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EP1651866A1 - Eccentric drive mechanism for volumetric pumps or motors - Google Patents

Eccentric drive mechanism for volumetric pumps or motors

Info

Publication number
EP1651866A1
EP1651866A1 EP04740680A EP04740680A EP1651866A1 EP 1651866 A1 EP1651866 A1 EP 1651866A1 EP 04740680 A EP04740680 A EP 04740680A EP 04740680 A EP04740680 A EP 04740680A EP 1651866 A1 EP1651866 A1 EP 1651866A1
Authority
EP
European Patent Office
Prior art keywords
bearing
lifting member
channel
stroke
pressure
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
EP04740680A
Other languages
German (de)
French (fr)
Other versions
EP1651866B1 (en
Inventor
Bernhard-Rudolf Frey
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.)
Frey Bernhard
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to PL04740680T priority Critical patent/PL1651866T3/en
Publication of EP1651866A1 publication Critical patent/EP1651866A1/en
Application granted granted Critical
Publication of EP1651866B1 publication Critical patent/EP1651866B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • 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 volumetric pumps or motors having the features of the preamble of claim 1. Such engines are known in the art.
  • the non-rotatably connected to the shaft of the crank gear lifting member with its with respect to the axis of this shaft eccentric stroke bearing can e.g. be designed as a crank pin of a conventional crankshaft, the coupling member as a connecting rod and the pressure member as a piston which is pivotally connected to the connecting rod by a piston pin.
  • the crank pin / connecting rod bearing and the Kolbolzenlager together again form a bearing with a translational, directed transversely to the degree of freedom, ie a transverse bearing.
  • a channel or bore system comes into consideration, 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 / conrod bearing, i. by the stroke storage.
  • the bearing encompassing, groove-shaped recesses are provided in the bearing surfaces.
  • the object of the invention is therefore to provide an eccentric, which is characterized in terms of storage by effective and safe lubrication and lubricating pressure maintenance.
  • the solution of this problem is determined by the features of claim 1. In the combination context of these solution features, it is important, inter alia, that the flow connection between the transverse bearing and the channel system of the lubricating fluid supply in the high-pressure phase respectively closed by the uninterrupted bearing surfaces of the rod bearing and thus an undesirable Return flow of the lubricating fluid is prevented.
  • the cavity arrangement is arranged in a bearing surface of the lifting member, which extends over at least part of the low-pressure phase of the Exzentertriebmaschines corresponding peripheral portion of the lifting member and at least partially has a distance extending from the edges of this bearing surface boundary.
  • the cavity arrangement has at least one cavity in the form of a groove which extends at most over a semicircular circumferential section of the lifting member is used for the same purpose of optimization.
  • the cavity assembly comprises a plurality of circumferentially and / or axially of the lifting member offset from each other arranged cavities, which are each in communication with the lubricating fluid system.
  • This allows comparatively large cross sections for the lubricating fluid flow with nevertheless reliable sealing against undesired backflow.
  • the cavity arrangement is limited in a front or rear circumferential angular distance from the front and / or rear end of the low pressure phase corresponding peripheral portion of the lifting member. This allows in certain applications expedient Phasenerschiebitch the beginning or the end of the lubricating fluid supply to the transverse storage.
  • phase shifts and / or changes in the pressure gradient over time due to the compressibility of the working medium can be taken into account.
  • positive as well as negative angular distances with respect to the geometrical dead center or reversal points of the eccentric engine come into consideration.
  • a 5-cylinder pump driven by a shaft (W) cylinder piston units (ZI) to (Z5), concentric with the axis (XX) of the shaft W and over its circumference are arranged evenly distributed.
  • the central housing (GZ) is still an eccentric engine to be displayed in detail.
  • the drive torque is initiated by a motor, not shown, via a stub shaft (WS).
  • the eccentric drive shown in Figures 3 and 4 comprises a with the shaft (W) rotatably connected lifting member (HG) having a relative to this axis (XX) of the shaft eccentric stroke bearing (HL).
