EP1651866B1 - Mecanisme de transmission excentrique destine a des pompes d'action volumetrique ou moteurs - Google Patents

Mecanisme de transmission excentrique destine a des pompes d'action volumetrique ou moteurs 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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EP
European Patent Office
Prior art keywords
stroke
mount
channel
lubricating fluid
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.)
Active
Application number
EP04740680.6A
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German (de)
English (en)
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EP1651866A1 (fr
Inventor
Bernhard Frey
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Frey Bernhard
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Individual
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Publication of EP1651866A1 publication Critical patent/EP1651866A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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.

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)

Claims (4)

  1. Mécanisme de transmission excentrique destiné à des pompes volumétriques et unidirectionnelles, présentant les caractéristiques suivantes :
    - au moins un organe de levage (HG),
    • qui est relié bloqué en rotation à un arbre (W) contenant un axe (XX) d'un mécanisme à mani velle, et
    • qui présente au moins un palier de levage (HL) excentrique par rapport à l'axe (XX) de l'arbre (W) ;
    - un organe de couplage (KG) qui est relié à l'organe de levage (HG) par le palier de levage (HL), l'organe de couplage (KG)
    • ne participant pas au mouvement de rotation et
    • étant relié de son côté par un palier transversal (QL) à au moins un organe de pression (DG) pour la commande de mouvement oscillant d'au moins une unité cylindre-piston de la pompe ;
    - au moins une source d'alimentation en pression (DQ) destinée à un fluide de graissage qui est reliée, côté sortie, au palier transversal (QL),
    - un système de canal, qui
    • relie la source d'alimentation en pression (DQ) au palier transversal (QL),
    • comprend, à partir d'un canal de raccordement (KA) relié à la source d'alimentation en pression (DQ) :
    • au moins un premier canal (K1) qui s'étend par l'organe de levage (HG) dans le palier de levage (HL), et
    • au moins un deuxième canal (K2) qui s'étend du palier de levage (HG) au palier transversal (QL) en passant par l'organe de couplage (KG) ;
    un agencement d'espaces creux,
    • qui est prévu dans la zone du palier de levage (HL) à l'intérieur d'une surface de palier (L1) reliée à l'organe de levage (HG) pour l'acheminement du fluide de graissage au moins au deuxième canal (K2),
    • qui est agencé et qui s'étend au moins approximativement à l'intérieur de la surface de palier (L1) et dans le sens circonférentiel de l'organe de levage (HG), ce qui permet un écoulement du fluide de graissage entre le au moins premier canal (K1) et le au moins deuxième canal (K2),
    l'agencement d'espaces creux
    - s'étendant sur une partie substantielle de la section de circonférence en demi-cercle (UN) - correspondant à la phase basse pression du mécanisme de transmission excentrique- de l'organe de levage (HG), de sorte que
    l'écoulement du fluide de graissage entre le au moins premier canal (K1) et le au moins deuxième canal (K2) s'effectue pendant une partie substantielle de l'ensemble de la phase basse pression du fluide de graissage dans le palier de levage (HL) ou dans le palier transversal (QL),
    et qu'un retour du fluide de graissage est empêché dans une phase haute pression suivante,
    - présente au moins par endroits une délimitation s'étendant à distance des bords de cette surface de palier (L1), et
    - présente au moins un espace creux sous la forme d'une rainure (HKN) qui s'étend à l'intérieur de la section circonférentielle en demi-cercle (UN) de l'organe de levage (HG), correspondant à la phase basse pression du mécanisme de transmission excentrique et
    - qui s'étend au maximum le long de la section circonférentielle en demi-cercle (UN) de l'organe de levage (HG) correspondant à la phase basse pression du mécanisme de transmission excentrique.
  2. Mécanisme de transmission excentrique selon la revendication 1, caractérisé en ce que l'agencement d'espaces creux comprend d'autres espaces creux, les espaces creux
    - étant agencés décalés les uns par rapport aux autres dans le sens circonférentiel et/ou dans le sens axial de l'organe de levage (HG), et
    - étant reliés ensemble ou séparément à la source d'alimentation en pression (DQ).
  3. Mécanisme de transmission excentrique selon la revendication 1, caractérisé en ce que l'agencement d'espaces creux dans une distance angulaire circonférentielle avant (av) et/ou une distance angulaire circonférentielle arrière (ah) est limité par l'extrémité avant ou arrière, en fonction du sens de rotation, d'une section circonférentielle (UN) de l'organe de levage (HG) correspondant à la phase basse pression de l'organe de levage (HG).
  4. Mécanisme de transmission excentrique selon la revendication 3, caractérisé en ce que la distance angulaire circonférentielle avant (av) et/ou la distance angulaire circonférentielle arrière de l'agencement d'espaces creux est égale au maximum à 10°.
EP04740680.6A 2003-07-07 2004-07-06 Mecanisme de transmission excentrique destine a des pompes d'action volumetrique ou moteurs Active EP1651866B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL04740680T PL1651866T3 (pl) 2003-07-07 2004-07-06 Mimośrodowy mechanizm napędowy dla silników lub pomp o działaniu wolumetrycznym

