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WO2012059315A1 - Pompe, en particulier pompe à carburant haute pression - Google Patents

Pompe, en particulier pompe à carburant haute pression Download PDF

Info

Publication number
WO2012059315A1
WO2012059315A1 PCT/EP2011/068097 EP2011068097W WO2012059315A1 WO 2012059315 A1 WO2012059315 A1 WO 2012059315A1 EP 2011068097 W EP2011068097 W EP 2011068097W WO 2012059315 A1 WO2012059315 A1 WO 2012059315A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
drive shaft
support element
roller
pump 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.)
Ceased
Application number
PCT/EP2011/068097
Other languages
German (de)
English (en)
Inventor
Matthias Greiner
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
Priority to CN201180052756.5A priority Critical patent/CN103201499B/zh
Priority to EP11770768.7A priority patent/EP2635797B1/fr
Publication of WO2012059315A1 publication Critical patent/WO2012059315A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or 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
    • 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
    • F04B1/0417—Cams consisting of two or more cylindrical elements, e.g. rollers
    • 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
    • F04B1/043—Hydraulic arrangements
    • 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.
  • a pump in the form of a high-pressure fuel pump is through the
  • This pump has a pump element with a pump piston, which is guided in a cylinder bore of a housing part and which is driven by a drive shaft in a lifting movement.
  • the drive shaft has for this purpose a cam or eccentric.
  • the pump piston is supported via a support element in the form of a roller shoe and a roller rotatably mounted in this on the drive shaft.
  • the pump piston and the support element are acted upon by a helical compression spring to the drive shaft.
  • the pump piston and the support member are inserted into a ram tube which is slidably guided in a bore of a housing part with little play in the direction of the stroke movement of the pump piston.
  • the support member with the roller and the ram tube together form a roller tappet, by which the rotational movement of the drive shaft is converted into a stroke movement of the pump piston.
  • the helical compression spring is held at its end facing the drive shaft on the support element and at its end facing away from the drive shaft on a housing part about its longitudinal axis held non-rotatably.
  • roller tappet By the roller tappet are arranged in the bore of the housing part above and below the roller tappet spaces separated. In the support element therefore continuous openings are required to between these spaces the lifting movement of the roller tappet to allow a volume or pressure compensation. Through these openings of the support element, the production is also complicated and the strength of the support element is possibly reduced.
  • the pump according to the invention with the features of claim 1 has the advantage that their production is simplified because no ram tube and no hole in a housing part are required. In addition, no through openings in the support element for pressure and volume compensation are required because no tight guide between the support member and a housing part is present.
  • FIG. 2 shows a section of the pump, designated by I I in FIG. 1, in an enlarged view
  • Figure 3 shows the pump fragmentary in a cross section along line
  • Figure 4 shows the pump fragmentary in a view in the direction of arrow IV in
  • FIG. 2 is a diagrammatic representation of FIG. 1
  • Figure 5 shows the pump fragmentary in a section along line V-V in
  • Figure 6 shows the pump fragmentary in a view in the direction of arrow VI in
  • FIG. 1 A first figure.
  • FIGS. 1 to 6 show a pump which is in particular a high-pressure fuel pump for a fuel injection device of an internal combustion engine.
  • the pump has a housing 10, which may be designed in several parts and in which a rotationally driven drive shaft 14 is rotatably mounted about an axis of rotation 15.
  • the drive shaft 14 has at least one cam 16, which may also be a multiple cam.
  • the pump has at least one or more pump elements 18, each having a pump piston 20 which is at least indirectly driven by the cam 16 of the drive shaft 14 in a lifting movement in at least approximately radial direction to the axis of rotation 15 of the drive shaft 14 and in the direction of the longitudinal axis 21 of the pump piston 20 becomes.
  • the pump does not have its own drive shaft 14 and the pump piston 20 of the pump element 18 is driven by a shaft of the internal combustion engine having a cam 16 or eccentric.
  • the pump piston 20 is tightly guided in a cylinder bore 22 of a housing part 24 of the pump.
  • the housing part 24 has a flange-like region 25 and a cylindrical projection 26 protruding therefrom towards the drive shaft 14, in which the cylinder bore 22 extends. With its end facing away from the drive shaft 14, the pump piston 20 in the cylinder bore 22 defines a pump working space 28.
  • the pump working space 28 has an inlet check valve 30 opening into this connection with an inlet 32 leading, for example, from a feed pump, via which the pump working space 28 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 28 also has an outlet check valve 34 which opens out of this connection with a drain 36, which for example leads to a high-pressure fuel accumulator 38 and fuel via the delivery stroke of the pump piston 20 directed radially outward from the rotation axis 15 of the drive shaft 14 the pump working space 28 is displaced.
  • the pump piston 20 is supported indirectly via a support element in the form of a roller shoe 42 on the cam 16 of the drive shaft 14.
  • the roller shoe 42 has on its side facing the drive shaft 14 a concave curved
  • Recess 44 in which an at least approximately circular cylindrical roller 46 is rotatably mounted, wherein the axis of rotation of the roller 46 is denoted by 48.
  • the roller 46 extends on the cam 16 of the drive shaft 14 from.
  • the housing 10 of the high-pressure fuel pump is filled with fuel and the fuel is lubricated between the roller 46 and the recess 44 of the roller shoe
  • roller shoe 42 The roller shoe 42 and the associated pump piston 20 are acted upon by a prestressed spring in the form of a cylindrical helical compression spring 50 to the drive shaft 14, so that the roller 46 is held in contact with the cam 16.