  • the Hub ⁇ agerung (HL) connects the lifting member (HG) with a non-participating in the rotary motion coupling member (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 is a simple eccentric disc which is non-rotatably mounted on the shaft (W) or formed integrally therewith.
  • the lifting member forms at its outer periphery a bearing surface (Ll), which sits in a corresponding cylindrical bearing surface (L2) of the coupling member and thus forms a stroke bearing (HL). Accordingly, despite the multi-cylinder arrangement, the construction does not have a pronounced crankshaft.
  • the pressure member is formed in the example as in a housing (GH) radially to the shaft slidably mounted bush in which a standing under the working pressure piston (KO) sits.
  • the piston itself form with its lower end face the said bearing surface of the transverse bearing.
  • a pressure feed source (DQ) for 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 through the coupling member (KG) Transverse storage (QL) extending second channel (K2).
  • a cavity arrangement for the forwarding of the lubricating fluid to at least one second channel (K2) is provided within the bearing surface (L1) connected to the lifting member (HG), and this cavity arrangement has within the bearing surface (L1) and in Circumferential direction of the lifting member (HG) at least approximately an arrangement and / or extent that allows a lubricating fluid flow between the first and second channel respectively only within a low pressure phase of the lubricating fluid in the stroke bearing (HL) or the transverse bearing (QL).
  • This construction or arrangement thus acts in the sense of a push valve control, which prevents undesired backflow of the lubricating fluid in the high pressure phases of the transverse bearing, but ensures sufficient filling of the transverse bearing gap with lubricating fluid in the low pressure phases.
  • the eccentric has a cavity arrangement in a bearing surface (Ll) of the lifting member (HG).
  • This cavity arrangement extends over at least part of the low-pressure phase of the eccentric engine corresponding peripheral portion (UN) of the lifting member (HG) and has at least in sections a distance from the edges of this bearing surface (Ll) extending boundary.
  • the construction is specially designed such that the cavity arrangement has at least one cavity in the form of a groove (HKN) which extends at most over a semicircular peripheral portion of the lifting member.
  • the cavity assembly comprises a plurality of in the circumferential and / or axial direction 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 lubricating fluid flow with nevertheless reliable sealing against undesired backflow.
  • the cavity assembly may be further limited in front and rear circumferential angular distance (av or ah) from the direction of rotation front and / or rear end of the low-pressure phase corresponding peripheral portion (UN) of the lifting member (HG) are limited. This allows a phase shift of the beginning or the end of the lubricating fluid supply to the transverse bearing.
  • the amount of such a phase shift is generally suitably limited to a value of about 10 ° - positive or negative.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Sliding-Contact Bearings (AREA)
  • General Details Of Gearings (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The invention relates to an eccentric drive mechanism for volumetric pumps or motors, comprising the following features: a) at least one stroke member (6, 6'), which is rotationally fixed to the shaft (W) of the crank gear and has at least one stroke bearing (HL) that is eccentric in relation to the axis (XX) of the shaft; b) the stroke bearing (HL) connects the stroke member (HG) to a coupling member (KG) that plays no part in the rotational displacement, said member being connected to at least one pressure member (DG) for the oscillating delivery drive mechanism of at least one piston-cylinder unit by means of a transversal bearing (QL); c) at least one pressure delivery source (DQ) for lubricant, which is connected on the output side to the transversal bearing (QL) via a system of channels; d) starting from a connection channel (KA) that is connected to the pressure delivery source (DQ), the channel system comprises a first channel (K1) running through the stroke member (HG) into the stroke bearing (HL) and at least one second channel (K2) running from said stroke bearing through the coupling member (KG) into the transversal bearing (QL).

Description

Exzentertriebwerk für volumetrisch wirkende Pumpen oder Motoren Eccentric drive for volumetric pumps or motors
Die Erfindung betrifft ein Exzentertriebwerk für volumetrisch wirkende Pumpen oder Motoren mit den Merkmalen des Oberbegriffs des Anspruchs 1. Solche Triebwerke sind im Stand der Technik bekannt.The invention relates to an eccentric drive for volumetric pumps or motors having the features of the preamble of claim 1. Such engines are known in the art.