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10330757A DE10330757A1 (de) 2003-07-07 2003-07-07 Exzentertriebwerk für volumetrisch wirkende Pumpen oder Motoren
PCT/EP2004/007352 WO2005003558A1 (fr) 2003-07-07 2004-07-06 Mecanisme de transmission excentrique destine a des pompes d'action volumetrique ou moteurs

Publications (2)

Publication Number Publication Date
EP1651866A1 EP1651866A1 (fr) 2006-05-03
EP1651866B1 true EP1651866B1 (fr) 2014-03-05

Family

ID=33559962

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04740680.6A Active EP1651866B1 (fr) 2003-07-07 2004-07-06 Mecanisme de transmission excentrique destine a des pompes d'action volumetrique ou moteurs

Country Status (11)

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

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE355460T1 (de) * 2003-02-11 2006-03-15 Ganser Hydromag Hochdruckpumpe
DE102008042378A1 (de) 2008-09-26 2010-04-01 Robert Bosch Gmbh Exzentertriebwerk
DE102008042380A1 (de) 2008-09-26 2010-04-01 Robert Bosch Gmbh Exzentertriebwerk
US8926298B2 (en) * 2012-01-04 2015-01-06 Husco International, Inc. Hydraulic piston pump with a variable displacement throttle mechanism
CN103047100A (zh) * 2013-01-10 2013-04-17 无锡开普机械有限公司 具有凸轮轴轴套的转子泵
CN103967743A (zh) * 2013-01-29 2014-08-06 王彦彬 磁力式同平面多缸多级组合压缩机
CN103967745A (zh) * 2013-01-30 2014-08-06 王彦彬 同平面多缸多级凸轮组合压缩机

Family Cites Families (15)

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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 (de) * 1967-03-25 1971-09-16 Teves Gmbh Alfred Radialkolbenpumpe
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 (fr) * 1977-06-13 1979-01-11
DE3039197C2 (de) * 1980-10-17 1986-07-17 Mannesmann Rexroth GmbH, 8770 Lohr Hydrostatische Radialkolbenpumpe
US4567815A (en) * 1984-12-04 1986-02-04 Vilter Manufacturing Corporation Connecting rod and bearing assembly therefor
DE4126640B4 (de) * 1991-08-12 2005-06-16 Robert Bosch Gmbh Pumpenanordnung mit einer Vorförderpumpe und einer Radialkolbenpumpe
GB9117975D0 (en) * 1991-08-20 1991-10-09 Collins Motor Corp Ltd Interconnecting rotary and reciprocating motion
JP2783381B2 (ja) * 1993-11-05 1998-08-06 松下冷機株式会社 密閉型圧縮機
KR0153343B1 (ko) * 1995-10-13 1999-03-20 김광호 왕복동형 압축기
JPH1089255A (ja) * 1996-09-10 1998-04-07 Hitachi Ltd 密閉形電動圧縮機
DE19906626A1 (de) * 1998-10-06 2000-04-13 Mannesmann Rexroth Ag Pumpenanordnung

Also Published As

Publication number Publication date
CN1846058A (zh) 2006-10-11
EP1651866A1 (fr) 2006-05-03
RU2006103487A (ru) 2006-06-10
JP2007526958A (ja) 2007-09-20
ES2460954T3 (es) 2014-05-16
NO20051157L (no) 2005-04-15
CA2540721C (fr) 2011-11-22
WO2005003558A1 (fr) 2005-01-13
DE10330757A1 (de) 2005-02-03
NO338172B1 (no) 2016-08-01
RU2354847C2 (ru) 2009-05-10
US20060245940A1 (en) 2006-11-02
CA2540721A1 (fr) 2005-01-13
US7441492B2 (en) 2008-10-28
PL1651866T3 (pl) 2014-08-29
CN1846058B (zh) 2010-04-21

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