  • the helical compression spring 50 surrounds the projection 26 of the housing part 24 and the longitudinal axis is at least approximately identical to the longitudinal axis 21 of the pump piston 20. From the flange portion 25 of the housing part 24 is inwardly, the neck 26 coaxially surrounding a collar 52 protruding. The collar 52 has, as shown in FIG. axis 21 of the pump piston 20 extending groove 54. The end of the spring 50 protrudes into the annulus formed between the boss 26 and the collar 52 and the end portion 56 of the last turn of the spring 50 is bent radially outward from the longitudinal axis 21 and projects into the groove 54. The spring 50 is thus non-rotatably connected to the housing part 24 via the end region 56 of its last turn about the longitudinal axis 21.
  • the roller shoe 42 is approximately cylindrical in shape with a round cross-section, the recess 44 being provided on its side facing the drive shaft 14. On the side facing away from the drive shaft 14 of the roller shoe
  • the pump piston 20 is firmly connected to the roller shoe 42, in particular by the end region of the pump piston 20 being pressed into the bore 58 of the roller shoe 42.
  • Roller shoe 42 is a reduced in diameter relative to the roller shoe 42 collar 60 which projects into the drive shaft 14 facing the end of the spring 50.
  • a groove 62 extending in the direction of the longitudinal axis 21 is formed on the circumference of the collar 60, and the end region 64 of the last turn of the spring 50 is bent inwards radially to the longitudinal axis 21 and protrudes into the groove 62.
  • the spring 50 is thus non-rotatably connected to the roller shoe 42 about the end portion 64 of its last turn about the longitudinal axis 21.
  • the recess 44 in the roller shoe 42 is for example formed so that it as shown in Figure 3, the roller 46 on the circumference of an angle ⁇ of at most 180 ° surrounds.
  • the recess 44 surrounds the roller 46 for less than 180 °, in particular about 140 °.
  • a holding element 66 is provided, which is arranged on the drive shaft 14 facing side of the roller shoe 42 and on
  • Roller shoe 42 is attached.
  • the roller shoe 42 has, on its side facing the drive shaft 14, a recess 68 which is circular in cross-section, for example.
  • the holding element 66 is disc-shaped with the recess 68 corresponding cross-section and inserted into the recess 68, in particular pressed into the recess 68.
  • the holding element 66 has, as shown in Figures 3 and 5, a slot-shaped opening 70, through which the roller 46 projects toward the drive shaft 14, wherein the width of the slot 70 in the radial direction with respect to the axis of rotation 48 of the roller 46 is smaller than the diameter the roller 46, so that the roller 46 can not pass through the slot 70.
  • the holding member 66 comes in its final assembled end position at the bottom 69 of the recess 68 of the roller shoe 42 for conditioning without the holding member 66 presses against the roller 46.
  • the lateral edges 71 of the slot 70 may be bevelled as shown in Figure 3, wherein the width of the slot 70 increases toward the roller 46 out.
  • the bevel of the edges 71 of the slot 70 sharp edges are avoided during start-up of the roller 46.
  • the lateral edges 71 of the slot 70 may also be rounded.
  • the length of the slot 70 in the direction of the axis of rotation 48 of the roller 46 is only slightly larger than the length of the roller 46.
  • the holding member 66 holds the roller 46 in the recess 44 of the roller shoe 42 and forms a support for the roller 46, on which Roller 46 can come to rest in the direction of its axis of rotation 48.
  • the holding element 66 is preferably made of a material with high wear resistance, for example hard metal or ceramic.
  • the pointing in the direction of its axis of rotation 48 axial ends 47 of the roller 46, with which they can start on the support member 66 may be formed convex rounded.
  • the support member 42 is guided only via the pump piston 20 in the direction of the lifting movement of the pump piston 20 and has no guide in a housing part. A sufficiently large distance is present between the support element 42 and the surrounding housing part, so that fuel can flow between the underside of the drive shaft 14 and the top side of the support element 42 facing away from the drive shaft 14.
  • the support member 42 and the support member 66 need therefore have no through openings, which allow a flow through the support member 42 and the support member 66 between the bottom and top. If necessary, the support member 42 and the retainer 66 may still be provided with apertures 74 to facilitate flow therethrough.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention concerne une pompe comportant au moins un élément de pompe (18) muni d'un piston de pompe (20) guidé dans un alésage de cylindre (22) d'un élément carter (24) et entraîné indirectement par un arbre d'entraînement (14) de manière à effectuer un mouvement alternatif. Le piston de pompe (20) s'appuie sur l'arbre d'entraînement (14) par l'intermédiaire d'un élément d'appui (42) et d'un galet (46) monté de manière à pouvoir tourner dans l'élément d'appui (42), l'élément d'appui (42) étant guidé au moins indirectement en direction du mouvement alternatif du piston de pompe (20). L'élément d'appui (42) et le piston de pompe (20) sont soumis en direction de l'arbre d'entraînement (14) à l'action d'un ressort (50), le ressort (50) étant relié à l'élément d'appui (42) par son extrémité tournée vers l'arbre d'entraînement (14), de manière non rotative autour de son axe longitudinal (21), et à l'élément carter (24) par son extrémité opposée à l'arbre d'entraînement (14), de manière non rotative autour de son axe longitudinal (21). Le piston de pompe (20) est fixé de manière fixe à l'élément d'appui (42), qui est guidé uniquement par l'intermédiaire du piston de pompe (20) dans la direction du mouvement alternatif du piston de pompe (20).
PCT/EP2011/068097 2010-11-05 2011-10-17 Pompe, en particulier pompe à carburant haute pression Ceased WO2012059315A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201180052756.5A CN103201499B (zh) 2010-11-05 2011-10-17 泵
EP11770768.7A EP2635797B1 (fr) 2010-11-05 2011-10-17 Pompe, en particulier pompe à carburant haute pression