Das mit der Welle des Kurbelgetriebes drehfest verbundene Hubglied mit seiner bezüglich der Achse dieser Welle exzentrischen Hublagerung kann z.B. als Kurbelzapfen einer üblichen Kurbelwelle, das Koppelglied als Pleuel und das Druckglied als Kolben ausgebildet sein, der mit dem Pleuel durch einen Kolbenbolzen schwenkbar verbunden ist. Das Kurbelzapfen/Pleuellager und das Kolbolzenlager bilden zusammen wiederum eine Lagerung mit einem translatorischen, quer zum Hub gerichteten Freiheitsgrad, also eine Querlagerung. Für die Schmierfluidzuführung zur Querlagerung kommt dann ein Kanal- bzw. 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, d.h. durch die Hublagerung. Im Interesse der Einspeisung und Verteilung des Schmierfluids in der Niederdruckphase für die ansc liessende, hydrodynamische Bildung eines Schmierfilms in der Hochdruckphase durch Relativ-Drehbewegung zwischen den Lagerfläcnen werden bekanntermassen entsprechend gross bemessene, das Lager umgreifende, nutförmige Aussparungen in den Lagerflächen vorgesehen .The non-rotatably connected to the shaft of the crank gear lifting member with its with respect to the axis of this shaft eccentric stroke bearing can e.g. be designed as a crank pin of a conventional crankshaft, the coupling member as a connecting rod and the pressure member as a piston which is pivotally connected to the connecting rod by a piston pin. The crank pin / connecting rod bearing and the Kolbolzenlager together again form a bearing with a translational, directed transversely to the degree of freedom, ie a transverse bearing. For the lubricating fluid supply to the transverse bearing then a channel or bore system comes into consideration, 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 / conrod bearing, i. by the stroke storage. In the interest of feeding and distribution of the lubricating fluid in the low-pressure phase for the ansc-leaving, hydrodynamic formation of a lubricating film in the high-pressure phase by relative rotational movement between the Lagerfläcnen known large sized, the bearing encompassing, groove-shaped recesses are provided in the bearing surfaces.
Nun herrschen in der jeweiligen Hochdruckphase zwischen den Lagerflächen der Querϊagerung - mindestens neben kontinuierlichen Relativ-Drehgebewegungen, bei wichtigen Konstruktionen jedoch ausschliesslich - oszillierende Bewegungszustände mit Stillständen, die den 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 Querlagerung7 in Verbindung stehende Hublager - sondern dieses Polster in den/Hochdruckphasen nicht zu rasch abfliessen zu lassen. Dieser Abfϊuss 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. Aufgabe der Erfindung ist daher die Schaffung eines Exzentertriebwerks, das sich hinsichtlich der Lagerung durch wirksame und sichere Schmierung und Schmierdruckhaltung auszeichnet. Die Lösung dieser Aufgabe ist bestimmt durch die Merkmale des Anspruchs 1. Im Kombinationszusammenhang dieser Lösungsmerkmale kommt es u.a. darauf an, dass die Strömungsverbindung zwischen der Querlagerung und dem Kanalsystem der Schmierfluidzuführung in der Hochdruckphase jeweils durch die nicht unterbrochenen Lagerflächen der Hublagerung verschlossen und damit eine unerwünschte Rückströmung des Schmierfluids unterbunden ist.Now prevail in the respective high-pressure phase between the bearing surfaces of the Querϊagerung - at least in addition to continuous relative rotational movements, in important constructions, however, exclusively - oscillating motion states with stoppages that virtually do not allow the construction of sufficiently viable hydrodynamic lubricating films. In these areas, it is important not only to introduce a sufficient lubricant cushion in the low pressure phases in the bearing gap - this is done via the associated with the transverse bearing 7 Stroke - but this cushion in the / high pressure phases not to drain too quickly. In turn, this discharge can take place 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. The object of the invention is therefore to provide an eccentric, which is characterized in terms of storage by effective and safe lubrication and lubricating pressure maintenance. The solution of this problem is determined by the features of claim 1. In the combination context of these solution features, it is important, inter alia, that the flow connection between the transverse bearing and the channel system of the lubricating fluid supply in the high-pressure phase respectively closed by the uninterrupted bearing surfaces of the rod bearing and thus an undesirable Return flow of the lubricating fluid is prevented.
