WO2013075949A1 - Pompe haute pression - Google Patents

Pompe haute pression Download PDF

Info

Publication number
WO2013075949A1
WO2013075949A1 PCT/EP2012/072105 EP2012072105W WO2013075949A1 WO 2013075949 A1 WO2013075949 A1 WO 2013075949A1 EP 2012072105 W EP2012072105 W EP 2012072105W WO 2013075949 A1 WO2013075949 A1 WO 2013075949A1
Authority
WO
WIPO (PCT)
Prior art keywords
roller
roller shoe
pump
sectional area
pressure pump
Prior art date
Application number
PCT/EP2012/072105
Other languages
German (de)
English (en)
Inventor
Werner Haag
Friedrich Boecking
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 JP2014542761A priority Critical patent/JP5897730B2/ja
Priority to CN201280056396.0A priority patent/CN103946535B/zh
Priority to EP12786954.3A priority patent/EP2783099B1/fr
Priority to BR112014012071A priority patent/BR112014012071A8/pt
Publication of WO2013075949A1 publication Critical patent/WO2013075949A1/fr

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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • F04B27/0428—Arrangements for pressing or connecting the pistons against 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication

Definitions

  • Combustion chambers injected.
  • the injection pressure is currently about 1600 bar to 2000 bar and will be increased in the future up to 2500 bar.
  • the highly compressed fuel is nowadays mostly provided via a storage (common rail) system.
  • a storage (common rail) system In this memory system, the by means of a
  • High-pressure pump compressed fuel introduced.
  • the high-pressure pump is usually a piston compressor whose pump pistons are moved by means of cams in a translatory direction. Most are in such
  • a roller is arranged, which is arranged in a part-cylindrical recess in the roller shoe and rolls during operation on the cam.
  • the cam in turn is firmly connected to a drive shaft, wherein the
  • the High-pressure pump is preceded by a prefeed pump, which draws fuel from a storage container and at its output provides a flow at a pressure which is supplied to both a pumping element for compression and a pump housing surrounding the pump housing for lubrication purposes. Due to the high pressures to be generated are the
  • the high pressure pump has a
  • Pump housing with a fuel-filled pump housing interior, wherein in the pump housing at least one pump element is arranged with a pump piston.
  • the pump piston is indirectly supported by a plunger body and a roller on a cam or an eccentric drive shaft.
  • the plunger body is drivable in the direction of a central axis via the cam or the eccentric in an oscillating movement. With the plunger body a roller shoe is firmly connected in the direction of the central axis.
  • the roller shoe has a substantially part-cylindrical
  • the roller shoe has at least one lubrication chamber, wherein the at least one
  • Lubricating chamber is supplied during the oscillating movement of the plunger body of the roller fuel from the pump housing interior.
  • the fuel supply can here
  • Lubricant or fuel pressure built up is so high that the contact surfaces between the roller and plunger body are lifted apart from each other about 1-2 ⁇ .
  • the increased fuel supply, on the one hand lubrication can be improved at the contact surfaces.
  • the heat generated at the contact surfaces can be dissipated better and thus the formation of so-called "hot spots", ie local overheating of the lubricant, prevented.
  • This embodiment of the roller shoe in conjunction with the lubrication chamber formed in the tappet body thus becomes a high-pressure pump provided in the opposite to the known from the prior art high-pressure pumps due to the increased supply of lubricant and the load, respectively, a surface pressure at the contact points between the roller and the roller shoe can be increased.
  • the at least one lubrication chamber extends substantially parallel to one
  • the slot-shaped opening which points from the lubricating chamber vin to the role.
  • the slot-shaped opening or the slot may be designed such that the lubricant forms a uniformly thick lubricating film after the feed on the roller.
  • the slot will be the
  • Lubricating chamber be arranged such that through the slot
  • supplied fuel is conveyed from the roller into a narrowing lubrication gap to the contact surface of the roller on the roller shoe.
  • Beispiet two mutually mirror-image formed lubrication chambers are formed with respect to the roller opposite each other in the roller shoe.
  • the lubrication chamber is fluid-conductively connected to the plunger space by means of at least one first opening having a first cross-sectional area.
  • the lubrication chamber is fluid-conductively connected to the pump interior by means of at least one second opening with a second cross-sectional area. A whole of the first
  • Cross-sectional areas forms a first total cross-sectional area.
