EP0929743B1 - Pompe a piston radial - Google Patents

Pompe a piston radial Download PDF

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Publication number
EP0929743B1
EP0929743B1 EP97939965A EP97939965A EP0929743B1 EP 0929743 B1 EP0929743 B1 EP 0929743B1 EP 97939965 A EP97939965 A EP 97939965A EP 97939965 A EP97939965 A EP 97939965A EP 0929743 B1 EP0929743 B1 EP 0929743B1
Authority
EP
European Patent Office
Prior art keywords
radial piston
piston pump
drive shaft
pump according
piston
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.)
Expired - Lifetime
Application number
EP97939965A
Other languages
German (de)
English (en)
Other versions
EP0929743A1 (fr
Inventor
Egon Eisenbacher
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.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring GmbH
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 Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Publication of EP0929743A1 publication Critical patent/EP0929743A1/fr
Application granted granted Critical
Publication of EP0929743B1 publication Critical patent/EP0929743B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0456—Cylindrical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F04B1/0535—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders the piston-driving cams being provided with inlets and outlets
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0469—Other heavy metals
    • F05C2201/0475—Copper or alloys thereof
    • F05C2201/0478—Bronze (Cu/Sn alloy)

Definitions

  • the invention relates to a radial piston pump according to the preamble of claim 1.
  • Such pumps usually have a large number of cylinders star-shaped in one or more planes around a drive shaft arranged, which is designed as an eccentric shaft.
  • the pistons of the cylinders rest on the eccentric and make a constant stroke, which corresponds to double eccentricity.
  • Such pumps are usually with pressure valves - for example automatic, spring-loaded valves - equipped, via the the pressurized medium is ejectable.
  • the suction can take place via automatic spring-loaded suction valves, which open during the suction stroke of the piston.
  • a radial piston pump is described in EP 0 520 286 B1, in which an eccentric ring is mounted on the drive shaft External circumference flats are provided on which the radial piston issue.
  • the invention has for its object the generic radial piston pump to be designed in such a way that with minimal device technology Wear and tear can be reduced.
  • the tangential surface of the eccentric is designed as a closed surface, therefore has no depressions. This means the whole Tangential surface is available as a contact surface for the radial piston.
  • the wear is reduced when using the radial piston pump kept low.
  • the opening of the piston inlet takes place through the peripheral edge between the tangential surface and the peripheral surface of the eccentric is formed.
  • By the Elimination of grooves or recesses that are manufactured with high precision manufacturing costs can be compared to the conventional solution can be reduced to a minimum. Doing so it is particularly preferred if between the eccentric and the piston an eccentric ring is provided which slides on the drive shaft is led. Due to the flat support of the piston face is the use of a material with emergency running properties for allows the eccentric ring, due to the lower surface pressure the piston face hydrostatic is partially relieved, so that a premature wear of the eccentric ring largely can be avoided.
  • the piston bore axis which in the conventional solutions are each coaxial to the central axes of the drive shaft cross section were arranged, offset against the direction of rotation, so that the bore axis is parallel to the corresponding one Central axis runs.
  • a kinematic reversal of the above principle can also be the tangential surface with reference to the piston axis in the direction of rotation, so that the can achieve the same effect.
  • the amount of lateral displacement between the piston face and tangential surface can be the relative position the peripheral edge opening the inlet opening vary easily with respect to the inlet opening, so that the opening period during the suction stroke is adaptable to different conditions.
  • the inflow of the fluid to be pumped can continue simplify if the tangential surfaces each be formed by a radial projection so that the fluid can freely enter the opening cross-section can.
  • sealing devices on the piston end face be provided so that an optimal seal the inlet opening is possible during the working stroke.
  • the lateral offset between the shaft cross-section axis and the bore axis can also be adjusted by the axis of the inlet opening at a distance from the Piston axis is formed.
  • Tilting of the eccentric ring can be prevented if the working stroke of the piston is limited to a maximum is, so that always a flat contact of the piston face is guaranteed on the tangential surface.
  • Figure 1 shows a cross section of an inventive Radial piston pump 1, in which in a cylinder or pot-shaped housing 2 three distributed over the circumference Pump cylinder 4 are arranged, the piston 6 by a Pump drive shaft 8 are driven, the Stroke axes of the respective pistons 6 approximately in the radial direction the drive shaft 8 are arranged.
  • the housing 2 has a mounting flange which in Figure 1 is shown in section and on which on a Pitch circle distributed through holes 10 for flange screws (not shown) are formed so that a front cover is attachable.
  • a back wall 12 of the housing are a variety of threaded holes 14 formed, via which the pump on an aggregate is attachable.
  • the axis of rotation 16 of the pump drive shaft 8 runs coaxial to the central axis of the housing, being in the illustration according to Figure 1 only an eccentric 18, which is perpendicular drive shaft 8 extending to the plane of the drawing see is.
  • the eccentric axis is in FIG. 1 with the reference symbol 20 provided.
  • the measure of eccentricity corresponds to e - as already mentioned at the beginning - half the lifting height piston 6.
  • the radial piston pump 1 has coaxial to the drive shaft axis 16 and the housing 2, an inner housing 22, the with three cylinder receptacles extending in the radial direction 24 is provided, into which the cylinder 4 is screwed are.
  • the axial length of the cylinder receptacles 24 and the cylinder 4 is selected so that the in Figure 1 for Drive shaft 8 facing end portion of each cylinder 4th approximately tangential to the cylindrical interior 26 of the Inner housing 22 extends.
