EP2188525B1 - Pompe, notamment pompe de carburant à haute pression - Google Patents

Pompe, notamment pompe de carburant à haute pression Download PDF

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Publication number
EP2188525B1
EP2188525B1 EP08802955A EP08802955A EP2188525B1 EP 2188525 B1 EP2188525 B1 EP 2188525B1 EP 08802955 A EP08802955 A EP 08802955A EP 08802955 A EP08802955 A EP 08802955A EP 2188525 B1 EP2188525 B1 EP 2188525B1
Authority
EP
European Patent Office
Prior art keywords
pump
drive shaft
pump piston
coupling device
indirectly
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.)
Not-in-force
Application number
EP08802955A
Other languages
German (de)
English (en)
Other versions
EP2188525A1 (fr
Inventor
Friedrich Boecking
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2188525A1 publication Critical patent/EP2188525A1/fr
Application granted granted Critical
Publication of EP2188525B1 publication Critical patent/EP2188525B1/fr
Not-in-force 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
    • 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
    • F04B1/0439—Supporting or guiding means for the pistons

Definitions

  • the invention relates to a pump, in particular high-pressure fuel pump according to the preamble of claim 1.
  • Such a pump is through the DE 73 05 570 U known, which represents the closest prior art.
  • This pump has at least one pump piston, which is tightly guided in a cylinder bore of a housing part of the pump.
  • the pump also has a drive shaft, which is provided with a drive section in the form of a cam or eccentric, by means of which the at least one pump piston is driven at least indirectly in a lifting movement.
  • the at least one pump piston is acted upon by a spring element at least indirectly to the drive portion of the drive shaft.
  • the spring element is designed as a bow spring, which is connected to the pump piston and which extends over the circumference of the drive shaft on the opposite side of the drive shaft and is fixed there.
  • the bow spring forms a coupling element which extends past the drive shaft.
  • a pump having at least one pump piston which is tightly guided in a cylinder bore of a housing part of the pump.
  • the pump also has a drive shaft, which is provided with a drive section in the form of a cam or eccentric, by means of which the at least one pump piston is driven at least indirectly in a lifting movement.
  • the at least one pump piston is acted upon by a spring element at least indirectly to the drive portion of the drive shaft.
  • the spring element is also designed here as a bow spring, which is connected to the pump piston and which extends over the circumference of the drive shaft on the opposite side of the drive shaft and is fixed there. Again, a large space over the circumference of the drive shaft is thus required, resulting in a corresponding size of the pump.
  • the pump according to the invention with the features of claim 1 has the advantage that the coupling device is arranged to save space, whereby the size of the pump can be kept low.
  • the pump according to the invention with the features of claim 1 has the advantage that by the arrangement of the spring element on the pump piston opposite side of the drive shaft, the housing part in the cylinder bore surrounding area with large
  • Wall thickness can be formed so that little or no
  • Training according to claim 2 is a simple design and space-saving
  • FIG. 1 fragmentary a pump in a longitudinal section
  • FIG. 2 the pump according to a modified version in a cross section along line II-II in FIG. 1
  • FIG. 3 a modified version of the pump in cross-section II-II.
  • a pump is shown, in particular a high-pressure fuel pump for a fuel injection of a
  • the pump has a housing 10 which may be formed in several parts and in which in a housing part 12, a rotationally driven drive shaft 14 is rotatably disposed about a rotation axis 15.
  • the drive shaft 14 is in the housing part 12 via two in the direction of the axis of rotation 15 of the drive shaft In a region lying between the two bearing points, the drive shaft 14 has at least one drive section 16, which is a cam or an eccentric
  • the pump has at least one or more pump elements, each with a pump piston 20 which is driven by the drive portion 16 of the drive shaft 14 at least indirectly in a lifting movement in at least approximately radial direction to the axis of rotation 15 of the drive shaft 14.
  • the pump piston 20 is tightly guided in a cylinder bore 22 of a housing part 24 of the pump. With its end facing away from the drive shaft 14, the pump piston 20 in the cylinder bore 22 defines a pump working chamber 26.
  • the pump working chamber 26 has a connection with an inlet 34 leading from a feed pump 32 via an inlet check valve 30 opening into the latter, via which the pump working chamber 26 radially inward to the axis of rotation 15 of the drive shaft 14 directed suction stroke of the pump piston 20 is filled with fuel.
  • the pump working chamber 26 also has an outlet check valve 36 which opens out of this connection with a drain 38 which leads, for example, to a high-pressure fuel accumulator 40 and fuel via the delivery stroke of the pump piston 20 directed radially outward from the rotational axis 15 of the drive shaft 14 the pump working space 26 is displaced.
