EP1906011B1 - Pompe à fluide, en particulier pompe à carburant haute pression pour systèmes d'injection de moteurs à combustion interne - Google Patents

Pompe à fluide, en particulier pompe à carburant haute pression pour systèmes d'injection de moteurs à combustion interne Download PDF

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Publication number
EP1906011B1
EP1906011B1 EP20070116361 EP07116361A EP1906011B1 EP 1906011 B1 EP1906011 B1 EP 1906011B1 EP 20070116361 EP20070116361 EP 20070116361 EP 07116361 A EP07116361 A EP 07116361A EP 1906011 B1 EP1906011 B1 EP 1906011B1
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EP
European Patent Office
Prior art keywords
pump
pump piston
support body
sleeve
shaped support
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
EP20070116361
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German (de)
English (en)
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EP1906011A2 (fr
EP1906011A3 (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
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Continental Automotive GmbH
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Publication of EP1906011A2 publication Critical patent/EP1906011A2/fr
Publication of EP1906011A3 publication Critical patent/EP1906011A3/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
    • 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
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • 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
    • F04B1/0408—Pistons
    • 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
    • F04B1/0439—Supporting or guiding means for the pistons

Definitions

  • the present invention relates to a fluid pump, in particular high-pressure fuel pump for injection systems of internal combustion engines, according to the preamble of claim 1.
  • Such a fluid pump is for example from the DE 100 39 210 A1 and comprises a pump piston, which is guided for reciprocating movement in the direction of a pump piston axis in a pump cylinder, and a sleeve-shaped support body, which is guided on an outer peripheral surface of the pump cylinder in the direction of the pump piston axis and is in driving connection with the pump piston.
  • the arrangement of the sleeve-shaped support body has the advantage that it can be introduced directly into a more or less rigid and rigid pump cylinder during operation of the pump transverse to the pump piston axis occurring transverse forces. On the pump piston then act only forces in the direction of the pump piston axis, which drive the piston to reciprocate.
  • the intrinsically undesirable transverse forces are generated by an eccentric, in which an eccentric performs a wobbling movement and a connected to the pump piston shoe not only charged for the desired stroke of the pump piston in the direction of the pump piston axis, but also introduces lateral forces in the shoe ,
  • the known pump has a number of disadvantages.
  • the connection is accomplished by a first and a second part, wherein the first part is fixedly connected to one end of the pumping piston (eg by means of a press fit) and in positive connection with the second part, which in turn is in positive connection with a shoulder of the pump sleeve-shaped support body is.
  • the two connecting parts should be relatively small dimensions. However, this adversely affects the reliability or fatigue strength of the connection.
  • the fluid pump according to the invention is characterized in that the sleeve-shaped support body is guided on an outer peripheral surface of the pump cylinder, the retaining ring is partially disposed in an inner circumferential groove of the sleeve-shaped support body, wherein the pump piston also further an adjoining, projecting beyond one end of the sleeve-shaped support body, even further widened second foot portion, on which rests the end of the sleeve-shaped support body.
  • the pump piston has an integrally formed with the pump piston, widened pump piston foot, which thus no longer a realized by separate parts connection with the actual pump piston or pump piston body (which goes back and forth in the pump cylinder) and advantageous even replace the shoe of the known construction. It is also essential for the invention that this one-piece design of a widened pump piston foot is simultaneously used for a particularly simple connection to the sleeve-shaped support body, which is realized by means of a securing ring.
  • the above-mentioned special design of the pump piston foot with the widened first foot section and an adjoining, even further widened second foot section, which are used in the manner described above, are essential for the invention.
  • This can also z.
  • a force introduced by a pump drive (eg eccentric drive) onto the pump piston foot in the direction of the pump piston axis in one direction (which normally corresponds to the so-called pump stroke) is largely or even substantially completely not via the securing ring, but instead the support of the support body is transmitted to the second body portion on the support body.