  • An entirety of the second cross-sectional areas forms a second overall cross-sectional area.
  • the first total cross-sectional area and the second total cross-sectional area are different from each other.
  • the reel body may be configured to have only a first and a second opening, respectively. Due to the throttle pressure can build up in the lubrication chamber. This pressure built up in the lubrication chamber can be used to pump fuel through the slot-shaped opening or slot of the
  • the first and the second opening may, for example, be designed as a bore, as a rule the lubrication chamber will be designed such that the fuel circulating between the first and the second opening is deflected through the lubrication chamber towards the roller.
  • the lubrication chamber may be configured such that the fuel is directed perpendicularly or at an angle to the roll.
  • the smaller overall cross-section at a position in the plunger body be selected such that the fuel is supplied to the roller either during an upward movement or during a downward movement of the plunger body.
  • the first and the second total cross-sectional area are designed such that in the at least one lubrication chamber, an overpressure of at most 2 bar is generated.
  • Fuel supply respectively lubricant supply, to ensure contact surfaces of roller and roller shoe.
  • the second total cross-sectional area is smaller than the first total cross-sectional area.
  • the fuel is advantageously the
  • the roller shoe of the high-pressure pump has a roller shoe body and a
  • roller shoe cover on. The roller shoe body and the
  • Roller shoe cover are firmly connected to each other in rotational and translational direction.
  • the roller shoe body is between the
  • the roller shoe body is limited by an end face facing the drive shaft.
  • the end face and the lateral circular cylindrical recess defining lateral surface intersect along a line.
  • the line lies in a tangential plane formed to the lateral surface, the tangential plane and the central axis enclosing an angle.
  • the angle is between 17 ° and 25 °. Due to the low angle, it is possible to thinly execute the roller shoe body with respect to the known from the prior art roller shoe bodies, in which this angle partially reaches 90 °. Due to a concomitant reduced material requirement of the roller shoe and the moving masses can be reduced. Reduced masses promote the creep strength of the high-pressure pump. Also, due to the good accessibility of the part-cylindrical recess, which results from the small angle of 17 ° to 25 °, can be in an excellent manner the surface of the partially cylindrical recess by means of carbon or a
  • Coating carbon compound as a sliding layer and / or wear protection layer in the plasma Coating carbon compound as a sliding layer and / or wear protection layer in the plasma. Also, roller shoe body and can
  • Roller shoe cover be made of different materials.
  • the roller shoe cover may be made of a material whose specific gravity is lower than that of the roller shoe body.
  • Lubrication gap formed between the line and the roller.
  • the fuel is supplied to the lubrication gap.
  • this lubrication gap will be about 20 ⁇ wide.
  • the fuel film drawn through the roller from the pump interior into the lubrication gap is about 3-6 pm thick.
  • the amount of fuel introduced into the lubrication gap by the lubrication chamber may be greater than the amount of fuel entrained by the roller as the fuel film.
  • the lubrication chamber is formed in the mechanically almost unloaded roller shoe cover.
  • the production of the roller shoe body can be decoupled from the production of the lubrication chamber.
  • the lubrication chamber can only by an interaction of
  • Roller shoe cover and roller shoe body are formed, for example, after joining the roller shoe cover to the roller shoe body.
  • the slot-shaped opening of the lubrication chamber may be formed in the surface.
  • one of the upper side of the roller shoe cover facing underside of the roller shoe body can be formed plan.
  • Roller shoe cover on an opposite side of the roller shoe body underside substantially parallel to the longitudinal direction of the roller edge.
  • the edge is spaced from the roller such that the edge deflects debris from the roller without adversely affecting a lubricating film on the roller.
  • the edge will preferably be spaced about 10 ⁇ from the roller.
  • the between 3-6 ⁇ thick lubricating film on the roll is not affected by the edge.
  • particles dragged along by the lubricating film may be removed from the roll so that it can not be dragged into the lubrication gap, particularly not into the contact surface of the roll on the roller shoe.
  • Roller shoe cover connected to the roller shoe body by means of a screw, clamp or latching connection.
  • the roller shoe cover of the high pressure pump engages behind the roller in cross section at least partially.