  • the housing part 24 has a flange-like region 42, which rests on the housing part 12, and a protruding from the region 42 cylindrical projection 44 which extends into an at least approximately radially to the axis of rotation 15 of the drive shaft 14 extending opening 46 which is formed for example as a bore, protrudes in the housing part 12.
  • the cylinder bore 22 extends from the end face of the projection 44 through the projection 44 into the region 42, where the pump working chamber 26 is arranged.
  • the inlet valve 30 and the outlet valve 36 are arranged.
  • a larger diameter centering collar 43 is provided in relation to the projection 44, which enters the bore 46 with little play and ensures centering of the housing part 24 with respect to the housing part 12.
  • the roller tappet 48 comprises a sleeve-shaped tappet body 50 guided in the bore 46 of the housing part 24, a roller shoe 52 inserted in the tappet body 50 and a roller 54 rotatably mounted in a housing 53 in the roller shoe 52.
  • the roller 54 rolls on the double cam 16 and is slid in the receptacle 53.
  • the plunger body 50 may also be guided over its inner jacket on the projection 44 of the housing part 24.
  • the pump piston 20 has an enlarged diameter in relation to the area guided in the cylinder bore 22 in the region of the piston foot, via which the pump piston 20 is coupled to the roller tappet 48 in the direction of its longitudinal axis
  • the drive portion 16 of the drive shaft 14 is formed as an eccentric, wherein the pump piston 20 rests directly or via a plunger, such as a cup tappet 148, on the eccentric or on a rotatably mounted on the eccentric ring 150.
  • the ring 150 may have an at least approximately flat flattening 152 in the region of the abutment of the pump piston 20 or of the plunger 148.
  • the installation of the pump piston 20 via the roller tappet 48 on the drive section 16 of the drive shaft 14 during the suction stroke of the pump piston 20 is ensured by a spring element 56.
  • the spring element 56 is arranged on the pump piston 20 opposite side of the drive shaft 14 in the housing 10 of the pump via a coupling device 58 at least indirectly on the pump piston 20 at.
  • the coupling device 58 is connected to the plunger body 50 of the roller tappet 48 and the plunger 148 and thus indirectly via this with the pump piston 20.
  • the coupling device 58 has two carrier-shaped parts 60, wherein in each case a carrier 60 laterally adjacent to the drive section 16th the drive shaft 14 is arranged.
  • the carriers 60 are designed such that they are as shown in FIG FIG.
  • the carrier 60 as in the Figures 2 and 3 illustrated a central hub-like region 62 with a large width in the region of the drive shaft 14 and to these subsequent, of the drive shaft 14 radially extending arms 64 with a smaller width.
  • the arms 64 are arranged at least approximately diametrically opposite each other.
  • a slot 66 is respectively introduced, through which the drive shaft 14 passes.
  • the two carriers 60 of the coupling device 58 are preferably formed identically in order to keep the production costs low.
  • the arms 64 of the carriers 60 of the coupling device 58 which extend to the tappet body 50, are connected at their end regions to the tappet body 50 or the tappet 148, for example by means of screws, rivets, by a welded connection or in some other way.
  • the arms 64 of the carrier 60 of the coupling device 58 extend approximately up to the level of the foot of the pump piston 20 and terminate at a distance in front of the end face of the projection 44 of the housing part 24.
  • the on the pump piston 20 remote from the side of the drive shaft 14 arranged arms 64 of the carrier 60 of the coupling device 58 are connected to each other by means of a plate-shaped member 68 at their ends.
  • the spring element 56 is designed, for example, as a cylindrical helical compression spring and clamped between the component 68 and a housing 10 of the pump, the drive portion 16 of the drive shaft 14 arranged adjacent stationary support 70.
  • the stationary support 70 is arranged at a sufficient distance from the drive section 16 in order to avoid contact with the drive section 16 during the rotation of the drive shaft 14.
  • the pump piston 20 performs a lifting movement together with the roller tappet 48.
  • This lifting movement also carries out the coupling device 58, wherein the spring element 56 is alternately compressed and relaxed.
  • the coupling device 58 Through the elongated holes 66 in the carriers 60 of the coupling device 58, the lifting movement of the coupling device 58 with respect to the drive shaft 14 is made possible.
  • Due to the arrangement of the spring element 56 on the pump piston 20 opposite side of the drive shaft 14 is between the portion 44 of the housing part 24 and the bore 46 in the housing part 12 only an annular gap with a small width for receiving the plunger body 50 is required.
  • the plunger body 50 can be designed with a small wall thickness, so that the annular gap is correspondingly narrow can be held.
  • the pump may also have a plurality, for example two pump pistons 20.
  • the two pump pistons 20 can be arranged at an angle of about 90 ° about the axis of rotation 15 of the drive shaft 14 to each other rotated, in which case the associated spring element 56 acts on each pump piston 20 via a coupling device 58, which on the pump piston 20 opposite side of Drive shaft 14 is arranged.
  • the coupling devices 58 of the two pump pistons 20 preferably extend in the direction of the axis of rotation 15 of the drive shaft 14 to each other, so that they do not interfere with each other.