  • a pump drive eg eccentric drive
  • suction stroke also satisfies a relatively small dimensioned circlip connection, since the forces occurring in this stroke are usually relatively small.
  • the construction according to the invention is compatible with very simply designed supporting bodies, since only one inner peripheral groove is to be provided on the supporting body, but the rest of the design is very variable.
  • the pump piston foot is important that this shape can be optimally adapted to the expected during operation mechanical loads.
  • the pump piston together with its pump piston foot is produced as a rotationally symmetrical milled part.
  • the respective mechanical loads optimally adapted or weight-optimized pump piston can be formed inexpensively together with its outer circumferential groove. If necessary, subsequent machining of the pump piston foot can then take place, in particular in those areas which later come into contact with an eccentric drive component of the pump, which, however, does not represent any appreciable additional expenditure.
  • the invention is particularly suitable for use in a so-called radial piston pump, in particular a radial piston pump with a plurality of pump pistons, the z. B. can be arranged in a common plane.
  • the pump comprises an eccentric shaft for driving a plurality of conveyor units accommodated in a pump housing, each of which has a pump piston guided for reciprocating movement in the direction of a respective pump piston axis in a respectively associated pump cylinder.
  • the sleeve-shaped support body is guided substantially free of play on the outer peripheral surface of the pump cylinder.
  • This can be z. B. accomplish in a simple manner by a cylindrical inner peripheral surface portion of the sleeve-shaped support body slides on a corresponding cylindrical outer peripheral surface portion of the pump cylinder.
  • the relevant sections of the support body as well each of the pump cylinder have a hollow cylindrical shape.
  • the outer circumferential groove of the pump piston foot and the inner peripheral groove of the sleeve-shaped supporting body are substantially directly adjacent to one another. This advantageously results in a very direct introduction of acting on the pump piston stem transverse forces in the support body and a particularly resilient entrainment of these two components in the direction of the pump piston axis. If the outer peripheral groove of the pump piston foot and the inner circumferential groove of the sleeve-shaped support body are not adjacent to each other directly or slightly spaced, it is preferred that the material of the locking ring is arranged in the two grooves at least 90% in the direction of the pump piston axis (and accordingly at most 10) % is located outside the grooves).
  • the retaining ring extends continuously over at least 70% of the circumferential length of the two grooves, the retaining ring preferably having a uniform cross-section (eg rectangular or circular) along its continuous circumferential extent.
  • the maximum extent of the securing ring in the direction of the pump piston axis is preferably at least as great as the maximum extent of the securing ring in the transverse direction (orthogonal to the pump piston axis).
  • the locking ring can be formed in a particularly simple manner as a so-called snap ring or Seeger ring.
  • the above-mentioned return spring may be formed as a spiral compression spring and surrounding the sleeve-shaped support body, wherein the coil spring can be supported in the direction of the pump piston axis on the one hand on a shoulder of the pump cylinder or a housing portion and on the other hand on a shoulder of the sleeve-shaped support body.
  • a widened pump piston foot is provided anyway, the second-mentioned support of the return spring can also be advantageous be provided directly on an outer peripheral region of the pump piston.
  • the training described above is well suited, in which one end of the sleeve-shaped support body rests on the pump piston or its second foot section.
  • the return spring is supported on the one hand on a shoulder of the pump cylinder and on the other hand on the second foot portion.
  • Fig. 1 illustrates the known construction of a delivery unit 1 of a high-pressure fuel pump, as it z. B. from the DE 100 39 210 A1 is known and described in detail there.
  • the illustrated delivery unit 1 is one of several pump delivery units that are operated by a shared eccentric shaft (not shown).
  • the feed unit 1 is used to fuel (eg, diesel for a storage injection system) from a supply line 2 (suction) via a first check valve 3 in a pump working space 4 and then via a second check valve 5 with high Pressure (eg over 1,500 bar) in a discharge line 6 (pressure chamber) to promote.
  • the described components are housed in a housing structure, of which in Fig. 1 a first housing part 7 and a second housing part 8 can be seen.
