EP1651866B1 - Eccentric drive mechanism for volumetric pumps or motors - Google Patents

Eccentric drive mechanism for volumetric pumps or motors Download PDF

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Publication number
EP1651866B1
EP1651866B1 EP04740680.6A EP04740680A EP1651866B1 EP 1651866 B1 EP1651866 B1 EP 1651866B1 EP 04740680 A EP04740680 A EP 04740680A EP 1651866 B1 EP1651866 B1 EP 1651866B1
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Prior art keywords
stroke
mount
channel
lubricating fluid
pressure
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EP04740680.6A
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German (de)
French (fr)
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EP1651866A1 (en
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Bernhard Frey
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Frey Bernhard
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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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • 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
    • F04B1/0404—Details or component parts
    • F04B1/0413—Cams
    • 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
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • F04B27/0414—Cams

Definitions

  • the invention relates to an eccentric drive for volumetrically unidirectional acting pumps.
  • Eccentric engines are known in the art.
  • a with a shaft of a crank mechanism rotatably connected with a lifting member with respect to an axis of this shaft eccentric stroke bearing can be designed as a crank pin a conventional crankshaft, a coupling member as a connecting rod and a pressure member as a piston which is pivotally connected to the connecting rod by a piston pin.
  • a crank pin / connecting rod bearing and a piston pin bearing together again form a bearing with a translational, directed transversely to the degree of freedom, ie a transverse bearing.
  • a channel or a bore system is considered, which extends, starting from a pressure source, through the crankshaft and the connecting rod to the piston pin.
  • This lubricating fluid supply also passes through the crankpin / connecting rod bearing, that is, by the rod bearing.
  • the bearing encompassing, groove-shaped Recesses provided in the storage areas. Now prevail in the respective high-pressure phase between the bearing surfaces of the transverse bearing, at least in addition to continuous relative rotational movements, in important constructions exclusively, oscillating states of motion with stoppages that virtually do not allow the construction of sufficiently viable hydrodynamic lubricating films.
  • the object of the invention is therefore to provide a Exzentertriebmaschinees, which is characterized in terms of storage by effective and safe lubrication and lubrication pressure maintenance.
  • An essential feature of the invention is that the cavity assembly is arranged in a bearing surface of a lifting member which extends over at least a portion of the corresponding low pressure phase, peripheral portion of the lifting member and at least partially has a distance extending from the edges of this bearing surface boundary.
  • the purpose of the same optimization purpose is to provide the cavity assembly with at least one cavity in the form of a groove extending at most over a semicircular peripheral portion of the lifting member.
  • the cavity arrangement comprises not only one but a plurality of circumferentially and / or axially staggered cavities arranged in each case communicating with the lubricating fluid system.
  • This allows comparatively large cross sections for the lubricating fluid flow with nevertheless reliable sealing against undesired backflow.
  • Another essential development of the inventive concept provides that the cavity arrangement in a front or rear circumferential angular distance of front and / or rear with respect to the rotational direction of the low pressure phase corresponding peripheral portion the lifting member is limited. This allows in certain applications expedient phase shifts of the beginning or the end of the lubricant supply to the transverse storage.
  • phase shifts and / or changes in the pressure gradient over time due to the compressibility of a working medium can be taken into account.
  • positive as well as negative angular distances with respect to the geometric dead or reversal points of the eccentric engine come into question.
  • a 5-cylinder pump with driven by a shaft (W) cylinder-piston units (Z1, Z2, Z3, Z4, Z5), the concentric to an axis (XX) of the shaft (W) and evenly distributed over the circumference are arranged.
  • a central housing (GZ) is still an individual to be displayed eccentric.
  • a drive torque is initiated by a motor, not shown, via a stub shaft (WS).
  • This in Fig. 3 and Fig. 4 shown eccentric engine comprises a with the shaft (W) non-rotatably connected lifting member (HG) having a relative to the axis (XX) of the shaft (W) eccentric stroke bearing (HL).
  • the stroke bearing (HL) does not connect the lifting member (HG) with one at the rotational movement participating coupling element (KG), which in turn is connected by a transverse bearing (QL) with a pressure member (DG) for the oscillating conveyor drive a piston-cylinder unit.
  • the lifting member (HG) is a simple eccentric disc which is non-rotatably mounted on the shaft (W) or formed integrally therewith.
  • the lifting member (HG) forms at its outer periphery a bearing surface (L1) which sits in a corresponding, cylindrical bearing surface (L2) of the coupling member (KG) and thus forms the stroke bearing (HL). Accordingly, the construction does not have a pronounced crankshaft despite the multi-cylinder arrangement.
  • the pressure member (DG) is formed in the example as in a housing (GH) radially to the shaft (W) displaceably mounted bush in which a working pressure under pressure piston (KO) sits.
  • This piston (KO) presses a substantially or approximately flat lower end face (F1) of the pressure member (DG) with great forces against a flat seat surface (F2) of the coupling member (KG).
  • the surfaces F1 and F2 form the transverse bearing (QL) as bearing surfaces. They are subject only translational sliding relative to each other. If appropriate, the piston (KO) can form the said bearing surface of the transverse bearing (QL) even with a lower end face.
  • a pressure-conveying source (DQ) for a lubricating fluid is provided, which is connected on the output side by a channel system with the transverse bearing (QL).
  • the channel system comprises a first channel (K1) extending through the lifting member (HG) into the stroke bearing (HL) and at least one of this stroke bearing (HL) through the coupling member (KG ) in the transverse bearing (QL) extending second channel (K2).
  • a cavity arrangement for forwarding the lubricating fluid to at least one second channel (K2) is provided within a bearing surface (L1) connected to the lifting member (HG), and this cavity arrangement has inside the bearing surface (L1) and in Circumferential direction of the lifting member (HG) at least approximately an arrangement and / or extent that a lubricating fluid flow between the first channel (K1) and second channel (K2) each only within a low pressure phase of the lubricating fluid in the stroke bearing (HL) or the transverse bearing (QL) permits.
  • This construction or arrangement thus acts in the sense of a push valve control, which prevents undesirable backflow of the lubricating fluid in the high pressure phases of the transverse bearing (QL), but ensures adequate filling of the gap of the transverse bearing with lubricating fluid in the low pressure phases.
  • the eccentric has the cavity arrangement in the bearing surface (L1) of the lifting member (HG).
  • This cavity arrangement extends over at least a portion of a peripheral portion (UN) of the lifting member (HG) corresponding to the low-pressure phase of the eccentric thruster and has, at least in sections, a boundary running away from edges of this bearing surface (L1). This improves the reverse flow blocking effect.
  • the construction is specially designed such that the cavity arrangement has at least one cavity in the form of a groove which extends at most over a semicircular peripheral portion of the lifting member (HG).
  • the cavity arrangement may comprise a plurality of circumferentially and / or axially of the lifting member (HG) offset from each other arranged cavities, which are each in communication with the lubricating fluid system. This allows comparatively large cross sections for the flow of the lubricating fluid while still reliable sealing against unwanted backflow.
  • the cavity assembly may be further limited in a front or rear circumferential angular distance (av or ah) from the front and / or rear end with respect to the rotational direction corresponding to the low pressure phase peripheral portion (UN) of the lifting member.
  • av or ah circumferential angular distance from the front and / or rear end with respect to the rotational direction corresponding to the low pressure phase peripheral portion (UN) of the lifting member.
  • QL transverse bearing
  • the amount of such a phase shift is generally conveniently limited to a value of about 10 ° - positive or negative.