Es ist hervorzuheben, dass vor allem bei Hochdruckpumpen und 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, especially with high-pressure pumps and 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 a high pressure operation acceptable mechanical efficiency.
Eine wesentliche Weiterbildung der Erfindung besteht darin, dass die Hohlraumanordnung in einer Lagerfläche des Hubgliedes angeordnet ist, die sich über mindestens einen Teil des der Niederdruckphase des Exzentertriebwerks 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 eine Weiterbildung derzufolge die Hohlraumanordnung mindestens einen Hohlraum in Form einer sich höchstens über einen Halbkreis-Umfangsabschnitt des Hubgliedes estreckenden Nut aufweist.An essential development of the invention is that the cavity arrangement is arranged in a bearing surface of the lifting member, which extends over at least part of the low-pressure phase of the Exzentertriebwerks corresponding 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. A further development according to which the cavity arrangement has at least one cavity in the form of a groove which extends at most over a semicircular circumferential section of the lifting member is used for the same purpose of optimization.
In gewissen Anwendungen kommt eine andere Weiterbildung in Betracht, derzufolge die Hohlraumanordnung eine Mehrzahl von in Umfangs- und/oder Axialrichtung des Hubgliedes 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 wesentlich Weiterbildung der Erfindungsgedanken sieht vor, dass die Hohlraumanordnung in einem vorderen bzw. rückwärtigen Umfangswinkelabstand vom bezüglich der Drehrichtung vorderen und/oder rückwärtigen Ende des der Niederdruckphase entsprechenden Umfangsabschnitts des Hubgliedes begrenzt ist. Dies ermöglicht in gewissen Anwendungen zweckmässige Phasenerschiebungen des Beginns bzw. des Endes der Schmierfluidzuführung zur Querlagerung. Damit kann gegebenenfalls auftretenden Phasenverschiebungen und/oder Änderungen des zeitlichen Druckgradienten infolge Kompressibilität des Arbeitsmediums Rechnung getragen werden. Dabei kommen grundsätzlich positive wie auch negative Winkelabstände bezüglich der geometrischen Tot- oder Umkehrpunkte punkte des Exzentertriebwerks in Betracht.In certain applications, another development is contemplated, according to which the cavity assembly comprises a plurality of circumferentially and / or axially of the lifting member offset from each other arranged cavities, which are each in communication with the lubricating fluid system. This allows comparatively large cross sections for the lubricating fluid flow with nevertheless reliable sealing against undesired backflow. A likewise substantially further development of the inventive idea provides that the cavity arrangement is limited in a front or rear circumferential angular distance from the front and / or rear end of the low pressure phase corresponding peripheral portion of the lifting member. This allows in certain applications expedient Phasenerschiebungen the beginning or the end of the lubricating fluid 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 the working medium can be taken into account. In principle, positive as well as negative angular distances with respect to the geometrical dead center or reversal points of the eccentric engine come into consideration.
Die Erfindung wird weiter unter Bezugnahme auf das in den Zeichnungen schematisch argestellte Ausführungsbeispiel erläutert, darin zeigt:The invention will be further explained with reference to the embodiment shown schematically in the drawings, in which:
Fig.l undFig.l and
Fig.2 als bevorzugtes Anwendungsbeispiel der Erfindung eine Radialkolbenmaschine in Axial- bzw. Radialansicht,2 as a preferred application example of the invention, a radial piston machine in axial or radial view,
Fig.3 einen in grösserem Massstab gehaltenen, quer zur Hauptwelle orientierten Teilschnitt des Exzentertriebwerks der Pumpe gemäss Fig.l und 2 und3 shows a larger scale, oriented transverse to the main shaft section of the Exzentertriebwerks the pump according to Fig.l and 2 and
Fig.4 einen Teil- Axialschnitt des Exzentertriebwerks mit einem teilweise angedeuteten Radial-Druckglied und zugehörigem Kolben sowie Zylinder.4 shows a partial axial section of the Exzentertriebwerks with a partially indicated radial pressure member and associated piston and cylinder.