  • Each cylinder 4 is with a Stop collar 28 provided with which the cylinder 4 on the outer end face of the cylinder receptacle 24 is supported.
  • the stop collar 28 closes in A cylinder head 30 in the direction of the wall of the housing 2 in which a valve device 32 is received, through the one cylinder bore to the outside, i.e. to that of Housing 2 on the one hand and from the inner housing 22 on the other enclosed annular space 34 can be shut off.
  • FIG. 2 shows a section along the line A-A in Figure 1, one of the cylinders 4 with the corresponding Part of the eccentric 18 shown in an enlarged view is. Accordingly, the valve device 32 acts a valve body 36 which against a spring via 38 Valve seat 40 is biased in the cylinder head 30.
  • the Valve body 36 lies on the outer end face of the cylinder head 30 on, so that the valve device 32 a Allows fluid flow out of the cylinder space, a Backflow prevented.
  • check valve instead of that in the figures 1 and 2 shown check valve also other valve designs, such as diaphragm valves, etc. can be used.
  • a spring 44 is supported, via which the piston 6 in Is biased towards the eccentric 18.
  • the cylinder bore is connected to the valve seat 36 expanded in the radial direction stepwise, whereby by a first step portion formed the inner end face 42 becomes. At this first step-shaped section then closes the cylinder liner expanded in the radial direction 46 on, in which the piston 6 is slidably received is.
  • the piston 6 has an approximately cup-shaped cross section, an inlet opening 48 in the bottom of the piston is trained.
  • the drive shaft end section is designed as a reduced-diameter radial projection 50, the end face of which is the contact surface of the piston 6 forms.
  • the piston 6 lies with its face not directly on the outer circumference of the eccentric 18 of the drive shaft 8, but between Eccentric 18 and projection 50 is an eccentric ring 52 formed with an inner bore 54, which of the Eccentric 18 is pushed through.
  • Suction control edge 62 designated.
  • the piston shown at the bottom right in FIG. 1 is located just in this suction position, in which Fluid is sucked into the interior of the piston. Because of the negative pressure in the cylinder space and the spring preload the valve device 32 closed so that the sucked Fluid does not pass through the cylinder head 30 can leak.
  • the suction stroke of the piston 6 located at the top in FIG. 1 is finished when the drive shaft 6 - going out from the shown reference position - has rotated by 180 °, so that the eccentric center in the vertical direction is located below the center of the drive shaft, so that according to the suction stroke double the eccentricity e is.
  • this rotational position of the drive shaft becomes the suction control edge 62 due to the wobble motion of the eccentric ring 52 back to its starting position moved back so that the inlet opening 48 just closed is and no more fluid can be sucked in.
  • the solution according to the invention has the further advantage that no stroke volume loss occurs.
  • a particularly good and quick filling of the piston and Cylinder interior can be achieved if the inlet opening 48 executed with a rectangular cross section is, with a side edge parallel to the suction control edge 62 is arranged so that already at the beginning of the control process a large suction cross section for Is made available.
  • piston 6 is assigned an anti-rotation device (not shown) become.
  • the eccentric ring 52 made of a material with emergency running properties, such as for example executed bronze, by the Self-adjustment (spring preload of the piston 6 out wear compensation for the support surface (flattening 56) can take place.
  • This choice of materials makes it possible also, the eccentric ring 52 directly on the eccentric 18 Drive shaft 8 to store without a bearing bush must be provided.
  • the inlet opening can also be related to the drive shaft plane 48 eccentrically in the piston crown, so that the same effect occurs (Anti-twist device required).
  • the eccentric ring 152 of the shown in Figure 3 The embodiment is not ring-shaped with flats trained, but with three radial projections 64, which protrude from the ring circumferential surface 66 in the radial direction. That is, in the embodiment shown in Figure 3 are those marked with X, the flattenings 56 delimiting side areas cut free, so that the inflow occurs when the inlet opening 48 is open the fluid in the piston 6 is facilitated, so that the pressure losses in the pump can be reduced to a minimum are and thus the efficiency is increased. Of further in this embodiment is the cost of materials to manufacture the eccentric ring 152 reduced to a minimum since the ring walls in the area the ring peripheral surfaces 66 are reduced to a minimum.
  • To tilt the eccentric ring 152 with respect to To prevent piston 6 are the axial lengths of cylinders 4 and piston 6 and the radial spacing of the flat 56 with reference to the eccentric axis 20 selected so that the piston 6 strikes the cylinder head 30 before the eccentric ring can tip out of its investment position, so that a Tilt almost without damaging the eccentric ring 152 is excluded.
  • FIG. Another possibility is shown in FIG. with the lateral offset between the piston face and the flat 56 is adjustable.
  • the lateral displacement is in this embodiment thereby causing the flattening (Support surfaces) not symmetrical to the median planes are arranged by the eccentric axis 20, but laterally offset so that these central planes the flattening 256 in two partial areas with different Divide width d, f. That is, through the side "Shift" of the flat 256 with respect to the piston axis 58 is also achieved that the suction control edge 62 straight in the area of the top dead center of the piston still covers the inlet opening 48.
  • the one shown in Fig. 4 The exemplary embodiment is thus a kinematic reversal of the construction principle of that in FIGS.
  • FIGS. 5 and 6 show two further variants shown, in which the end face end portions the piston 6 compared to the above-described embodiments were modified.
  • a particularly good sealing effect between the face of the piston 6 and the flat 56 can be achieved if in the peripheral area of the mouth of the inlet opening 48 a sealing device 70 is provided, via which the piston 6 is supported on the flat 56. there it can be an elastomeric seal that by spring action or by inherent elasticity in Direction of the flat 56 is biased.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (13)