Description

Die Erfindung betrifft ein Exzentertriebwerk für volumetrisch unidirektional wirkende Pumpen.The invention relates to an eccentric drive for volumetrically unidirectional acting pumps.

Exzentertriebwerke sind im Stand der Technik bekannt. Ein mit einer Welle eines Kurbeltriebes drehfest verbundenes Hubglied mit einer bezüglich einer Achse dieser Welle exzentrischen Hublagerung kann zum Beispiel als Kurbelzapfen einer üblichen Kurbelwelle, ein Koppelglied als Pleuel und ein Druckglied als Kolben ausgebildet sein, der mit dem Pleuel durch einen Kolbenbolzen schwenkbar verbunden ist. Ein Kurbelzapfen/Pleuellager und ein Kolbenbolzenlager bilden zusammen wiederum eine Lagerung mit einem translatorischen, quer zum Hub gerichteten Freiheitsgrad, also eine Querlagerung. Für eine Schmierfluidzuführung zur Querlagerung kommt dann ein Kanal bzw. ein Bohrungssystem in Betracht, das sich, ausgehend von einer Druckförderquelle, durch die Kurbelwelle und das Pleuel zum Kolbenbolzen erstreckt. Diese Schmierfluidzuführung verläuft auch durch das Kurbelzapfen/Pleuellager, das heisst, durch die Hublagerung. Im Interesse der Einspeisung und Verteilung von Schmierfluid in der Niederdruckphase für die anschliessende, hydrodynamische Bildung eines Schmierfilms in einer Hochdruckphase durch RelativDrehbewegung zwischen den Lagerflächen werden bekanntermassen entsprechend gross bemessenen, das Lager umgreifende, nutförmige Aussparungen in den Lagerflächen vorgesehen. Nun herrschen in der jeweiligen Hochdruckphase zwischen den Lagerflächen der Querlagerung, mindestens neben kontinuierlichen Relativ-Drehbewegungen, bei wichtigen Konstruktionen jedoch ausschliesslich, oszillierende Bewegungszustände mit Stillständen, die einen Aufbau von ausreichend tragfähigen hydrodynamischen Schmierfilmen praktisch nicht zulassen. In diesen Bereichen kommt es darauf an, nicht nur ein ausreichendes Schmierstoffpolster in den Niederdruckphasen in den Lagerspalt einzubringen - dies erfolgt über das mit der Querlagerung in Verbindung stehende Hublager - sondern dieses Polster in den Hochdruckphasen nicht zu rasch abfliessen zu lassen. Dieser Abfluss kann wiederum über das Hublager erfolgen. Wegen der oben erwähnten Aussparungen in den Lagerflächen des Hublagers sind die bekannten Exzentertriebwerke im Hinblick auf diese erwünschte Schmierdruckhaltung verbesserungsbedürftig.Eccentric engines are known in the art. A with a shaft of a crank mechanism rotatably connected with a lifting member with respect to an axis of this shaft eccentric stroke bearing can be designed as a crank pin a conventional crankshaft, a coupling member as a connecting rod and a pressure member as a piston which is pivotally connected to the connecting rod by a piston pin. A crank pin / connecting rod bearing and a piston pin bearing together again form a bearing with a translational, directed transversely to the degree of freedom, ie a transverse bearing. For a lubricating fluid supply to the transverse bearing then a channel or a bore system is considered, which extends, starting from a pressure source, through the crankshaft and the connecting rod to the piston pin. This lubricating fluid supply also passes through the crankpin / connecting rod bearing, that is, by the rod bearing. In the interest of the supply and distribution of lubricating fluid in the low pressure phase for the subsequent hydrodynamic formation of a lubricating film in a high pressure phase by relative rotational movement between the bearing surfaces are known to be correspondingly large sized, the bearing encompassing, groove-shaped Recesses provided in the storage areas. Now prevail in the respective high-pressure phase between the bearing surfaces of the transverse bearing, at least in addition to continuous relative rotational movements, in important constructions exclusively, oscillating states of motion with stoppages that virtually do not allow the construction of sufficiently viable hydrodynamic lubricating films. In these areas, it is important to not only introduce a sufficient lubricant cushion in the low-pressure phases in the bearing gap - this is done via the associated with the transverse bearing rod bearings - but this cushion in the high pressure phases not to drain too quickly. This outflow can in turn be done via the stroke bearing. Because of the above-mentioned recesses in the bearing surfaces of the stroke bearing the known Exzentertriebwerke are in need of improvement in view of this desired lubrication pressure maintenance.