Bei der Radialkolbenmaschine nach Fig.l und 2 handelt es sich um eine 5-Zylinderpumpe mit von einer Welle (W) angetriebenen Zylinder- Kolbeneinheiten (ZI) bis (Z5), die konzentrisch zur Achse (X-X) der Welle W und über deren Umfang gleichmässig verteilt angeordnet sind. Im Zentralgehäuse (GZ) befindet sich ein noch im einzelnen darzustellendes Exzentertriebwerk. Das Antriebsmoment wird von einem nicht dargestellten Motor über einen Wellenstummel (WS) eingeleitet. Das in Fig.3 und 4 dargestellte Exzentertriebwerk umfasst ein mit der Welle (W) drehfest verbundenes Hubglied (HG), das eine bezüglich dieser Achse (XX) der Welle exzentrische Hublagerung (HL) aufweist. Die Hubϊagerung (HL) verbindet das Hubglied (HG) mit einem an der Drehbewegung nicht teilnehmenden Koppelglied (KG) , das seinerseits durch eine Querlagerung (QL) mit einem Druckglied (DG) für den oszillierenden Förderantrieb einer Kolben-Zylindereinheit verbunden ist. Bei dem vorliegenden, bevorzugten Anwendungsbeispiel ist das Hubglied eine einfache Exzenterscheibe, die drehfest auf der Welle (W) sitzt oder mit dieser einstückig ausgebildet ist. Das Hubglied bildet an seinem äusseren Umfang eine Lagerfläche (Ll), die in einer entsprechenden, zylindrischen Lagerfläche (L2) des Koppelgliedes sitzt und damit eine Hublagerung (HL) bildet. Demgemäss besitzt die Konstruktion trotz der Mehrzylinderanordnung keine ausgeprägte Kurbelwelle.In the radial piston machine according to Fig.l and 2 is a 5-cylinder pump driven by a shaft (W) cylinder piston units (ZI) to (Z5), concentric with the axis (XX) of the shaft W and over its circumference are arranged evenly distributed. In the central housing (GZ) is still an eccentric engine to be displayed in detail. The drive torque is initiated by a motor, not shown, via a stub shaft (WS). The eccentric drive shown in Figures 3 and 4 comprises a with the shaft (W) rotatably connected lifting member (HG) having a relative to this axis (XX) of the shaft eccentric stroke bearing (HL). The Hubϊagerung (HL) connects the lifting member (HG) with a non-participating in the rotary motion coupling member (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 is a simple eccentric disc which is non-rotatably mounted on the shaft (W) or formed integrally therewith. The lifting member forms at its outer periphery a bearing surface (Ll), which sits in a corresponding cylindrical bearing surface (L2) of the coupling member and thus forms a stroke bearing (HL). Accordingly, despite the multi-cylinder arrangement, the construction does not have a pronounced crankshaft.
Das Druckglied ist im Beispiel als in einem Gehäuse (GH) radial zur Welle verschiebbar gelagerte Büchse ausgebildet, in der ein unter dem Arbeitsdruck stehender Kolben (KO) sitzt. Dieser presst die im Beispiel im wesentlichen oder annähernd ebene untere Stirnfäche (Fl) des Druckgliedes mit grossen Kräften gegen eine ebene Sitzfläche (F2) des Koppelgliedes (KG). Die Flächen (Fl) und (F2) bilden als Lagerflächen zusammen die Querlagerung (QL). Sie unterliegen ausschliesslich translatorischen Gleitbewegungen relativ zueinander. Gegebenenfalls kann der Kolben selbst mit seiner unteren Stirnfläche die genannte Lagerfläche der Querlagerung bilden.The pressure member is formed in the example as in a housing (GH) radially to the shaft slidably mounted bush in which a standing under the working pressure piston (KO) sits. This presses in the example substantially or approximately flat lower Stirnfäche (Fl) of the pressure member with large forces against a flat seat surface (F2) of the coupling member (KG). The surfaces (Fl) and (F2) together form the transverse bearing (QL) as bearing surfaces. They are subject only translational sliding relative to each other. Optionally, the piston itself form with its lower end face the said bearing surface of the transverse bearing.
