pairs opposing pistons a common coupling ring which engages laterally in a circumferential groove of the piston. This common coupling of two equiaxed, opposing pairs of pistons by only one coupling ring is made possible by a its transverse displacement in the second pair of pistons permitting engagement over four at an angle of 90 ° to each other arranged planar sliding surfaces of the coupling ring. For their contact with the eccentric and the lateral engagement of the coupling ring in the central region of the piston length, these pistons have a relatively large length and the machine has a correspondingly large radial extent. The machine size co-determining size of the coupling ring is obtained by its inclusion in a over the entire circumference of the cylinder block extending, also required for its assembly large annular channel. This annular channel also serves to receive a stop, which is a lateral ejection of the coupling ring from the annular groove of the piston should prevent. Also, by the relatively large size of the coupling ring, for which an embodiment of wire is provided, such a machine for high speeds is unsuitable.

Der Erfindung liegt die Aufgabe zugrunde, eine Radialkolbenmaschine der genannten Art zu finden, die bei besonders kompakter Bauweise nur verhältnismäßig wenige, einfach herstellbare und einfach montierbare Bauteile benötigt und die darüber hinaus, z.B. bei der Ausführung als Kompressor einer CO2-Klimaanlage, bei hohen Drücken und durch hohe mögliche Drehgeschwindigkeiten hohe Leistungen ermöglicht. Die Lösung dieser Aufgabe erfolgt erfindungsgemäß aufgrund der kennzeichnenden Merkmale des Patentanspruchs 1. Vorteilhafte Ausführungsformen der Erfindung sind Gegenstand der abhängigen Patentansprüche und der folgenden Beschreibung anhand der Zeichnungen zu entnehmen. Es zeigt:

  • Fig.1 einen Axialschnitt durch eine erfindungsgemäße Radialkolbenmaschine,
  • Fig.2 einen die Kolbenachsen einschließenden Radialschnitt entlang der Linie II-II der Fig.1,
  • Fig.3 eine perspektivische Darstellung zweier benachbarter Kolben der Kolbenanordnung entsprechend Fig.2, mit einem in diese Kolben eingreifenden Umfangsbereich des Steuerringes,
  • Fig.4 eine Aufsicht auf eine Ventilmembran von an den Kolben und an den Zylinderköpfen vorgesehenen Rückschlagventilen,
  • Fig.5 eine vergrößerte Darstellung aus dem Bereich V der Fig.1,
  • Fig.6 eine Seitenansicht des Steuerringes der Hubkolbenmaschine nach Fig.1 und 2 und
  • Fig.7 einen vergrößerten Axialschnitt eines der fünf Kolben der Hubkolbenmaschine nach Fig.1 und 2 mit schematischer Darstellung einer rotierenden Zuströmung.
The invention has for its object to find a radial piston engine of the type mentioned, the relatively compact design requires only a relatively few, easy to produce and easy to install components and beyond, for example, when running as a compressor of a CO 2 air conditioning, at high Press and high power possible through high possible rotational speeds. The solution of this object is achieved according to the invention by the characterizing features of claim 1. Advantageous embodiments of the invention are the subject of the dependent claims and the following description with reference to the drawings. It shows:
  • Fig.1 an axial section through a radial piston machine according to the invention,
  • Fig.2 a piston axis enclosing radial section along the line II-II of Fig.1 .
  • Figure 3 a perspective view of two adjacent pistons of the piston assembly accordingly Fig.2 with a circumferential region of the control ring engaging in this piston,
  • Figure 4 a plan view of a valve diaphragm provided on the piston and on the cylinder heads check valves,
  • Figure 5 an enlarged view of the area V of Fig.1 .
  • Figure 6 a side view of the control ring of the reciprocating engine after Fig.1 and 2 and
  • Figure 7 an enlarged axial section of one of the five pistons of the reciprocating engine after Fig.1 and 2 with a schematic representation of a rotating inflow.

