EP1596065B1 - Pompe radiale avec masse d'equilibrage - Google Patents

Pompe radiale avec masse d'equilibrage Download PDF

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Publication number
EP1596065B1
EP1596065B1 EP20050103658 EP05103658A EP1596065B1 EP 1596065 B1 EP1596065 B1 EP 1596065B1 EP 20050103658 EP20050103658 EP 20050103658 EP 05103658 A EP05103658 A EP 05103658A EP 1596065 B1 EP1596065 B1 EP 1596065B1
Authority
EP
European Patent Office
Prior art keywords
pump
shaft
radial
balancing weight
rotor
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 - Fee Related
Application number
EP20050103658
Other languages
German (de)
English (en)
Other versions
EP1596065A1 (fr
Inventor
Ngoc-Tam Vu
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.)
Continental Automotive GmbH
Original Assignee
VDO Automotive AG
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 VDO Automotive AG filed Critical VDO Automotive AG
Publication of EP1596065A1 publication Critical patent/EP1596065A1/fr
Application granted granted Critical
Publication of EP1596065B1 publication Critical patent/EP1596065B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/001—Noise damping

Definitions

  • the invention relates to a radial piston pump with a drive shaft mounted in a pump housing and at least one pump unit driven by the drive shaft.
  • the radial piston pump has a pump housing in which a pump shaft is rotatably mounted. On the pump shaft, an eccentric portion is formed on which a cam ring is slidably guided. On the cam preferably support several, with respect to the drive shaft radially in the pump housing longitudinally movably guided pump piston.
  • Each pump piston is assigned a suction valve and a pressure valve. During the intake stroke, fuel is supplied to the pump cylinder from the low pressure region. After the compression stroke, the compressed fuel passes via the pressure valve to a common high-pressure accumulator, the so-called common rail.
  • Such a radial piston pump is usually preceded by a fuel priming pump, which supplies the fuel from the fuel tank of the high-pressure pump.
  • the fuel feed pump is usually driven by an electric motor or via the camshaft.
  • the invention is characterized in that the balancing weight arranged on the pump shaft is at the same time a rotor of a blocking-vane pump which serves as a fuel priming pump acts.
  • the fuel feed pump can be structurally arranged very close to the radial piston pump, resulting in a particularly compact design.
  • the prefeed pump can be produced by a particularly small number of components, which facilitates assembly and significantly reduces manufacturing costs.
  • the balance weight preferably has the same eccentricity as the eccentric section of the pump shaft.
  • the mass of the balance weight can then be determined by the thickness or the outer circumference of the balance weight.
  • An advantageous embodiment of the invention provides that the balance weight is connected to the pump shaft via a shaft-hub connection.
  • Shaft-hub connections are easy to make and ensure a secure connection between the balance weight and the pump shaft.
  • the one shaft-hub connection is designed as a positive connection.
  • the positive connection allows a particularly secure connection between the pump shaft and the balance weight. A release of the connection during pump operation is thereby excluded.
  • splined shaft profiles, serrations or polygonal profiles are suitable as a form-locking connection. It is also possible to positively connect the positive connection between the balance weight and the pump shaft by additional elements such as feather keys, sliding spring or transverse pins.
  • a particularly advantageous embodiment of the invention provides that the positive connection is formed such that the balance weight can be fixed only in a predetermined position on the pump shaft. As a result, the installation of the balance weight on the pump shaft is greatly facilitated.
  • the positive connection is designed such that the centrifugal force of the balance weight of Centrifugal force of the eccentric is opposite. An error during assembly is reliably avoided because the balance weight can only be fixed in a predetermined position.
  • a further advantageous embodiment of the invention provides that the pump shaft has a cantilevered end portion on which the balance weight is arranged.
  • a receiving profile for the counterweight can be formed in a particularly simple manner.
  • the balance weight can then be easily attached to the cantilevered end.
  • the balance weight can not be detached from the pump shaft, it is Favor additionally secured by a securing element.
  • wedges which are driven between the balance weight and the pump shaft are suitable for securing.
  • the shaft and the hub on a receiving groove. Through the receiving groove in both components, the mounting position is clearly defined to each other.
  • the rotor of the Sperrulatelpumpe is designed as a rotary valve.
  • the prefeed pump to an inlet and an outlet window is formed, which is opened or closed by the rotor designed as a rotary valve.
  • the fuel feed pump is integrated into the pump housing of the radial piston high-pressure pump.