Des weiteren ist eine Druckförderquelle (DQ) für 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 (Kl) und mindestens einen von dieser Hublagerung durch das Koppelglied (KG) in die Querlagerung (QL) verlaufenden zweiten Kanal (K2). Im Bereich der Hublagerung (HL) ist innerhalb der mit dem Hubglied (HG) verbundenen Lagerfläche (Ll) eine Hohlraumanordnung für die Weiterleitung des Schmierfluids zu mindestens einem zweiten Kanal (K2) vorgesehen, und diese Hohlraumanordnung hat innerhalb der Lagerfläche (Ll) und in Umfangsrichtung des Hubgliedes (HG) wenigstens annähernd eine Anordnung und/oder Erstreckung, die eine Schmierfluiddurchströmung zwischen erstem und zweitem Kanal 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 verhindert, jedoch eine ausreichende Füllung des Querlagerspaltes mit Schmierfluid in den Niedrdruckphasen sichert.Furthermore, a pressure feed source (DQ) for 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 through the coupling member (KG) Transverse storage (QL) extending second channel (K2). In the region of the stroke bearing (HL), a cavity arrangement for the forwarding of the lubricating fluid to at least one second channel (K2) is provided within the bearing surface (L1) connected to the lifting member (HG), and this cavity arrangement has within the bearing surface (L1) and in Circumferential direction of the lifting member (HG) at least approximately an arrangement and / or extent that allows a lubricating fluid flow between the first and second channel respectively only within a low pressure phase of the lubricating fluid in the stroke bearing (HL) or the transverse bearing (QL). This construction or arrangement thus acts in the sense of a push valve control, which prevents undesired backflow of the lubricating fluid in the high pressure phases of the transverse bearing, but ensures sufficient filling of the transverse bearing gap with lubricating fluid in the low pressure phases.
Im einzelnen hat das Exzentertriebwerk eine Hohlraumanordnung in einer Lagerfläche (Ll) des Hubgliedes (HG). Diese Hohlraumanordnung erstreckt sich über mindestens einen Teil des der Niederdruckphase des Exzentertriebwerks entsprechenden Umfangsabschnitts (UN) des Hubgliedes (HG) und weist wenigstens abschnittsweise eine mit Abstand von den Rändern dieser Lagerfläche (Ll) verlaufende Begrenzung auf. Dies verbessert die Rückstrom-Sperrwirkung. Im Ausführungsbeispiel ist die Konstruktion speziell so gestaltet, dass die Hohlraumanordnung mindestens einen Hohlraum in Form einer sich höchstens über einen Halbkreis-Umfangsabschnitt des Hubgliedes estreckenden Nut (HKN) aufweist. Gegebenenfalls kann die Hohlraumanordnung eine Mehrzahl von in Umfangs- und/oder Axialrichtung des Hubgliedes (HG) 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. 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 Umfangsabschnitts (UN) des Hubgliedes (HG) begrenzt ausgebildet werden. Dies ermöglicht eine Phasenverschiebung des Beginns bzw. des Endes der Schmierfluidzuführung zur Querlagerung. Der Betrag einer solchen Phasenverschiebung wird im allgemeinen zweckmässig auf einen Wert von etwa 10° - positiv oder negativ - beschränkt. Specifically, the eccentric has a cavity arrangement in a bearing surface (Ll) of the lifting member (HG). This cavity arrangement extends over at least part of the low-pressure phase of the eccentric engine corresponding peripheral portion (UN) of the lifting member (HG) and has at least in sections a distance from the edges of this bearing surface (Ll) extending boundary. This improves the reverse flow blocking effect. In the exemplary embodiment, the construction is specially designed such that the cavity arrangement has at least one cavity in the form of a groove (HKN) which extends at most over a semicircular peripheral portion of the lifting member. Optionally, the cavity assembly comprises a plurality of in the circumferential and / or axial direction 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 lubricating fluid flow with nevertheless reliable sealing against undesired backflow. The cavity assembly may be further limited in front and rear circumferential angular distance (av or ah) from the direction of rotation front and / or rear end of the low-pressure phase corresponding peripheral portion (UN) of the lifting member (HG) are limited. This allows a phase shift of the beginning or the end of the lubricating fluid supply to the transverse bearing. The amount of such a phase shift is generally suitably limited to a value of about 10 ° - positive or negative.