Die Radialkolbenmaschine 1 hat eine vorzugsweise ungerade Anzahl von beispielsweise fünf Kolben-Zylindereinheiten 2,3, die ringförmig nebeneinander, in einem gemeinsamen, relativ flachen Gehäusekörper 4 eines Maschinengehäuses 5 angeordnet sind, indem in dessen massives Material fünf radial gerichtete, die Kolben 2 führende Zylinderbohrungen 3 eingearbeitet sind.The radial piston machine 1 has a preferably odd number of, for example, five piston-cylinder units 2,3, which are arranged side by side in a ring, in a common, relatively flat housing body 4 of a machine housing 5 by five radially directed, the piston 2 leading cylinder bores in the solid material 3 are incorporated.

Zur Materialeinsparung ist der Gehäusekörper 4 entsprechend der Darstellung in Fig.2 vorzugsweise sternförmig ausgebildet und hat außen fünf Flanschflächen 6 für die dichte Montage von Auslassventilen 7 und von eine Abströmleitung 8 einschließenden Zylinderköpfen 9.To save material, the housing body 4 as shown in FIG Fig.2 preferably star-shaped and has five outer flange surfaces 6 for the tight assembly of exhaust valves 7 and a discharge line 8 enclosing cylinder heads. 9

Zum Zentrum des Gehäusekörpers 4 hin enden die Zylinderbohrungen 3 in einem zentrisch zur Exzenterwelle 12 angeordneten, möglichst kleinen, kreisförmigen Getrieberaum 10, in dem der Exzenter 11 der Exzenterwelle 12 mit einem ihn umschließenden Wälzlager 13 eine Umlaufbewegung ausführt.Toward the center of the housing body 4, the cylinder bores 3 end in a centric to the eccentric shaft 12 arranged as small as possible, circular gear chamber 10 in which the eccentric 11 of the eccentric shaft 12 with a rolling bearing 13 enclosing it performs a circulating movement.

Der Außenring 14 des z.B. als Nadellager ausgeführten Wälzlagers 13 befindet sich in ständigem Kontakt mit der ihm zugekehrten, inneren Stirnfläche 15 der Kolben 2, so dass die Umlaufbewegung des Exzenters 11 die Kolben 2 aufeinander folgend, radial nach außen schiebt, um ihren Auswärtshub auszuführen.The outer ring 14 of the example designed as a needle bearing roller bearing 13 is in constant contact with the facing him, inner end face 15 of the piston 2, so that the orbital motion of the eccentric 11, the piston 2 consecutively pushes radially outward to perform their Auswärtshub.

Für den Antrieb des Einwärtshubs sind die fünf Kolben 2 durch einen polygonförmigen Steuerring 16 miteinander gekoppelt, indem dieser jeweils in eine seitliche Aussparung 17 der Kolben 2 eingreift. Diese Kopplung bewirkt, dass der Steuerring 16 durch den Auswärtshub jedes Kolbens 2 in Reihenfolge entsprechend der Umlaufbewegung des Exzenters 11 nach außen gezogen wird und folglich die diametral gegenüberliegend angeordneten Kolben 2 mitnehmend, diese nach innen zieht, so dass sie ihren Einwärtshub ausführen.For the drive of the inward stroke, the five pistons 2 are coupled together by a polygonal control ring 16 by each engaging in a lateral recess 17 of the piston 2. This coupling causes the control ring 16 to be pulled outward by the outward stroke of each piston 2 in order according to the orbital motion of the eccentric 11, and thus entraining the diametrically opposed pistons 2, pulling them inwardly to make their inward stroke.