  1. Pompe à pistons radiaux comprenant un arbre d'entraínement (8) présentant un excentrique (18) et au moins un cylindre (4) dans lequel est guidé un piston radial (6) précontraint contre une surface tangentielle (56) de l'excentrique (18), lequel a un perçage avec un orifice d'admission (48) à travers lequel du fluide peut être aspiré hors d'une partie à basse pression de la pompe à pistons radiaux (1), et comportant une soupape de pression (32), dans la partie à haute pression de la pompe à haute pression (1), associée au piston radial (6), la position relative de la face frontale du piston radial (6) par rapport à la surface tangentielle (56) étant choisie telle que l'orifice d'admission (48) du perçage peut être commandé par une arête (62) située à l'arrière dans le sens de rotation (Z), de la surface tangentielle (56), caractérisée en ce que la surface tangentielle (56) est réalisée sous forme de surface fermée, et en ce que l'arête (62) est une arête périphérique formée entre la surface tangentielle (56) sur la surface périphérique de l'excentrique (18).
  2. Pompe à pistons radiaux selon la revendication 1, caractérisée en ce que l'axe de l'orifice d'admission (48) est agencé en décalage à l'opposée du sens de rotation (Z) de l'arbre d'entraínement (8), à distance du plan médian de l'arbre d'entraínement (8) contenant une verticale de la surface tangentielle (56).
  3. Pompe à pistons radiaux selon l'une ou l'autre des revendications 1 et 2, caractérisée en ce que l'axe de l'orifice d'admission (48) se trouve dans un plan médian de l'arbre d'entraínement, et une arête de commande d'aspiration de la surface tangentielle (56) est agencée en décalage par rapport au plan médian d'arbre d'entraínement, dans le sens de rotation de l'arbre d'entraínement (Y).
  4. Pompe à pistons radiaux selon l'une des revendications précédentes, caractérisée en ce que l'orifice d'admission (48) a une section transversale rectangulaire dont une arête rectangulaire est agencée parallèlement à l'arête périphérique (62) de la surface tangentielle (56).
  5. Pompe à pistons radiaux selon l'une des revendications précédentes, caractérisée en ce qu'une bague d'excentrique (52) montée à coulissement sur l'arbre d'entraínement (8) est agencée entre l'excentrique (18) de l'arbre d'entraínement (8) et le piston (6).
  6. Pompe à pistons radiaux selon la revendication 5, caractérisée en ce que la surface tangentielle (56) est réalisée sur une saillie radiale (50) de la bague d'excentrique (52).
  7. Pompe à pistons radiaux selon l'une des revendications précédentes, caractérisée en ce que l'axe de l'orifice d'admission (48) est décalé par rapport à l'axe du piston.
  8. Pompe à pistons radiaux selon l'une des revendications précédentes, caractérisée en ce que dans la face frontale du piston radial (6) est prévu un dispositif d'étanchéité (70) entourant l'orifice d'admission (48), lequel coopère avec la surface tangentielle (56).
  9. Pompe à pistons radiaux selon l'une des revendications précédentes, caractérisée en ce que le piston radial (6) a une sécurité antirotation.
  10. Pompe à pistons radiaux selon l'une des revendications précédentes, caractérisée en ce que l'orifice d'admission (48) est évasé dans la région d'embouchure.
  11. Pompe à pistons radiaux selon l'une des revendications 5 à 10, caractérisée en ce que la bague d'excentrique (52) est en un matériau avec des propriétés de fonctionnement d'urgence à capacités limitées, de préférence en bronze.
  12. Pompe à pistons radiaux selon l'une des revendications précédentes, caractérisée en ce qu'à l'arbre d'entraínement (8) sont associés trois cylindres (4).
  13. Pompe à pistons radiaux selon l'une des revendications 3 à 12, caractérisée en ce que la course de travail du piston radial (6) est limitée par une butée, de telle sorte que la bague d'excentrique (52) ne peut pas basculer hors de sa position de consigne.
EP97939965A 1996-10-01 1997-08-19 Pompe a piston radial Expired - Lifetime EP0929743B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19640596 1996-10-01
DE19640596A DE19640596A1 (de) 1996-10-01 1996-10-01 Radialkolbenpumpe
PCT/DE1997/001785 WO1998014704A1 (fr) 1996-10-01 1997-08-19 Pompe a piston radial