  • the integration of the fuel feed pump allows a particularly compact design of the pump unit.
  • the radial piston pump according to the invention is thus characterized by the fact that the counterweight can additionally be used as a rotor for a fuel feed pump. This makes it possible to form a particularly inexpensive and simply constructed pump unit, consisting of the radial piston high-pressure pump and the fuel priming pump.
  • FIG. 1a shows a radial section through the radial piston high pressure pump.
  • the radial piston high-pressure pump consists essentially of a pump housing 1, in which a pump shaft 2 is rotatably mounted.
  • the pump shaft 2 has an eccentric section 3.
  • On the eccentric 3, a cam ring 11 is slidably mounted.
  • the cam ring 11 has a number of the pump piston 4 corresponding number of flats.
  • the pump piston 4 are based on sliding blocks 12 on the flattenings of the cam ring 11 from.
  • the pump pistons 4 are reciprocated during pump operation by the eccentric portion of the pump shaft 2 in the pump cylinder 5. They alternately perform a suction and a compression stroke.
  • the pump shaft 2 has a cantilevered end portion 10.
  • the cantilevered end portion 10 has two flats 7 which serve for the positive reception of a balance weight 6.
  • the compensating weight 6 has an opening which has a shape corresponding to the cantilever-mounted end area 10, so that there is a positive connection between the cantilever-mounted end area 10 and the compensating weight 8.
  • the balance weight is additionally secured with a securing element 13.
  • the securing element 13 is preferably introduced into a groove formed both in the pump shaft and in the balance weight 6 and clamps the two components together. Wedges are particularly suitable for this purpose.
  • the trained both in the balance weight 6 and in the pump shaft groove also ensures that the balance weight 6 can be attached only in one position on the pump shaft 2. As a result, assembly errors can be avoided and the balance weight 6 is always properly aligned with the eccentric portion 3 of the pump shaft 2.
  • the balance weight 6 has the same eccentricity as the eccentric portion 3 of the pump shaft 2. However, the balance weight 6 is arranged opposite the eccentric by 180 °, displaced on the pump shaft 2. As a result, the balance weight 6 generates a centrifugal force during pump operation, which counteracts the centrifugal force of the eccentric. The centrifugal forces cancel each other, which effectively avoids torsional vibrations of the pump.
  • the balancing weight of the balancing weight 6 can be determined via the eccentricity s of the balancing weight 6 and the thickness or the diameter of the balancing weight 6.
  • balance weight 6 is not attached to a cantilevered end portion 10, but is pushed onto the pump shaft 2 prior to assembly.
  • the cantilevered end allows However, a particularly simple installation of the balance weight 6 after assembly of the pump housing and pump shaft.
  • the balance weight 6 can be used simultaneously as a rotor 8 for a Kraftstoffvor suitmpe 9.
  • the fuel feed pump 9 consists essentially of the formed as a rotor 8 balance weight 6, an outer ring 15 and a fixed locking wing 16.
  • At the front side of the fuel feed 9 is an inlet and a drain window 17, 18 formed by the fluid on or can flow out.
  • the pump chamber 19 results from the eccentric arrangement of the rotor 8 with respect to the outer ring 15. This results in a sickle-shaped pump chamber 19 which moves with the rotation of the drive shaft 2 and the rotor 8 along the circumference.
  • fuel can thereby enter the pump chamber 19 through the inlet window 17 or run out of the pump chamber 19 through the outlet window 18.
  • the blocking wing 16 is pressed by a spring 20 against the rotor 8 and thereby seals the inlet side and the outlet side of the pump chamber from each other.
  • FIGS. 2a to 2d The following will be sent to the FIGS. 2a to 2d describes the operation of the Sperrwügelpumpe.
  • the rotor 8 In FIG. 2a the rotor 8 is in its upper starting position. In this case, the outflow window 18 is completely closed by the rotor 8, so that no fuel can flow out of the sickle-shaped pump chamber 19.
  • the inlet window 17, however, is not completely closed by the rotor 8 and fuel can flow through the inlet window 17 in the crescent-shaped pump chamber 19.
  • FIG. 2b the rotor has rotated 90 ° counterclockwise. In this position, the rotor 8 completely closes the inlet window 17.
  • the crescent-shaped pump chamber 19 has also shifted by 90 ° in the counterclockwise direction, so that now the outlet window 18 is released from the rotor 8 and the fuel from the outlet window 18 can flow out of the fuel feed pump 9.
  • the balancing weight can advantageously be used simultaneously as a rotor for a fuel priming pump.
  • Kraftstoffvor suitpumpe is particularly suitable a Sperrerielpumpe with a fixed barrier wing.
  • the pump housing may be formed directly in a pump cover of the pump housing.
  • the proposed radial piston pump is particularly suitable for high-pressure fuel generation in modern common-rail injection systems.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (8)