Die Aussparung 17 der Kolben hat die Form eines in Richtung einer Sekante geführten und der Querschnittsform des Steuerringes 16 angepassten Einschnittes, mit somit zueinander parallelen Flächen. Dabei hat die Aussparung 17 von der inneren Stirnfläche 15 der Kolben 2 einen möglichst geringen Abstand, der der Dicke einer Bodenwand 18 des vorzugsweise als Hohlkörper ausgeführten Kolbens 2 entspricht und sie ist auf einem begrenzten Umfangsbereich des Kolbens (2) als seitliche Unterbrechung seiner im Zylinder 3 gleitenden, zylindrischen Gleitfläche ausgeführt. Dies hat den Vorteil, dass die Kolben zumindest auf ihrer nicht durch die Aussparung 17 unterbrochenen, in Umfangsrichtung einen Bogen von wesentlich mehr als 180° aufweisenden größeren Seite, über ihre gesamte Länge lückenlos im Zylinder 3 geführt sind.The recess 17 of the piston has the shape of a guided in the direction of a secant and the cross-sectional shape of the control ring 16 adapted incision, thus having mutually parallel surfaces. In this case, the recess 17 of the inner end face 15 of the piston 2 has the smallest possible distance, which corresponds to the thickness of a bottom wall 18 of the preferably designed as a hollow body piston 2 and it is on a limited peripheral region of the piston (2) as a lateral interruption of his in the cylinder 3 sliding cylindrical sliding surface executed. This has the advantage that the pistons, at least on their not interrupted by the recess 17, in the circumferential direction an arc of substantially more than 180 ° having larger side, are guided over their entire length gapless in the cylinder 3.

Es versteht sich, dass die Aussparungen 17 der Kolben (2) und entsprechend der Steuerring 16, in Abweichung vom dargestellten Ausführungsbeispiel, auch auf der dem Gehäuseraum 45 zugekehrten, anderen Seite des Gehäusekörpers 4 vorgesehen sein können. Auch können für den Steuerring 16, abhängig vom Herstellungsaufwand und der an ihm auftretenden Kräfte, andere Querschnittsformen vorgesehen sein, als entsprechend der scheibenförmigen Ausführung des Steuerringes 16 des dargestellten Ausführungsbeispieles, wie z.B. quadratisch, so dass sich eine breitere innere Steuerfläche 20 ergibt.It is understood that the recesses 17 of the piston (2) and corresponding to the control ring 16, in deviation from the illustrated embodiment, also on the housing space 45 facing the other side of the housing body 4 may be provided. Also may be provided for the control ring 16, depending on the manufacturing cost and the forces occurring on it, other cross-sectional shapes, as corresponding to the disc-shaped design of the control ring 16 of the illustrated embodiment, such as square, so that a wider inner control surface 20 results.

Die im dargestellten Ausführungsbeispiel fünf inneren Steuerflächen 20 des Steuerringes 16 verlaufen zumindest angenähert und gehen über eine kleine, zur besseren Verteilung von am Steuerring 16 wirkenden Kräften vorgesehene Ausrundung 22 in die in Umfangsrichtung folgende innere Steuerfläche 20 über, so dass der Steuerring 16 eine polygonförmige innere Kontur hat. Eine geringfügige konvexe Krümmung dieser Steuerflächen 20 in Umfangsrichtung kann von Vorteil sein, um einer Belastung der quer zur Kolbenachse endseitigen Begrenzungskanten 61,62 der Kontaktflächen entgegen zu wirken.The illustrated in the embodiment, five inner control surfaces 20 of the control ring 16 extend at least approximately and go over a small, provided for better distribution of forces acting on the control ring 16 forces rounding 22 in the circumferentially following inner control surface 20, so that the control ring 16 is a polygonal inner Contour has. A slight convex curvature of these control surfaces 20 in the circumferential direction may be advantageous in order to counteract a load on the boundary surfaces 61, 62 of the contact surfaces which are transverse to the piston axis.

Da die Aussparung 17 der Kolben 2 somit seitlich offen ist, kann sich der Steuerring 16 quer durch die Kolben 2 erstrecken und in dieser Richtung relativ zum Kolben ungehindert eine Querbewegung ausführen, die sich durch die phasengleich mit der Umlaufbewegung des Exzenters 11 erfolgende Steuerbewegung ergibt. Dabei gleiten seine inneren Steuerflächen 20 auf der jeweiligen inneren Bodenwand 18 der fünf Kolben 2. Außerdem ermöglichen die seitlich offenen Aussparungen 17 der Kolben 2 bei der Montage der Maschine ein einfaches Zusammenfügen der beweglichen Komponenten.Since the recess 17 of the piston 2 is thus open to the side, the control ring 16 can extend transversely through the piston 2 and in this direction relative to the piston unhindered perform a transverse movement, which results from the in-phase control of the orbital movement of the eccentric 11 control movement. In this case, slide its inner control surfaces 20 on the respective inner bottom wall 18 of the five pistons 2. In addition, the laterally open recesses 17 allow the piston 2 during assembly of the machine, a simple assembly of the movable components.