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010043512 DE102010043512A1 (de) 2010-11-05 2010-11-05 Pumpe, insbesondere Kraftstoffhochdruckpumpe
DE102010043512.0 2010-11-05

Publications (1)

Publication Number Publication Date
WO2012059315A1 true WO2012059315A1 (fr) 2012-05-10

Family

ID=44925499

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/068097 Ceased WO2012059315A1 (fr) 2010-11-05 2011-10-17 Pompe, en particulier pompe à carburant haute pression

Country Status (4)

Country Link
EP (1) EP2635797B1 (fr)
CN (1) CN103201499B (fr)
DE (1) DE102010043512A1 (fr)
WO (1) WO2012059315A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2915994A1 (fr) * 2014-03-06 2015-09-09 Continental Automotive GmbH Agencement de poussoir et pompe

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2064700A (en) * 1979-09-13 1981-06-17 Leco Hydraulics Ltd Ball piston
WO1998014722A1 (fr) * 1996-10-02 1998-04-09 Jurij Manfreda Ensemble piston pour moteur a pistons hydrauliques radiaux
WO2005088125A1 (fr) * 2004-03-09 2005-09-22 Robert Bosch Gmbh Pompe haute pression, notamment pour un dispositif d'injection de carburant d'un moteur a combustion interne
WO2009098095A1 (fr) * 2008-02-04 2009-08-13 Robert Bosch Gmbh Came sans effort transversal pour pompes haute pression à rampe commune
DE102008000699A1 (de) 2008-03-17 2009-09-24 Robert Bosch Gmbh Kraftstoffhochdruckpumpe

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2440949Y (zh) * 2000-09-08 2001-08-01 无锡威孚集团有限公司 喷油泵
CN2663678Y (zh) * 2003-07-28 2004-12-15 上海东维燃油喷射有限公司 强力型喷油泵总成

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2064700A (en) * 1979-09-13 1981-06-17 Leco Hydraulics Ltd Ball piston
WO1998014722A1 (fr) * 1996-10-02 1998-04-09 Jurij Manfreda Ensemble piston pour moteur a pistons hydrauliques radiaux
WO2005088125A1 (fr) * 2004-03-09 2005-09-22 Robert Bosch Gmbh Pompe haute pression, notamment pour un dispositif d'injection de carburant d'un moteur a combustion interne
WO2009098095A1 (fr) * 2008-02-04 2009-08-13 Robert Bosch Gmbh Came sans effort transversal pour pompes haute pression à rampe commune
DE102008000699A1 (de) 2008-03-17 2009-09-24 Robert Bosch Gmbh Kraftstoffhochdruckpumpe

Also Published As

Publication number Publication date
EP2635797A1 (fr) 2013-09-11
CN103201499A (zh) 2013-07-10
DE102010043512A1 (de) 2012-05-10
EP2635797B1 (fr) 2015-10-07
CN103201499B (zh) 2016-10-05

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