Publications (2)

Publication Number Publication Date
EP0929743A1 EP0929743A1 (fr) 1999-07-21
EP0929743B1 true EP0929743B1 (fr) 2002-12-11

Family

ID=7807640

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97939965A Expired - Lifetime EP0929743B1 (fr) 1996-10-01 1997-08-19 Pompe a piston radial

Country Status (4)

Country Link
EP (1) EP0929743B1 (fr)
DE (2) DE19640596A1 (fr)
ES (1) ES2184129T3 (fr)
WO (1) WO1998014704A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0816675B1 (fr) * 1996-07-01 2002-04-10 Mannesmann Rexroth AG Dispositif pour la stabilisation de l'anneau excentrique d'une pompe à pistons radiaux
US6104802A (en) 1997-02-10 2000-08-15 Genesys Telecommunications Laboratories, Inc. In-band signaling for routing
DE102007002730B4 (de) * 2007-01-18 2012-03-01 Continental Automotive Gmbh Radialkolbenpumpe zur Kraftstoffförderung sowie Herstellungsverfahren hierfür
IT1396002B1 (it) * 2009-04-30 2012-11-09 Bosch Gmbh Robert Anello poligonale di azionamento di una pompa a pistoni, pompa a pistoni comprendente tale anello poligonale, e metodo per realizzare l'anello poligonale

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1287601A (fr) * 1961-02-03 1962-03-16 Rech Etudes Prod Moteur hydraulique
US3614267A (en) * 1969-10-31 1971-10-19 Applied Power Ind Inc Two-stage fluid pump
DE2061962A1 (de) * 1970-12-16 1972-06-29 Fichtel & Sachs Ag, 8720 Schweinfurt Radialkolbenpumpe mit Gleitschuh zwischen Kolben und Exzenter
DE2244920B2 (de) * 1972-09-13 1974-07-11 Paul Pleiger Maschinenfabrik, 5812 Herbede Radialkolbenmotor
DE3028999A1 (de) * 1980-07-31 1982-02-25 Fichtel & Sachs Ag, 8720 Schweinfurt Radialkolbenpumpe mit saugventil
DE3046753C2 (de) * 1980-12-12 1986-02-27 Mannesmann Rexroth GmbH, 8770 Lohr Hydrostatische Radialkolbenpumpe
JPS59500231A (ja) * 1982-01-19 1984-02-16 ユニパツト　アクチエンゲゼルシヤフト ラジアルピストン液圧機械
JPH0216370A (ja) * 1988-07-01 1990-01-19 Kayaba Ind Co Ltd ラジアルピストンポンプ
ES2076746T3 (es) * 1991-01-30 1995-11-01 Barmag Luk Automobiltech Bomba de pistones radiales.
EP0520286B1 (fr) * 1991-06-27 1995-12-20 LuK Automobiltechnik GmbH & Co. KG Pompe à pistons radiaux
DE4310062C2 (de) * 1993-03-27 2003-07-03 Continental Teves Ag & Co Ohg Radialkolbenmaschine
DE19518198A1 (de) * 1995-05-18 1996-11-21 Luk Automobiltech Gmbh & Co Kg Radialkolbenpumpe

Also Published As

Publication number Publication date
ES2184129T3 (es) 2003-04-01
DE19640596A1 (de) 1998-04-02
WO1998014704A1 (fr) 1998-04-09
EP0929743A1 (fr) 1999-07-21
DE59708963D1 (de) 2003-01-23

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