Um den Steuerring 16 auch in Richtung seitlich nach außen in den Aussparungen 17 der Kolben (2) zu sichern, gleitet er bei seiner Umlaufbewegung in einer umlaufend ausgeführten Ausnehmung 65 des Gehäusekörpers 4, die beispielsweise als radialer Einschnitt ausgeführt ist. Der möglichst klein ausgeführte Getrieberaum 10 des massiven Gehäusekörpers 4 hat seitlich angrenzend an den Steuerring 16 eine kreisförmig umlaufende Erweiterung 66 entsprechend der Größe des Steuerringes 16, die sein Einsetzen in den einteilig ausgeführten Gehäusekörper 4 ermöglicht.In order to secure the control ring 16 in the direction of laterally outward in the recesses 17 of the piston (2), it slides in its circumferential movement in a circumferentially extending recess 65 of the housing body 4, which is designed for example as a radial incision. The smallest possible executed gear housing 10 of the solid housing body 4 has laterally adjacent to the control ring 16 has a circular circumferential extension 66 corresponding to the size of the control ring 16, which allows its insertion into the one-piece housing body 4.

Außen hat der Steuerring 16 fünf kreisbogenförmige Teile 21 einer Zylinderfläche, die jeweils durch eine Ausnehmung 23 des Steuerringes 16 begrenzt sind. Diese fünf Ausnehmungen 23 bilden jeweils eine Zuströmöffnung zu dem durch die Aussparung 17 seitlich geöffneten, zylindrischen Innenraum 24 der Kolben 2. Dabei sind die Ausnehmungen 23 derart angeordnet, dass sie sich entsprechend der Darstellung in Fig.3 über einen seitlichen Teil des jeweiligen Eingriffsbereichs des Steuerringes 16 erstrecken, und die Einströmung in die Kolbenaussparung 17 entsprechend seitlich und dadurch tangential in den zylindrischen Innenraum 24 der Kolben 2 erfolgt.Outside, the control ring 16 has five circular arc-shaped parts 21 of a cylindrical surface which are each bounded by a recess 23 of the control ring 16. These five recesses 23 each form an inflow opening to the laterally open through the recess 17, cylindrical interior 24 of the piston 2. The recesses 23 are arranged such that they are shown in FIG Figure 3 extend over a lateral part of the respective engagement region of the control ring 16, and the inflow into the piston recess 17 corresponding to the side and thereby tangentially into the cylindrical interior 24 of the piston 2 takes place.

Die tangentiale Einströmung in Richtung der doppelten Pfeile 25,26 führt im zylindrischen Innenraum 24 zu einer Spiralströmung 27 mit einer Zentrifugalwirkung, so dass ein in gasförmigem Betriebsmedium enthaltenes Schmiermittel in der Maschine 1 zurückgehalten wird, wie die gegen die zylindrische Innenwand 19 des Kolbens 2 gerichteten Pfeile 26 andeuten. Diese Zentrifugalwirkung wird durch die Abströmung des gasförmigen Mediums durch einen zentralen Innenstutzen 28 des Kolbens 2 unterstützt, dessen zentraler Kanal an der radial äußeren Stirnfläche des Kolbens (2) in einer Ventilöffnung 30 mündet.The tangential inflow in the direction of the double arrows 25,26 leads in the cylindrical interior 24 to a spiral flow 27 with a centrifugal action, so that a lubricant contained in gaseous operating medium is retained in the machine 1, as directed against the cylindrical inner wall 19 of the piston 2 Indicate arrows 26. This centrifugal action is assisted by the outflow of the gaseous medium through a central inner socket 28 of the piston 2, the central channel of which opens on the radially outer end face of the piston (2) in a valve opening 30.