Claims

Ansprüche: Claims:
1. Exzentertriebwerk für volumetrisch wirkende Pumpen oder Motoren, umfassend folgende Merkmale:1. Exzentertriebwerk for volumetric pumps or motors, comprising the following features:
a) Es ist mindestens ein mit der Welle (W) des Kurbelgetriebes drehfest verbundenes Hubglied (HG) vorgesehen, das mindestens eine bezüglich dieser Achse (XX) der Welle exzentrische Hublagerung (HL) aufweist;a) It is at least one with the shaft (W) of the crank gear rotatably connected lifting member (HG) is provided which has at least one with respect to this axis (XX) of the shaft eccentric stroke bearing (HL);
b) die Hublagerung (HL) verbindet das Hubglied (HG) mit einem an der Drehbewegung nicht teilnehmenden Koppelglied (KG) , das seinerseits durch eine Querlagerung (QL) mit mindestens einem Druckglied (DG) für den oszillierenden Förderantrieb mindestens einer Kolben-Zylindereinheit verbunden ist;b) the stroke bearing (HL) connects the lifting member (HG) with a non-participating in the rotary motion coupling member (KG), which in turn connected by a transverse bearing (QL) with at least one pressure member (DG) for the oscillating conveyor drive at least one piston-cylinder unit is;
c) es ist mindestens eine Druckförderquelle (DQ) für Schmier-fluid vorgesehen, die ausgangsseitig durch ein Kanalsystem mit der Querlagerung (QL) verbunden ist;c) there is provided at least one pressure source (DQ) for lubricating fluid, which is connected on the output side by a channel system with the transverse bearing (QL);
d) ausgehend von einem mit der Druckförderquelle (DQ) verbundenen Anschlusskanal (KA) umfasst das Kanalsystem mindestens einen durch das Hubglied (HG) in die Hublagerung (HL) verlaufenden ersten Kanal (Kl) und mindestens einen von dieser Hublagerung durch das Koppelglied (KG) in die Querlagerung (QL) verlaufenden zweiten Kanal (K2); gekennzeichnet durch folgende Merkmale:d) starting from a connected to the pressure-conveying source (DQ) connection channel (KA), the channel system comprises at least one by the lifting member (HG) in the stroke bearing (HL) extending first channel (Kl) and at least one of this Hublagerung by the coupling member (KG ) in the transverse storage (QL) extending second channel (K2); characterized by the following features:
e) im Bereich der Hublagerung (HL) ist innerhalb einer mit dem Hubglied (HG) verbundenen Lagerfläche (Ll) eine Hohlraumanordnung für die Weiterleitung des Schmierfluids zu mindestens einem zweiten Kanal (K2) vorgesehen, und diese Hohlraumanordnung hat innerhalb der Lagerfläche (Ll) und in Umfangs- richtung des Hubgliedes (HG) wenigstens annähernd eine Anordnung und/oder Erstreckung, die eine Schmierfluiddurch- strömung zwischen erstem und zweitem Kanal jeweils nur innerhalb einer Niederdruckphase des Schmierfluids in der Hublagerung (HL) bzw. der Querlagerung (QL) zulässt. e) in the region of the stroke bearing (HL), a cavity arrangement for the forwarding of 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 within the bearing surface (L1) and in the circumferential direction of the lifting member (HG) at least approximately an arrangement and / or extent that allows a Schmierfluiddurch- flow between the first and second channel respectively only within a low pressure phase of the lubricating fluid in the stroke bearing (HL) or the transverse bearing (QL) ,
2. Triebwerk nach Anspruch 1, dadurch gekennzeichnet, dass die Hohlraumanordnung in einer Lagerfläche (Ll) des Hubgliedes (HG), die sich über mindestens einen Teil des der Niederdruckphase des Exzentertriebwerks entsprechenden Umfangsabschnitts (UN) des Hubgliedes (HG) erstreckt, angeordnet ist und wenigstens abschnittsweise eine mit Abstand von den Rändern dieser Lagerfläche (Ll) verlaufende Begrenzung aufweist.2. Engine according to claim 1, characterized in that the cavity arrangement in a bearing surface (Ll) of the lifting member (HG), which extends over at least part of the low-pressure phase of the Exzentertriebwerks corresponding peripheral portion (UN) of the lifting member (HG) is arranged and at least in sections has a running at a distance from the edges of this bearing surface (Ll) boundary.