Aus der US-4,132,510-A ist ein Exzentertriebwerk bekannt. Dieses Exzentertriebwerk, das im Übrigen für einen Gaskompressor bestimmt ist und bidirektional wirken kann, weist gewisse Merkmale des erfindungsgemässen Exzentertriebwerks auf, unterscheidet sich aber durch eine andere Konstruktion insbesondere des Mündungsbereichs des ersten Kanals in die Hublagerung, wobei dieser lediglich durch eine kleinflächige Abplattung des Hubgliedes gebildet ist, die sich längs einem sehr beschränkten Umfangswinkelbereich erstreckt. Diese Abplattung dient nur dazu, den Zustrom des Schmierfluids zu ermöglichen.From the US-4,132,510-A is known an eccentric engine. This Exzentertriebwerk, which is otherwise intended for a gas compressor and can act bidirectionally, has certain features of the inventive Exzententriebwerks, but differs by another design, in particular the mouth region of the first channel in the stroke storage, this only by a small area flattening of the lifting member is formed, which extends along a very limited circumferential angular range. This flattening serves only to allow the influx of lubricating fluid.

In Anlehnung an den Wortlaut des Anspruchs 1 unterscheidet sich die vorliegende Erfindung vom Stand der Technik nach US-4,132,510 A

  • durch eine unidirektional wirkende Pumpe,
  • durch die Hohlraumanordnung, die sich über einen wesentlichen Teil des - der gesamten Niederdruckphase des Exzentertriebwerks entsprechenden - Halbkreis-Umfangsabschnitts des Hubgliedes erstreckt, so daß das Durchströmen des Schmierfluids zwischen dem mindestens einen ersten Kanal und dem mindestens einen zweiten Kanal jeweils während eines wesentlichen Teils der gesamten Niederdruckphase des Schmierfluids in der Hublagerung bzw. in der Querlagerung stattfindet, und eine Rückströmung des Schmierfluids in einer folgenden Hochdruckphase unterbunden ist, weiter
  • durch die Hohlraumanordnung, die einen Hohlraum in Form einer Nut aufweist, die sich innerhalb der Niederdruckphase des Exzentertriebwerks entsprechenden Halbkreis-Umfangsabschnitts des Hubgliedes und
höchstens längs der Niederdruckphase des Exzentertriebwerks entsprechenden Halbkreis-Umfangsabschnitt des Hubgliedes erstreckt.Based on the wording of claim 1, the present invention differs from the prior art US 4,132,510 A
  • by a unidirectionally acting pump,
  • by the cavity assembly extending over a substantial portion of the - the entire low-pressure phase of the Exzententriebwerks - semicircular peripheral portion of the lifting member, so that the passage of the lubricating fluid between the at least one first channel and the at least one second channel each during a substantial part of the entire low-pressure phase of the lubricating fluid in the stroke storage or in the transverse storage takes place, and a back flow of the lubricating fluid is prevented in a subsequent high-pressure phase, on
  • through the cavity assembly, which has a cavity in the form of a groove, which within the low-pressure phase of the Exzententriebwerks corresponding semicircular peripheral portion of the lifting member and
at most along the low pressure phase of the Exzententriebwerks corresponding semicircular peripheral portion of the lifting member extends.

Aufgabe der Erfindung ist daher die Schaffung eines Exzentertriebwerkes, das sich hinsichtlich der Lagerung durch wirksame und sichere Schmierung und Schmierdruckhaltung auszeichnet.The object of the invention is therefore to provide a Exzentertriebwerkes, which is characterized in terms of storage by effective and safe lubrication and lubrication pressure maintenance.