Landscapes

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

Claims (6)

  1. Pompe, notamment pompe de carburant haute pression, comprenant un boîtier (10, 12, 24), un arbre d'entraînement (14) qui est entraîné en rotation et qui présente au moins une portion d'entraînement (16), au moins un piston de pompe (20) qui est guidé de manière hermétique dans un alésage cylindrique (22) d'une partie de boîtier (24) de la pompe et qui est entraîné de manière au moins indirecte en un mouvement alternatif par la portion d'entraînement (16) de l'arbre d'entraînement (14), l'au moins un piston de pompe (20) étant sollicité par un élément de ressort (56) au moins de manière indirecte vers la portion d'entraînement (16) de l'arbre d'entraînement (14), l'élément de ressort (56) étant disposé du côté de l'arbre d'entraînement (14) opposé au piston de pompe (20) et venant en prise par le biais d'un dispositif d'accouplement (58) s'étendant devant l'arbre d'entraînement (14) au moins de manière indirecte sur le piston de pompe (20), caractérisée en ce que le dispositif d'accouplement (58) présente deux supports (60), un support (60) étant à chaque fois disposé latéralement à côté de la portion d'entraînement (16) de l'arbre d'entraîneinent (14) et étant connecté au moins de manière indirecte au piston de pompe (20).
  2. Pompe selon la revendication 1, caractérisée en ce que les deux supports (60) du dispositif d'accouplement (58) présentent à chaque fois un trou oblong (66) à travers lequel passe l'arbre d'entraînement (14).
  3. Pompe selon la revendication 2, caractérisée en ce que les supports (60) du dispositif d'accouplement (58), vus dans la direction de l'axe de rotation (15) de l'arbre d'entraînement (14), présentent à chaque fois une région centrale (62) de grande largeur, dans laquelle est disposé le trou oblong (66), et présentent à chaque fois deux bras (64) de plus petite largeur opposés l'un à l'autre et partant de la région centrale (62).
  4. Pompe selon la revendication 3, caractérisée en ce que les bras (64) des supports (60) du dispositif d'accouplement (58) tournés vers le piston de pompe (20) sont connectés au niveau de leurs régions d'extrémité au moins de manière indirecte au piston de pompe (20).
  5. Pompe selon la revendication 3 ou 4, caractérisée en ce que l'élément de ressort (56) est serré entre les régions d'extrémité des bras (64) du dispositif d'accouplement (58) opposés au piston de pompe (20) et un appui (70) fixe disposé à proximité de l'arbre d'entraînement (14).
  6. Pompe selon l'une quelconque des revendication précédentes, caractérisé en ce que le piston de pompe (20) s'applique par le biais d'un élément de support (48) sur la portion d'entraînement (16) de l'arbre d'entraînement (14) et en ce que le dispositif d'accouplement (58) est connecté à l'élément de support (48).
EP08802955A 2007-08-16 2008-08-01 Pompe, notamment pompe de carburant à haute pression Not-in-force EP2188525B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007038525A DE102007038525A1 (de) 2007-08-16 2007-08-16 Pumpe, insbesondere Kraftstoffhochdruckpumpe
PCT/EP2008/060172 WO2009021865A1 (fr) 2007-08-16 2008-08-01 Pompe, notamment pompe de carburant à haute pression