  1. Pompe à piston radial, en particulier pompe à piston radial pour générer une haute pression de carburant, avec un carter de pompe (1) où est monté un arbre de pompe (2) rotatif avec une partie excentrique (3) et avec au moins un piston de pompe (4) entraîné par l'arbre de pompe (2), logé dans un cylindre de pompe (5) de manière à être déplaçable en va-et-vient radialement à l'arbre de pompe (2), une masse d'équilibrage (6) étant disposée sur l'arbre de pompe (2), laquelle compense un déséquilibre de l'arbre de pompe (2) pendant le fonctionnement de la pompe, caractérisée en ce que la masse d'équilibrage (6) est simultanément un rotor (8) d'une pompe à palette fonctionnant comme pompe de refoulement préliminaire du carburant (9).
  2. Pompe à piston radial selon la revendication 1,
    caractérisée en ce que la masse d'équilibrage (6) présente la même excentricité (e) que la partie excentrique (3) de l'arbre de pompe (2).
  3. Pompe à piston radial selon la revendication 1 ou la revendication 2,
    caractérisée en ce que la masse d'équilibrage (6) est reliée à l'arbre de pompe (2) par un raccord arbre-moyeu (7).
  4. Pompe à piston radial selon la revendication 3,
    caractérisée en ce que le raccord arbre-moyeu (7) est réalisé comme raccord par complémentarité de forme.
  5. Pompe à piston radial selon la revendication 4,
    caractérisée en ce que le raccord par complémentarité de forme est réalisé de telle sorte que la masse d'équilibrage (6) ne peut être fixée que dans une position prescrite sur l'arbre de pompe (2).
  6. Pompe à piston radial selon l'une des revendications précédentes,
    caractérisée en ce que l'arbre de pompe (2) présente une zone d'extrémité volante (10) où la masse d'équilibrage (6) est montée.
  7. Pompe à piston radial selon l'une des revendications précédentes,
    caractérisée en ce que le rotor (8) de la pompe à palette est réalisé comme tiroir rotatif.
  8. Pompe à piston radial selon l'une des revendications précédentes,
    caractérisée en ce que la pompe de refoulement préliminaire du carburant (9) est intégrée au carter de pompe (1).
EP20050103658 2004-05-11 2005-05-03 Pompe radiale avec masse d'equilibrage Expired - Fee Related EP1596065B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004023195 2004-05-11
DE200410023195 DE102004023195B4 (de) 2004-05-11 2004-05-11 Radialkolbenpumpe mit Ausgleichsgewicht

Publications (2)

Publication Number Publication Date
EP1596065A1 EP1596065A1 (fr) 2005-11-16
EP1596065B1 true EP1596065B1 (fr) 2008-04-02

Family

ID=34939649

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20050103658 Expired - Fee Related EP1596065B1 (fr) 2004-05-11 2005-05-03 Pompe radiale avec masse d'equilibrage

Country Status (2)

Country Link
EP (1) EP1596065B1 (fr)
DE (2) DE102004023195B4 (fr)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04219472A (ja) * 1990-12-19 1992-08-10 Aisin Seiki Co Ltd ラジアルプランジャポンプ
DE19848035A1 (de) * 1998-10-17 2000-04-20 Bosch Gmbh Robert Radialkolbenpumpe für Kraftstoffhochdruckerzeugung
DE19953248A1 (de) * 1999-11-04 2001-05-23 Luk Fahrzeug Hydraulik Radialkolbenpumpe
DE10210300B4 (de) * 2002-03-08 2008-11-20 Robert Bosch Gmbh Pumpenelement für eine Hochdruckpumpe und Hochdruckpumpe mit steuerbarer Fördermenge

Also Published As

Publication number Publication date
DE102004023195B4 (de) 2006-06-14
DE102004023195A1 (de) 2005-12-08
DE502005003525D1 (de) 2008-05-15
EP1596065A1 (fr) 2005-11-16

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