Die Lösung dieser Aufgabe ist erfindungsgemäss bestimmt durch die Merkmale des Patentanspruchs 1. Bevorzugte Einzelheiten und Weiterbildungen des erfindungsgemässen Exzentertriebwerkes sind durch die abhängigen Patentansprüche 2 bis 4 definiert.The solution of this problem is inventively determined by the features of claim 1. Preferred details and further developments of the inventive Exzentertriebwerkes are defined by the dependent claims 2 to 4.

Im Kombinationszusammenhang der Lösungsmerkmale des Anspruchs 1 kommt es unter anderem darauf an, dass eine Strömungsverbindung zwischen der Querlagerung und einem Kanalsystem der Zuführung von Schmierfluid in der Hochdruckphase jeweils durch nicht unterbrochene Lagerflächen der Hublagerung verschlossen und damit eine unerwünschte Rückströmung des Schmierfluids unterbunden ist.In the combination context of the solution features of claim 1, it depends, inter alia, that a flow connection between the Transverse storage and a channel system of the supply of lubricating fluid in the high pressure phase in each case closed by uninterrupted bearing surfaces of the stroke bearing and thus an undesirable backflow of the lubricating fluid is prevented.

Es ist hervorzuheben, dass nicht nur bei Hochdruckpumpen sondern auch bei entsprechenden Motoren, die statt einer ausgeprägten Kurbelwelle nur eine Exzenterscheibe oder mehrere derselben sowie entsprechende Exzenterkulissen mit rein translatorischer Gleitbewegung gegenüber auf diesen Kulissen aufsitzenden Druckgliedern aufweisen, durch die Erfindung eine zuverlässige Gleitschmierung und damit ein Hochdruckbetrieb mit annehmbarem mechanischem Wirkungsgrad ermöglicht wird.It should be emphasized that not only in high-pressure pumps but also in corresponding engines, which instead of a pronounced crankshaft only one eccentric or more of them and corresponding eccentric with purely translational sliding relative to these scenes seated pressure members, by the invention, a reliable sliding lubrication and thus High pressure operation with acceptable mechanical efficiency is possible.

Ein wesentliches Merkmal der Erfindung besteht darin, dass die Hohlraumanordnung in einer Lagerfläche eines Hubgliedes angeordnet ist, die sich über mindestens einen Teil eines, der Niederdruckphase entsprechenden, Umfangsabschnitts des Hubgliedes erstreckt und wenigstens abschnittsweise eine mit Abstand von den Rändern dieser Lagerfläche verlaufende Begrenzung aufweist. Dadurch wird eine besonders wirksame Abdichtung der Hohlraumanordnung gegen Schmierfluid-Rückströmung erreicht. Dem gleichen Optimierungszweck dient die Ausbildung, derzufolge die Hohlraumanordnung mindestens einen Hohlraum in Form einer sich höchstens über einen Halbkreis-Umfangsabschnitt des Hubgliedes erstreckenden Nut aufweist.An essential feature of the invention is that the cavity assembly is arranged in a bearing surface of a lifting member which extends over at least a portion of the corresponding low pressure phase, peripheral portion of the lifting member and at least partially has a distance extending from the edges of this bearing surface boundary. As a result, a particularly effective sealing of the cavity assembly against lubricating fluid return flow is achieved. The purpose of the same optimization purpose is to provide the cavity assembly with at least one cavity in the form of a groove extending at most over a semicircular peripheral portion of the lifting member.

In gewissen Anwendungen kommt eine Weiterbildung in Betracht, derzufolge die Hohlraumanordnung nicht nur einen, sondern eine Mehrzahl von im Umfang und/oder Axialrichtung gegeneinander versetzt angeordneten Hohlräumen umfasst, die jeweils mit dem Schmierfluidsystem in Verbindung stehen. Dies ermöglicht vergleichsweise grosse Querschnitte für die Schmierfluidströmung bei gleichwohl zuverlässiger Abdichtung gegen unerwünschte Rückströmung.
Eine ebenfalls wesentliche Weiterbildung der Erfindungsgedanken sieht vor, dass die Hohlraumanordnung in einem vorderen bzw. rückwärtigen Umfangswinkelabstand von bezüglich der Drehrichtung vorderen und/oder rückwärtigen Ende des der Niederdruckphase entsprechenden Umfangsabschnitts des Hubgliedes begrenzt ist. Dies ermöglicht in gewissen Anwendungen zweckmässige Phasenverschiebungen des Beginns bzw. des Endes der Schmiermittelzuführung zur Querlagerung. Damit kann gegebenenfalls auftretenden Phasenverschiebungen und/oder Änderungen des zeitlichen Druckgradienten infolge Kompressibilität eines Arbeitsmediums Rechnung getragen werden. Dabei kommen grundsätzlich positive wie auch negative Winkelabstände bezüglich der geometrischen Tot- oder Umkehrpunkte des Exzentertriebwerkes in Frage.In certain applications, a further development is contemplated, according to which the cavity arrangement comprises not only one but a plurality of circumferentially and / or axially staggered cavities arranged in each case communicating with the lubricating fluid system. This allows comparatively large cross sections for the lubricating fluid flow with nevertheless reliable sealing against undesired backflow.
Another essential development of the inventive concept provides that the cavity arrangement in a front or rear circumferential angular distance of front and / or rear with respect to the rotational direction of the low pressure phase corresponding peripheral portion the lifting member is limited. This allows in certain applications expedient phase shifts of the beginning or the end of the lubricant supply to the transverse storage. In this way, possibly occurring phase shifts and / or changes in the pressure gradient over time due to the compressibility of a working medium can be taken into account. In principle, positive as well as negative angular distances with respect to the geometric dead or reversal points of the eccentric engine come into question.