  • the pump further comprises a pump piston 10, which is guided for reciprocating movement in the direction of a pump piston axis A in a pump cylinder 12, during a Saubhubs (in Fig. 1 Down) to promote fuel from the supply line 2 via the check valve 3 in the pump chamber 4 and during a pumping stroke (in Fig. 1 to top) to compress the fuel located in the pump working space 4 or to deliver via the check valve 5 under high pressure to the pressure chamber 6.
  • a pump piston 10 which is guided for reciprocating movement in the direction of a pump piston axis A in a pump cylinder 12, during a Saubhubs (in Fig. 1 Down) to promote fuel from the supply line 2 via the check valve 3 in the pump chamber 4 and during a pumping stroke (in Fig. 1 to top) to compress the fuel located in the pump working space 4 or to deliver via the check valve 5 under high pressure to the pressure chamber 6.
  • the pump cylinder 12 is in the illustrated embodiment, an integrally projecting from the housing part 8 and projecting into a cylindrical recess of the housing part 7 section.
  • the pump comprises a sleeve-shaped support body 14, which is guided on an outer peripheral surface of the pump cylinder 12 in the direction of the pump piston axis A and by means of a connection arrangement 16 is in driving connection with the pump piston 10.
  • an eccentric ring 18 penetrated by an eccentric section of the eccentric shaft performs a tumbling motion whose component is transmitted to the pump piston 10 parallel to the pump piston axis A via a sliding shoe 20.
  • a return spring 22 coil compression spring
  • the upper end is supported on a shoulder of the pump cylinder 12 and the lower end is supported on a shoulder of the support body 14, the lower end in turn such shaped with an outer periphery of the shoe 20 cooperates, that the force acting on the support body 14 spring force is transmitted to the shoe 20 and thus via the connection assembly 16 on the pump piston 10 and this leads down.
  • connection assembly 16 is constructed comparatively complicated and problematic in terms of the reliability of the connection thus created.
  • Fig. 2 shows a conveyor unit 1a, wherein for the sake of simplicity some components are omitted, which are not essential for the modification.
  • a pump piston 10a which is guided for reciprocating movement in the direction of a .Pumpkolbenachse A in a pump cylinder 12a, and a sleeve-shaped support body 14a, which is guided on an outer peripheral surface of the pump cylinder 12a in the direction of the pump piston axis A.
  • the pump piston 10a at its in Fig. 2 lower end of an integrally formed with the pump piston 10a, widened pump piston 30a on.
  • the pump piston foot 30a has a widened first foot section 32a and a second foot section 34a, which adjoins it at the bottom and projects beyond an end of the sleeve-shaped support body 14a.
  • the driving connection between the pump piston 10a and the support body 14a is realized by a snap ring 36a, which is partially disposed in an outer circumferential groove of the pump piston 30a and partially in an inner circumferential groove of the sleeve-shaped support body 14a.
  • the outer circumferential groove of the pump piston foot 30a is arranged in the region of the first foot portion 32a and adjoins directly to the inner circumferential groove of the substantially hollow cylindrical supporting body 14a.
  • the pump piston foot 30a which is formed integrally with the pump piston 10a, serves as a tappet, which, for B. in a conventional manner by means of a Exzentertriebs in Direction of the pump piston axis A can be charged to drive the pump piston 10a upwards (pumping stroke).
  • the provision of the pump piston 10a in the suction stroke is again by a return spring 22a, which is supported on the one hand on a shoulder of the pump cylinder 12a and on the other hand on the outer circumference of the second foot portion 34a.
  • the restoring force of the spring 22a is thus exerted directly on the pump piston foot 30a and the pump piston 10a connected in one piece therewith.
  • the actuation force exerted on the pump piston foot 30a by the pump impulse used during the pumping stroke is likewise transmitted directly to the pump piston 10a and to the support body 14a, since the in Fig. 2 lower end of the support body 14a also rests on an upper side of the second foot portion 34a.
  • Fig. 2 the design shown can be extensively modified in the context of the invention. As a particularly favorable it has z. However, for example, when a cross-sectional area or diameter of the pump plunger 10a initially gradually increases in a transitional area to the first leg portion 32a, the cross-sectional area or diameter of the first leg portion 32a (apart from the outer circumferential groove) is substantially constant, and the cross-section or the diameter at the transition to the second foot portion 34a increases again abruptly to a footprint for the Return spring 22a and / or provide the support body 14a.