An der Stirnfläche der Kolben 2 ist die Membran 33 eines Rückschlagventils 31 mittels ihres Randes 35 z.B. durch Schweißen befestigt. Die Membran 33 hat einen zentralen Schließteil 32 und drei sich von diesem bogenförmig zum Membranrand 35 erstreckende Stegteile 34, so dass die Stegteile 34 Federelemente für die Hubbewegung des Schließteiles 32 bilden.At the end face of the pistons 2, the diaphragm 33 of a check valve 31 is closed by means of its edge 35, e.g. fixed by welding. The membrane 33 has a central closing part 32 and three web parts 34 extending from the latter in an arcuate manner to the membrane edge 35, so that the web parts 34 form spring elements for the lifting movement of the closing part 32.

Radial nach außen sind die Zylinderbohrungen 3 durch einen plattenförmigen Teil 36 des Zylinderkopfes 9 begrenzt, der einen zentralen Ausströmkanal 37 umschließt, an dem außen die Membran 38 eines Rückschlagventils anliegt, die entsprechend der Darstellung in Fig.4 gleich ausgeführt ist, wie die Membran 33 des am Kolben 2 vorgesehenen Rückschlagventils.Radially outward, the cylinder bores 3 are bounded by a plate-shaped part 36 of the cylinder head 9, which encloses a central outflow channel 37 against which the membrane 38 of a check valve rests on the outside, correspondingly the representation in Figure 4 is carried out the same as the diaphragm 33 of the valve 2 provided on the check valve.

Aus den zylindrischen Arbeitsräumen 3 strömt das Arbeitsmedium in Anschlussblöcke 39, die über Verbindungskanäle 40 die Verbindung zu einer das Maschinengehäuse 5 umschließenden Sammelleitung 41 herstellen. Durch diese außen am Gehäusekörper 4 befestigten Anschlussblöcke sind die plattenförmigen Teile der Zylinderköpfe 9 unter Vorspannung dicht am Gehäusekörper 4 gehalten.From the cylindrical work chambers 3, the working fluid flows into connection blocks 39, which connect via connecting channels 40 to a connection to the machine housing 5 enclosing manifold 41. By this outside the housing body 4 attached terminal blocks, the plate-shaped parts of the cylinder heads 9 are held under prestressing close to the housing body 4.

Die Exzenterwelle 12 ist im Maschinengehäuse 5 bzw. dessen glockenförmigem Gehäusekörper 50 durch zwei Wälzlager 42,43 gelagert. Eine antriebsseitige Dichtanordnung 44 dichtet den Gehäuseinnenraum 45 axial nach außen ab, während das freie, den Exzenter 11 und ein Ausgleichsgewicht 46 tragende Wellenende 47 in einem Gehäuseraum 48 endet, der durch einen angeflanschten Gehäusedeckel 49 verschlossen ist. Für einen Druckausgleich zwischen den Gehäuseräumen 45 und 48 kann sich auf nicht dargestellte Weise ein Ausgleichskanal durch die Exzenterwelle hindurch erstrecken.The eccentric shaft 12 is mounted in the machine housing 5 or its bell-shaped housing body 50 by two roller bearings 42,43. A drive-side sealing arrangement 44 seals the housing interior 45 axially to the outside, while the free, the eccentric 11 and a balance weight 46 supporting shaft end 47 ends in a housing space 48 which is closed by a flanged housing cover 49. For a pressure equalization between the housing chambers 45 and 48, a compensation channel may extend through the eccentric shaft in a manner not shown.