Die Erfindung wird weiter unter Bezugnahme auf ein in den Zeichnungen schematisch dargestelltes Ausführungsbeispiel erläutert. Darin zeigen:

Fig. 1
als bevorzugtes Anwendungsbeispiel der Erfindung eine Radialkolbenmaschine in Axialansicht;
Fig. 2
die in Fig. 1 gezeigte Radialkolbenmaschine in Radialansicht;
Fig. 3
einen in grösserem Massstab gehaltenen, quer zur Hauptwelle orientierten Teilschnitt des Exzentertriebwerkes der in Fig. 1 und Fig. 2 gezeigten Radialkolbenmaschine; und
Fig. 4
einen Teil-Axialschnitt des Exzentertriebwerkes mit einem teilweise angedeuteten Radial-Druckglied und zugehörigem Kolben sowie Zylinder.
The invention will be further explained with reference to an embodiment schematically illustrated in the drawings. Show:
Fig. 1
as a preferred embodiment of the invention, a radial piston machine in axial view;
Fig. 2
in the Fig. 1 Radial piston machine shown in radial view;
Fig. 3
a larger scale, oriented transverse to the main shaft section of the Exzentertriebwerkes in Fig. 1 and Fig. 2 shown radial piston machine; and
Fig. 4
a partial axial section of the Exzentertriebwerkes with a partially indicated radial pressure member and associated piston and cylinder.

Bei der Radialkolbenmaschine nach Fig. 1 und Fig. 2 handelt es sich um eine 5-Zylinderpumpe mit von einer Welle (W) angetriebenen Zylinder-Kolbeneinheiten (Z1, Z2, Z3, Z4, Z5), die konzentrische zu einer Achse (XX) der Welle (W) und über deren Umfang gleichmässig verteilt angeordnet sind. In einem Zentralgehäuse (GZ) befindet sich ein noch im Einzelnen darzustellendes Exzentertriebwerk. Ein Antriebsmoment wird von einem nicht dargestellten Motor über einen Wellenstummel (WS) eingeleitet.At the radial piston machine after Fig. 1 and Fig. 2 it is a 5-cylinder pump with driven by a shaft (W) cylinder-piston units (Z1, Z2, Z3, Z4, Z5), the concentric to an axis (XX) of the shaft (W) and evenly distributed over the circumference are arranged. In a central housing (GZ) is still an individual to be displayed eccentric. A drive torque is initiated by a motor, not shown, via a stub shaft (WS).

Das in Fig. 3 und Fig. 4 dargestellte Exzentertriebwerk umfasst ein mit der Welle (W) drehfest verbundenes Hubglied (HG), das eine bezüglich der Achse (XX) der Welle (W) exzentrische Hublagerung (HL) aufweist. Die Hublagerung (HL) verbindet das Hubglied (HG) mit einem an der Drehbewegung nicht teilnehmenden Kuppelglied (KG), das seinerseits durch eine Querlagerung (QL) mit einem Druckglied (DG) für den oszillierenden Förderantrieb einer Kolbenzylindereinheit verbunden ist. Bei dem vorliegenden, bevorzugten Anwendungsbeispiel ist das Hubglied (HG) eine einfache Exzenterscheibe, die drehfest auf der Welle (W) sitzt oder mit dieser einstückig ausgebildet ist. Das Hubglied (HG) bildet an seinem äusserem Umfang eine Lagerfläche (L1), die in einer entsprechenden, zylindrischen Lagerfläche (L2) des Koppelgliedes (KG) sitzt und damit die Hublagerung (HL) bildet. Demgemäss besitzt die Konstruktion trotz Mehrzylinderanordnung keine ausgeprägte Kurbelwelle.This in Fig. 3 and Fig. 4 shown eccentric engine comprises a with the shaft (W) non-rotatably connected lifting member (HG) having a relative to the axis (XX) of the shaft (W) eccentric stroke bearing (HL). The stroke bearing (HL) does not connect the lifting member (HG) with one at the rotational movement participating coupling element (KG), which in turn is connected by a transverse bearing (QL) with a pressure member (DG) for the oscillating conveyor drive a piston-cylinder unit. In the present, preferred application example, the lifting member (HG) is a simple eccentric disc which is non-rotatably mounted on the shaft (W) or formed integrally therewith. The lifting member (HG) forms at its outer periphery a bearing surface (L1) which sits in a corresponding, cylindrical bearing surface (L2) of the coupling member (KG) and thus forms the stroke bearing (HL). Accordingly, the construction does not have a pronounced crankshaft despite the multi-cylinder arrangement.