Landscapes

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

Claims (4)

  1. Pompe à fluide, en particulier pompe de carburant à haute pression pour systèmes d'injection de moteurs à combustion interne, comprenant au moins un piston de pompe (10a), qui est actionné dans un cylindre de pompe (12a) pour suivre un mouvement de va-et-vient dans le sens d'un axe de piston de pompe (A), et un élément de support en forme de douille (14a), qui est actionné dans le sens de l'axe de piston de pompe (A) et qui est en liaison d'entraînement avec le piston de pompe (10a), lequel piston de pompe (10a) présente un élargissement formant le pied de piston de pompe (30a), piston de pompe (10a) et pied de piston de pompe (30a) étant formé d'un seul tenant, et la liaison d'entraînement étant assurée par un circlip (36a), qui est positionné en partie dans une rainure de la périphérie externe du pied de piston de pompe (30a), lequel pied de piston de pompe (30a) présente une première section de pied (32a) élargie, dans laquelle est positionnée la rainure de la périphérie externe destiné au circlip (36a),
    caractérisée en ce que le l'élément de support en forme de douille est actionné au niveau d'une surface périphérique externe du cylindre de la pompe, en ce que le circlip est positionné, en partie, dans une rainure de la périphérie interne de l'élément de support en forme de douille (14a) et en ce que le pied de piston de la pompe (30a) présente, en outre, une seconde section de pied, plus élargie encore (34a) que la première et rejoignant celle-ci et dépassant une extrémité de l'élément de support en forme de douille (14a), sur laquelle seconde section est posée l'extrémité de l'élément de support en forme de douille (14a).
  2. Pompe à fluide selon la revendication 1, dans laquelle la rainure de la périphérie externe du pied de piston de pompe (30a) et la rainure de la périphérie interne de l'élément de support en forme de douille (14a) sont, sensiblement, immédiatement contigus l'une à l'autre.
  3. Pompe à fluide selon l'une quelconque des revendications précédentes, comprenant un ressort de rappel (22a) dont l'effort, situé entre le cylindre de pompe (12a) et le piston de pompe (10a), opère dans le sens de l'axe du piston de pompe (A).
  4. Pompe à fluide selon la revendication 3, dans laquelle le ressort de rappel (22a) s'appuie, d'une part, sur un épaulement du cylindre de pompe (12a) et, d'autre part, sur la seconde section du pied (34a).
EP20070116361 2006-09-14 2007-09-13 Pompe à fluide, en particulier pompe à carburant haute pression pour systèmes d'injection de moteurs à combustion interne Active EP1906011B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200610043187 DE102006043187B3 (de) 2006-09-14 2006-09-14 Fluidpumpe, insbesondere Hochdruck-Kraftstoffpumpe für Einspritzsysteme von Brennkraftmaschinen

Publications (3)

Publication Number Publication Date
EP1906011A2 EP1906011A2 (fr) 2008-04-02
EP1906011A3 EP1906011A3 (fr) 2008-10-29
EP1906011B1 true EP1906011B1 (fr) 2011-05-18

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20070116361 Active EP1906011B1 (fr) 2006-09-14 2007-09-13 Pompe à fluide, en particulier pompe à carburant haute pression pour systèmes d'injection de moteurs à combustion interne

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EP (1) EP1906011B1 (fr)
DE (1) DE102006043187B3 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010042484A1 (de) * 2010-10-15 2012-04-19 Robert Bosch Gmbh Hochdruckpumpe für eine Kraftstoffeinspritzvorrichtung

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH256927A (de) * 1946-02-09 1948-09-15 Haahr Poul Pumpe.
US4322546A (en) 1979-06-07 1982-03-30 American Cyanamid Company 15-Deoxy-16-hydroxy-16-allenyl prostane derivatives of the E and F series
US4355546A (en) * 1979-08-09 1982-10-26 Lucas Industries Limited Reciprocable plunger fuel injection pump
DE10039210A1 (de) * 2000-08-10 2002-02-28 Siemens Ag Radialkolbenpumpe mit zweiteiligem Federträger
EP1415092A1 (fr) * 2001-08-08 2004-05-06 CRT Common Rail Technologies AG Pompe d'alimentation haute pression
DE10200792A1 (de) * 2002-01-11 2003-07-31 Bosch Gmbh Robert Kraftstoffpumpe für eine Brennkraftmaschine
JP3861846B2 (ja) * 2003-04-23 2006-12-27 株式会社デンソー 回転直線変換装置および燃料噴射ポンプ
DE102004013245A1 (de) * 2004-03-18 2005-10-06 Robert Bosch Gmbh Radialkolbenpumpe

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Publication number Publication date
EP1906011A2 (fr) 2008-04-02
DE102006043187B3 (de) 2008-04-03
EP1906011A3 (fr) 2008-10-29

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