Die Zuströmung des Arbeitsmediums in die Hubkolbenmaschine 1 erfolgt über mindestens einen am glockenförmigen zweiten Gehäuseblock 50 radial angeschlossenen Anschlussstutzen 51. Anschließend durchströmt es entsprechend der Darstellung in Fig.5 in der Gehäuseinnenwand 52 vorgesehene Axialkanäle 53,54 und trifft auf eine sich mit der Exzenterwelle 11 drehende Prallplatte 55, an der ein Schmiermittelanteil im gasförmigen Betriebsmedium abgeschieden wird. Die Weiterströmung erfolgt durch Umströmung der Prallplatte 55 und über einen Spalt 56 zwischen der Prallplatte und dem Gehäusekörper 50 zu dem zentrisch zur Gehäuse- und Wellenachse 57 angeordneten und kreisförmigen Getrieberaum 10 des Gehäusekörpers 4, in dem der Exzenter 11 umläuft, so dass das Betriebsmedium vom endseitigen Gehäuseraum 48 in der zuvor beschriebenen Weise in die Kolben 2 einströmen kann.The inflow of the working medium in the reciprocating engine 1 via at least one bell-shaped second housing block 50 radially connected connecting piece 51. Then it flows through as shown in FIG Figure 5 provided in the housing inner wall 52 axial channels 53,54 and meets a rotating with the eccentric shaft 11 baffle plate 55, on which a lubricant portion is deposited in the gaseous operating medium. The further flow takes place by flowing around the baffle plate 55 and a gap 56 between the baffle plate and the housing body 50 to the centrally arranged to the housing and shaft axis 57 and circular gear chamber 10 of the housing body 4, in which the eccentric 11 rotates, so that the operating medium from end Housing chamber 48 can flow into the piston 2 in the manner described above.

Die Ausbildung der genannten Rückschlagventile für die Zuströmung in die Arbeitszylinder 3 und die Abströmung aus diesen als Membranventil und die Anordnung eines derselben unmittelbar am Kolben 2 ermöglicht besonders geringe radiale Dimensionen bzw. eine besonders kompakte Bauweise der Hubkolbenmaschine 1 und sie kann dennoch mit hohen Drehgeschwindigkeiten ihres Exzenters 11 betrieben werden, so dass hohe Leistungen möglich sind. Entsprechend ist die erfindungsgemäße Hubkolbenmaschine 1 besonders als Kompressor einer CO2-Klimaanlage für den Einbau in den Motorraum eines Kraftfahrzeuges geeignet. Weiterhin sind die erfindungswesentlichen Komponenten der Maschine so gestaltet, dass sie auf einfache Weise herstellbar und zueinander montierbar sind.The formation of said check valves for the inflow into the working cylinder 3 and the outflow of these as a diaphragm valve and the arrangement of a same directly on the piston 2 allows particularly small radial dimensions or a particularly compact design of the reciprocating engine 1 and they can still with high rotational speeds of their Exzenters 11 are operated so that high performance is possible. Accordingly, the reciprocating piston engine 1 according to the invention is particularly suitable as a compressor of a CO 2 air conditioning system for installation in the engine compartment of a motor vehicle. Furthermore, the essential components of the invention of the machine are designed so that they can be produced in a simple manner and mounted to each other.

Für ihre einfache Herstellbarkeit bestehen die Kolben 2 aus zwei teleskopartig ineinander geschobenen Teilen und vor ihrer Vereinigung wird an einem dieser Teile, d.h. dem den Kolbenboden 29 aufweisenden Teil, die Ventilmembran 33 befestigt und am anderen Teil die Aussparung 17 durch eine seitliche Einfräsung hergestellt. Beim Zusammenfügen durch eine Presspassung nehmen sie zwischen sich einen Kolbenring 58 auf.For ease of manufacture, the pistons 2 consist of two telescopically intermeshed parts, and prior to their combination, one of these parts, i. attached to the piston head 29 having part, the valve diaphragm 33 and the other part of the recess 17 made by a lateral milled recess. When joined by a press fit they take between them a piston ring 58.

Eine erfindungsgemäße Hubkolbenmaschine 1 ist für hohe Drehgeschwindigkeiten von mehr 10 000 U/min geeignet, so dass die Auswuchtung der Exzenterwelle 12 und der sich mit ihr drehenden Komponenten, u.a. durch das Ausgleichsgewicht 46 und z.B. eine Ausnehmung 60 an der mitumlaufenden Prallplatte 55 von besonderer Bedeutung ist.A reciprocating piston engine 1 according to the invention is suitable for high rotational speeds of more than 10,000 revs / min, so that the balancing of the eccentric shaft 12 and the components rotating with it, i.a. by the balance weight 46 and e.g. a recess 60 on the co-rotating baffle plate 55 is of particular importance.