Das Druckglied (DG) ist im Beispiel als in einem Gehäuse (GH) radial zur Welle (W) verschiebbar gelagerte Büchse ausgebildet, in der ein unter Arbeitsdruck stehender Kolben (KO) sitzt. Dieser Kolben (KO) presst eine im Wesentlichen oder annähernd ebene untere Stirnfläche (F1) des Druckgliedes (DG) mit grossen Kräften gegen eine ebene Sitzfläche (F2) des Koppelgliedes (KG). Die Flächen F1 und F2 bilden als Lagerflächen die Querlagerung (QL). Sie unterliegen ausschliesslich translatorischen Gleitbewegungen relativ zueinander. Gegebenen falls kann der Kolben (KO) selbst mit einer unteren Stirnfläche die genannte Lagerfläche der Querlagerung (QL) bilden.The pressure member (DG) is formed in the example as in a housing (GH) radially to the shaft (W) displaceably mounted bush in which a working pressure under pressure piston (KO) sits. This piston (KO) presses a substantially or approximately flat lower end face (F1) of the pressure member (DG) with great forces against a flat seat surface (F2) of the coupling member (KG). The surfaces F1 and F2 form the transverse bearing (QL) as bearing surfaces. They are subject only translational sliding relative to each other. If appropriate, the piston (KO) can form the said bearing surface of the transverse bearing (QL) even with a lower end face.

Des Weiteren ist eine Druckförderquelle (DQ) für ein Schmierfluid vorgesehen, die ausgangsseitig durch ein Kanalsystem mit der Querlagerung (QL) verbunden ist. Ausgehend von einem mit der Druckförderquelle (DQ) verbundenen Anschlusskanal (KA) umfasst das Kanalsystem einen durch das Hubglied (HG) in die Hublagerung (HL) verlaufenden ersten Kanal (K1) und mindestens einen von dieser Hublagerung (HL) durch das Koppelglied (KG) in die Querlagerung (QL) verlaufenden zweiten Kanal (K2).Furthermore, a pressure-conveying source (DQ) for a lubricating fluid is provided, which is connected on the output side by a channel system with the transverse bearing (QL). Starting from a connection channel (KA) connected to the pressure-conveying source (DQ), the channel system comprises a first channel (K1) extending through the lifting member (HG) into the stroke bearing (HL) and at least one of this stroke bearing (HL) through the coupling member (KG ) in the transverse bearing (QL) extending second channel (K2).

Im Bereich der Hublagerung (HL) ist innerhalb einer mit dem Hubglied (HG) verbundenen Lagerfläche (L1) eine Hohlraumanordnung für eine Weiterleitung des Schmierfluids zu mindestens einem zweiten Kanal (K2) vorgesehen, und diese Hohlraumanordnung hat innerhalb der Lagerfläche (L1) und in Umfangsrichtung des Hubgliedes (HG) wenigstens annähernd eine Anordnung und/oder Erstreckung, die eine Schmierfluiddurchströmung zwischen erstem Kanal (K1) und zweitem Kanal (K2) jeweils nur innerhalb einer Niederdruckphase des Schmierfluids in der Hublagerung (HL) bzw. der Querlagerung (QL) zulässt. Diese Konstruktion bzw. Anordnung wirkt somit im Sinne einer Schubventilsteuerung, die eine unerwünschte Rückströmung des Schmierfluids in den Hochdruckphasen der Querlagerung (QL) verhindert, jedoch eine ausreichende Füllung des Spaltes der Querlagerung mit Schmierfluid in den Niederdruckphasen sichert.In the area of the stroke bearing (HL), a cavity arrangement for forwarding the lubricating fluid to at least one second channel (K2) is provided within a bearing surface (L1) connected to the lifting member (HG), and this cavity arrangement has inside the bearing surface (L1) and in Circumferential direction of the lifting member (HG) at least approximately an arrangement and / or extent that a lubricating fluid flow between the first channel (K1) and second channel (K2) each only within a low pressure phase of the lubricating fluid in the stroke bearing (HL) or the transverse bearing (QL) permits. This construction or arrangement thus acts in the sense of a push valve control, which prevents undesirable backflow of the lubricating fluid in the high pressure phases of the transverse bearing (QL), but ensures adequate filling of the gap of the transverse bearing with lubricating fluid in the low pressure phases.

Im Einzelnen hat das Exzentertriebwerk die Hohlraumanordnung in der Lagerfläche (L1) des Hubgliedes (HG). Diese Hohlraumanordnung erstreckt sich über mindestens einen Teil eines der Niederdruckphase des Exzentertriebwerkes entsprechenden Umfangsabschnitt (UN) des Hubgliedes (HG) und weist wenigstens abschnittsweise eine mit Abstand von Rändern dieser Lagerfläche (L1) verlaufende Begrenzung auf. Dies verbessert die Rückstrom-Sperrwirkung. Im Ausführungsbeispiel gemäss Fig. 3 ist die Konstruktion speziell so gestaltet, dass die Hohlraumanordnung mindestens einen Hohlraum in Form einer sich höchstens über einen Halbkreis-Umfangsabschnitt des Hubgliedes (HG) erstreckenden Nut aufweist. Gegebenen falls kann die Hohlraumanordnung eine Mehrzahl von in Umfangs- und/oder Axialrichtung des Hubgliedes (HG) gegeneinander versetzt angeordneten Hohlräumen umfassen, die jeweils mit dem Schmierfluidsystem in Verbindung stehen. Dies ermöglicht vergleichsweise grosse Querschnitte für die Strömung des Schmierfluids bei gleichwohl zuverlässiger Abdichtung gegen unerwünschte Rückströmung.Specifically, the eccentric has the cavity arrangement in the bearing surface (L1) of the lifting member (HG). This cavity arrangement extends over at least a portion of a peripheral portion (UN) of the lifting member (HG) corresponding to the low-pressure phase of the eccentric thruster and has, at least in sections, a boundary running away from edges of this bearing surface (L1). This improves the reverse flow blocking effect. In the embodiment according to Fig. 3 the construction is specially designed such that the cavity arrangement has at least one cavity in the form of a groove which extends at most over a semicircular peripheral portion of the lifting member (HG). If appropriate, the cavity arrangement may comprise a plurality of circumferentially and / or axially of the lifting member (HG) offset from each other arranged cavities, which are each in communication with the lubricating fluid system. This allows comparatively large cross sections for the flow of the lubricating fluid while still reliable sealing against unwanted backflow.