Publications (2)

Publication Number Publication Date
EP2188525A1 EP2188525A1 (fr) 2010-05-26
EP2188525B1 true EP2188525B1 (fr) 2011-07-20

Family

ID=40010491

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08802955A Not-in-force EP2188525B1 (fr) 2007-08-16 2008-08-01 Pompe, notamment pompe de carburant à haute pression

Country Status (8)

Country Link
US (1) US8337178B2 (fr)
EP (1) EP2188525B1 (fr)
JP (1) JP5119332B2 (fr)
KR (1) KR20100042646A (fr)
CN (1) CN101779038B (fr)
AT (1) ATE517257T1 (fr)
DE (1) DE102007038525A1 (fr)
WO (1) WO2009021865A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008000824A1 (de) * 2008-03-26 2009-10-01 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe
DE102010041340A1 (de) * 2010-09-24 2012-03-29 Robert Bosch Gmbh Spannstift
CN101985920B (zh) * 2010-10-27 2012-07-04 牛彦波 一种水切割机或水清洗机用环形超高压增压器
JP2013130114A (ja) * 2011-12-21 2013-07-04 Bosch Corp 燃料供給ポンプ
JP5677329B2 (ja) * 2012-01-20 2015-02-25 日立オートモティブシステムズ株式会社 電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ
DE102014220878A1 (de) * 2014-10-15 2016-04-21 Continental Automotive Gmbh Kraftstoffhochdruckpumpe

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1893216A (en) * 1928-03-15 1933-01-03 Abraham M Babitch Linkage for fuel pumps
US1893217A (en) * 1928-09-10 1933-01-03 Abraham M Babitch Fuel pump with lost motion lever
US2036452A (en) * 1934-12-06 1936-04-07 Gen Motors Corp Fuel pump
US2139347A (en) * 1936-04-08 1938-12-06 Gen Motors Corp Fuel pump
US2359960A (en) * 1943-08-12 1944-10-10 Chicago & Southern Air Lines I Pumping mechanism
US3314365A (en) * 1964-08-24 1967-04-18 Douglas E Ritchie Direct acting variable pump
DE7305570U (de) 1973-02-14 1973-08-16 Zahnradfabrik Friedrichshafen Ag Federnde Halterung des Kolbens in einer Radialkolbenmaschine
US3924970A (en) * 1973-11-28 1975-12-09 Gen Motors Corp Electrically controlled fuel pump
DE4027794C2 (de) * 1990-09-01 2002-06-20 Continental Teves Ag & Co Ohg Hydraulische Radialkolbenpumpe
DE19503621A1 (de) * 1995-02-03 1996-08-08 Bosch Gmbh Robert Hubkolbenpumpe
DE19848040A1 (de) 1998-10-17 2000-04-20 Bosch Gmbh Robert Kolbenpumpe zur Kraftstoffhochdruckversorgung
US6506033B2 (en) * 2000-10-26 2003-01-14 Okenseiko Co., Ltd. Miniature pump with ball-plate drive
JP4439723B2 (ja) * 2000-12-28 2010-03-24 株式会社ミクニ 燃料ポンプ
DE102008000824A1 (de) * 2008-03-26 2009-10-01 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe

Also Published As

Publication number Publication date
JP2010537096A (ja) 2010-12-02
CN101779038B (zh) 2012-11-14
WO2009021865A1 (fr) 2009-02-19
ATE517257T1 (de) 2011-08-15
US8337178B2 (en) 2012-12-25
EP2188525A1 (fr) 2010-05-26
JP5119332B2 (ja) 2013-01-16
KR20100042646A (ko) 2010-04-26
CN101779038A (zh) 2010-07-14
DE102007038525A1 (de) 2009-02-19
US20110200463A1 (en) 2011-08-18

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