Claims (10)

  1. Reciprocating engine with annularly arranged, radially directed piston-cylinder units (2, 3) and with an eccentric shaft (12) extending through a casing body (4) of an engine casing (5) enclosing the cylinders (3) and whose cam (11) controls the outward stroke of the pistons (2), the inward stroke of the pistons (2) being controlled by a common control ring (16) engaging in the pistons (2), characterized in that the engagement of the control ring (16) takes place in a lateral recess (17) of each piston (2) running in the direction of a secant and adapted to a cross-sectional shape of the control ring (16) and which bounds a base wall of the piston (2), the control ring (16) being in controlling sliding contact via an inner control face (20) with said base wall (18).
  2. Reciprocating engine according to claim 1, characterized in that the number of piston-cylinder units (2, 3) is uneven, so that the substantially linearly directed, inner control faces (20) of the control ring (16) together form a polygon with a non-right-angled, reciprocal association.
  3. Reciprocating engine according to claim 1 or 2, characterized in that the inner control faces (20) of the control ring (16) have a slightly convex curvature preventing edge contact with the base wall (18).
  4. Reciprocating engine according to one of the claims 1 to 3, characterized in that a lateral face of the control ring (16) borders with sliding contact the boundary surface of the recess (17) running in the direction of a secant.
  5. Reciprocating engine according to one of the claims 1 to 4, characterized in that the recess (17) and therefore the control ring (16) extend by up to more than half the piston radius into the particular piston (2).
  6. Reciprocating engine according to one of the claims 1 to 5, characterized in that a clearance (65) forming at least one butting face for the control ring (16) is provided in the casing body (4).
  7. Reciprocating engine according to one of the claims 1 to 6, characterized in that the pistons (2) are constructed as hollow bodies with a cylindrical inner wall (19), so that the recess (17) provided for the control ring (16) forms a lateral piston opening.
  8. Reciprocating engine according to claim 7, characterized in that on its circumferential areas engaging in a recess (17) of the pistons (2), the control ring (16) has in each case a clearance (23), which forms an inflow connection to the inner piston space (24) tangential to the cylindrical piston inner wall (19).
  9. Reciprocating engine according to one of the claims 7 or 8, characterized in that an inner connection (28) is provided on the outer piston head (29) and therefore forms a central piston channel issuing at the end face of the piston (2), the diaphragm (33) of a diaphragm valve (31) engaging on said end face.
  10. Reciprocating engine according to one of the claims 1 to 9, characterized in that the pistons (2) comprise two telescopically engaged parts enclosing between them a piston ring (58) and on one of said parts is provided a central inner connection (28) and a valve diaphragm (33) and the recess (17) is milled laterally in the other part.
EP04405737A 2003-12-03 2004-11-29 Reciprocating piston engine Not-in-force EP1553291B1 (en)

Applications Claiming Priority (2)

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DE10356373A DE10356373A1 (en) 2003-12-03 2003-12-03 reciprocating engine
DE10356373 2003-12-03

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EP1553291A2 EP1553291A2 (en) 2005-07-13
EP1553291A3 EP1553291A3 (en) 2008-03-12
EP1553291B1 true EP1553291B1 (en) 2009-03-11

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EP04405737A Not-in-force EP1553291B1 (en) 2003-12-03 2004-11-29 Reciprocating piston engine

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US (1) US7273004B2 (en)
EP (1) EP1553291B1 (en)
JP (1) JP4523394B2 (en)
CN (1) CN1651720B (en)
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Also Published As

Publication number Publication date
ATE425358T1 (en) 2009-03-15
US20050120984A1 (en) 2005-06-09
US7273004B2 (en) 2007-09-25
CN1651720B (en) 2010-10-13
DE502004009129D1 (en) 2009-04-23
DE10356373A1 (en) 2005-07-07
JP2005163792A (en) 2005-06-23
JP4523394B2 (en) 2010-08-11
EP1553291A3 (en) 2008-03-12
EP1553291A2 (en) 2005-07-13
CN1651720A (en) 2005-08-10

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