Die Hohlraumanordnung kann ferner in einem vorderen bzw. rückwärtigen Umfangswinkelabstand (av bzw. ah) vom bezüglich der Drehrichtung vorderen und/oder rückwärtigen Ende des der Niederdruckphase entsprechenden Umfangsabschnitt (UN) des Hubgliedes begrenzt ausgebildet werden. Dies ermöglicht eine Phasenverschiebung des Beginns bzw. Endes der Zuführung des Schmiermittels zur Querlagerung (QL). Der Betrag einer solchen Phasenverschiebung wird im Allgemeinen zweckmässig auf einen Wert von etwa 10° - positiv oder negativ - beschränkt.The cavity assembly may be further limited in a front or rear circumferential angular distance (av or ah) from the front and / or rear end with respect to the rotational direction corresponding to the low pressure phase peripheral portion (UN) of the lifting member. This allows a phase shift of the beginning or end of the supply of lubricant to the transverse bearing (QL). The amount of such a phase shift is generally conveniently limited to a value of about 10 ° - positive or negative.

Claims (4)

  1. An eccentric drive mechanism for volumetrically and unidirectionally acting pumps, comprising the following features:
    - at least one stroke element (HG)
    - which is connected in a rotationally-fixed manner to a shaft (W) of a crank drive, which contains an axis (XX), and
    - which has at least one eccentric stroke mount (HL) with respect to the axis (XX) of the shaft (W);
    - a coupling element (KG), which is connected by the stroke mount (HL) to the stroke element (HG), wherein the coupling element (KG)
    - does not participate in the rotational movement and
    - is in turn connected by a transverse mount (QL) to at least one pressure element (DG) for an oscillating delivery drive of at least one piston/cylinder unit of the pump;
    - at least one pressure delivery source (DQ) for a lubricating fluid, which is connected on the outlet side to the transverse mount (QL),
    - a channel system, which
    - connects the pressure delivery source (DQ) to the transverse mount (QL),
    - proceeding from a connection channel (KA) connected to the pressure delivery source (DQ), comprises:
    - at least one first channel (K1), which extends through the stroke element (HG) in the stroke mount (HL), and
    - at least one second channel (K2), which extends from this stroke mount (HL) through the coupling element (KG) in the transverse mount (QL),
    - a cavity arrangement,
    - which is provided in the region of the stroke mount (HL) inside a bearing surface (L1) connected to the stroke element (HG) for relaying the lubricating fluid to the at least one second channel (K2),
    - which at least approximately has an arrangement and/or extension, inside the bearing surface (L1) and in the circumferential direction of the stroke element (HG), which permits through flow of the lubricating fluid between the at least one first channel (K1) and the at least one second channel (K2),
    wherein the cavity arrangement
    - extends over a substantial part of the semicircular circumferential section (UN) - corresponding to the entire low-pressure phase of the eccentric drive mechanism - of the stroke element (HG), so that
    the through flow of the lubricating fluid between the at least one first channel (K1) and the at least one second channel (K2) respectively occurs during a substantial part of the entire low-pressure phase of the lubricating fluid in the stroke mount (HL) or in the transverse mount (QL),
    and a reverse flow of the lubricating fluid in a following high-pressure phase is prevented,
    - at least sectionally has a delimitation which extends at a distance from the edges of this bearing surface (L1), and
    - has at least one cavity in the form of a groove (HKN), which extends inside the semicircular circumferential section (UN) of the stroke element (HG) corresponding to the low-pressure phase of the eccentric drive mechanism and at most along the semicircular circumferential section (UN) of the stroke element (HG) corresponding to the low-pressure phase of the eccentric drive mechanism.
  2. The eccentric drive mechanism according to Claim 1, characterized in that the cavity arrangement comprises further cavities, wherein the cavities
    - are arranged offset to one another in the circumferential and/or axial direction of the stroke element (HG) and
    - are connected to the pressure delivery source (DQ) with one another or separately.
  3. The eccentric drive mechanism according to Claim 1, characterized in that the cavity arrangement is delimited in a front circumferential angle spacing (av) and/or a rear circumferential angle spacing (ah) from the front or rear end, respectively, with respect to the rotational direction of a circumferential direction (UN) of the stroke element (HG) corresponding to the low-pressure phase (HG).
  4. The eccentric drive according to Claim 3, characterized in that the front circumferential angle spacing (av) and/or the rear circumferential angle spacing of the cavity arrangement is at most 10°.
EP04740680.6A 2003-07-07 2004-07-06 Eccentric drive mechanism for volumetric pumps or motors Active EP1651866B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL04740680T PL1651866T3 (en) 2003-07-07 2004-07-06 Eccentric drive mechanism for volumetric pumps or motors