3. Triebwerk nach Anspruch 2, dadurch gekennzeichnet, dass die Hohlraumanordnung mindestens einen Hohlraum in Form einer sich höchstens über einen Halbkreis-Umfangsabschnitt des Hubgliedes estreckenden Nut (HKN) aufweist.3. Engine according to claim 2, characterized in that the cavity arrangement has at least one cavity in the form of a maximum of a semicircular peripheral portion of the lifting member estreckenden groove (HKN).
4. Triebwerk nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass die Hohlraumanordnung eine Mehrzahl von in Umfangs- und/oder Axialrichtung des Hubgliedes (HG) gegeneinander versetzt angeordneten Hohlräumen umfasst, die miteinander oder gesondert mit dem Schmierfluidsystem verbunden sind..4. Engine according to claim 2 or 3, characterized in that the cavity arrangement comprises a plurality of circumferential and / or axial direction of the lifting member (HG) offset from each other arranged cavities, which are connected to each other or separately with the lubricating fluid system.
5. Triebwerk nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die Hohlraumanordnung in einem vorderen bzw. rückwärtigen Umfangswinkelabstand (av bzw. ah) vom bezüglich der Drehrichtung vorderen und/oder rückwärtigen Ende des der Niederdruckphase des Hubgliedes (HG) entsprechenden Umfangsabschnitts (UN) des Hubgliedes (HG) begrenzt ist.5. Engine according to one of the preceding claims, characterized in that the cavity arrangement in a front or rear circumferential angular distance (av or ah) with respect to the direction of rotation front and / or rear end of the low pressure phase of the lifting member (HG) corresponding peripheral portion (UN ) of the lifting member (HG) is limited.
6. Triebwerk nach Anspruch 5, dadurch gekennzeichnet, dass der vordere und /oder rückwärtige Umfangswinkelabstand (av bzw. ah) der Hohlraumanordnung höchstens etwa 10° beträgt. 6. Engine according to claim 5, characterized in that the front and / or rear circumferential angular distance (av or ah) of the cavity assembly is at most about 10 °.
EP04740680.6A 2003-07-07 2004-07-06 Eccentric drive mechanism for volumetric pumps or motors Expired - Lifetime 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 true EP1651866A1 (en) 2006-05-03
EP1651866B1 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)

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CN1846058B (en) 2010-04-21
CA2540721C (en) 2011-11-22
PL1651866T3 (en) 2014-08-29
DE10330757A1 (en) 2005-02-03
EP1651866B1 (en) 2014-03-05
JP2007526958A (en) 2007-09-20
NO338172B1 (en) 2016-08-01
RU2006103487A (en) 2006-06-10
US7441492B2 (en) 2008-10-28
WO2005003558A1 (en) 2005-01-13
CN1846058A (en) 2006-10-11
NO20051157L (en) 2005-04-15
US20060245940A1 (en) 2006-11-02
RU2354847C2 (en) 2009-05-10
CA2540721A1 (en) 2005-01-13
ES2460954T3 (en) 2014-05-16

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