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10330757A DE10330757A1 (en) 2003-07-07 2003-07-07 Eccentric drive for volumetric pumps or motors
PCT/EP2004/007352 WO2005003558A1 (en) 2003-07-07 2004-07-06 Eccentric drive mechanism for volumetric pumps or motors

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EP1651866A1 EP1651866A1 (en) 2006-05-03
EP1651866B1 true EP1651866B1 (en) 2014-03-05

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US (1) US7441492B2 (en)
EP (1) EP1651866B1 (en)
JP (1) JP2007526958A (en)
CN (1) CN1846058B (en)
CA (1) CA2540721C (en)
DE (1) DE10330757A1 (en)
ES (1) ES2460954T3 (en)
NO (1) NO338172B1 (en)
PL (1) PL1651866T3 (en)
RU (1) RU2354847C2 (en)
WO (1) WO2005003558A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2003281906A1 (en) * 2003-02-11 2004-09-06 Ganser-Hydromag Ag High pressure pump
DE102008042380A1 (en) 2008-09-26 2010-04-01 Robert Bosch Gmbh Eccentric drive mechanism for fuel-high pressure pump for engine, has piston operatively connected with rotatably mounted eccentric by sliding bearing element that is tiltably arranged relative to piston
DE102008042378A1 (en) 2008-09-26 2010-04-01 Robert Bosch Gmbh Eccentric cam engine, particularly for high-pressure fuel pump, has rotatably mounted eccentric cam, where piston interacts with eccentric cam, and multiple roller elements are provided in roller bearing
US8926298B2 (en) * 2012-01-04 2015-01-06 Husco International, Inc. Hydraulic piston pump with a variable displacement throttle mechanism
CN103047100A (en) * 2013-01-10 2013-04-17 无锡开普机械有限公司 Rotor pump with cam shaft sleeve
CN103967743A (en) * 2013-01-29 2014-08-06 王彦彬 Magnetic coplanar multi-cylinder multi-level combining compressor
CN103967745A (en) * 2013-01-30 2014-08-06 王彦彬 Coplanar multi-cylinder multi-stage cam combined compressor

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB740784A (en) * 1953-08-17 1955-11-16 Lucas Industries Ltd Reciprocatory pumps
GB884556A (en) * 1958-06-18 1961-12-13 Hobourn Eaton Mfg Co Ltd Improvements in reciprocating liquid pumps of positive displacement type
US3093301A (en) * 1960-07-05 1963-06-11 Mitchell Co John E Lubricating system for compressor
DE1653632A1 (en) * 1967-03-25 1971-09-16 Teves Gmbh Alfred Radial piston pump
US3456874A (en) * 1967-08-01 1969-07-22 Eaton Yale & Towne Cam driven compressor
US4132510A (en) 1976-06-09 1979-01-02 Sampei Komiya Compressor
JPS543604U (en) * 1977-06-13 1979-01-11
DE3039197C2 (en) * 1980-10-17 1986-07-17 Mannesmann Rexroth GmbH, 8770 Lohr Hydrostatic radial piston pump
US4567815A (en) * 1984-12-04 1986-02-04 Vilter Manufacturing Corporation Connecting rod and bearing assembly therefor
DE4126640B4 (en) * 1991-08-12 2005-06-16 Robert Bosch Gmbh Pump arrangement with a prefeed pump and a radial piston pump
GB9117975D0 (en) * 1991-08-20 1991-10-09 Collins Motor Corp Ltd Interconnecting rotary and reciprocating motion
JP2783381B2 (en) * 1993-11-05 1998-08-06 松下冷機株式会社 Hermetic compressor
KR0153343B1 (en) * 1995-10-13 1999-03-20 김광호 Reciprocating compressor
JPH1089255A (en) * 1996-09-10 1998-04-07 Hitachi Ltd Hermetic motor-driven compressor
DE19906626A1 (en) * 1998-10-06 2000-04-13 Mannesmann Rexroth Ag Pump arrangement with high pressure radial piston pump having eccentric drive has piston unit hydraulically biased against eccentric ring in application position by resulting pressure

Also Published As

Publication number Publication date
ES2460954T3 (en) 2014-05-16
JP2007526958A (en) 2007-09-20
CA2540721C (en) 2011-11-22
CN1846058A (en) 2006-10-11
CN1846058B (en) 2010-04-21
NO338172B1 (en) 2016-08-01
WO2005003558A1 (en) 2005-01-13
RU2006103487A (en) 2006-06-10
NO20051157L (en) 2005-04-15
US20060245940A1 (en) 2006-11-02
DE10330757A1 (en) 2005-02-03
RU2354847C2 (en) 2009-05-10
CA2540721A1 (en) 2005-01-13
PL1651866T3 (en) 2014-08-29
EP1651866A1 (en) 2006-05-03
US7441492B2 (en) 2008-10-28

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