  • Roller shoe cover as a captive for the role in the assembly.
  • roller shoe cover of the high pressure pump integrally formed.
  • the roller shoe cover as Spritzgusstei! be educated.
  • the roller shoe cover may also be formed in several pieces. However, this can lead to higher manufacturing and assembly costs compared to the integrally formed roller shoe cover.
  • Roller shoe cover made of plastic.
  • Roller shoe and the plunger body of the high-pressure pump integrally formed.
  • FIG. 1 shows a high-pressure pump with one in a roller shoe
  • FIG. 2 shows a detail from that known from FIG.
  • FIG. 3 shows a roller shoe body in cross section
  • FIG. 4 shows a roller shoe cover in cross section.
  • FIG. 1 shows a high-pressure pump 2 for a fuel injection device of an internal combustion engine, the high-pressure pump 2 having a pump housing 4 with a pump housing interior 6 filled with fuel 100.
  • the pump housing 4 In the pump housing 4, at least one pump not shown here
  • Pump element arranged with a pump piston 8.
  • the pump piston 8 is supported on a tappet body 10 via a roller 12 on a cam 14 of a drive shaft 16. By a rotation of the drive shaft 16 in
  • the plunger body 10 has a roller shoe 18.
  • the roller shoe 18 has a part-cylindrical recess 20 which is formed here as a bore.
  • two opposing and mutually mirror-image formed lubrication chambers 22 are formed
  • the plunger body 10 divides the pump housing interior 6 in a plunger space 24 and a pump interior 26. This is located in the plunger space 24 of the
  • the plunger space 24 is fiuid valuedd connected to the pump interior 26.
  • the lubrication chamber 22 is connected to the plunger space 24 by a fuel injected in the roller shoe 18 first opening 28.
  • the lubrication chamber 22 is connected to the pump interior 26 by means of a fuel injected in the roller shoe 18 second opening 30. Both the plunger chamber 24 and the pump inner space 26 are filled with fuel 100 During the oscillating movement Z of the roller shoe 18, fuel 100 through the first opening 28 via the
  • Lubrication chamber 22 and the second opening 30 of the plunger chamber 24 to the pump interior 26 and vice versa This ensures that there is essentially no pressure difference between the plunger chamber 24 and the pump interior 26 during the oscillating movement Z.
  • the roller shoe 18 includes a between the roller 12 and the
  • the lubrication chamber 22 is formed in the made of plastic roller shoe cover 34.
  • the lubrication chamber 22 through an end face 44 of the roller shoe cover 34 facing Roller shoe body 32, which is formed as a flat bottom, and a contoured the roller shoe body 32 facing upper side 46 of
  • roller shoe cover 34 limited. Furthermore, the flat underside 44 and the contoured upper side 46 form a slot-shaped opening formed in the roller shoe cover 34 and facing the roller 12 in the form of a
  • FIG. 2 which shows a section of the high-pressure pump 2 known from FIG. 1, is that the underside 44 of the roller shoe body 32 and a lateral surface 42 delimiting the part-circular cylindrical recess 20 intersect along a line L.
  • the line L lies in a tangential plane T formed to the lateral surface 42.
  • Central axis I include an angle ⁇ .
  • the angle ⁇ is between 17 ° and 25 °.
  • the formed between the bottom 44 of the roller shoe body 32 and the roller shoe cover 34 and the roller 12 facing slot 36 is shown in phantom for clarity.
  • the slot 36 forms the narrowest point between the roller shoe body 32 and the
  • roller shoe cover 34 Furthermore, the lubrication chamber 22 is limited by this slot 36.
  • the bottom 48 forms at its intersection with a part-circular cylindrical recess 49, in which the roller 12 is partially received, an edge 50 from.
  • the edge 50 is approximately 10 ⁇ m away from the roller 12 during operation and serves to adhere particles from a roller 12 rotating during operation
  • FIG. 3 shows the roller shoe body 32 in cross section.
  • the lubrication chamber which is not visible here, is fuel-conductively connected to the plunger space 24 by means of two first openings 28.
  • the two first openings 28 each have one first cross-sectional area 52. The entirety of the first two
  • Cross-sectional areas 52 results in a first total cross-sectional area.
  • FIG. 4 shows the roller shoe cover 34 in cross section.
  • the lubrication chamber not shown here, with the pump interior by means of the second opening 30 is fuel conductively connected, wherein the second opening 30 has a second cross-sectional area 54, which is also the second
  • Opening 30 is a throttle.
  • the first and the second total cross-sectional area are dimensioned such that during the upward movement of the plunger body 10 in the lubrication chamber 22, a pressure up to 2 bar is formed
  • Roller shoe body 32 in the region of the contact surface 40 during operation spaced about 1-2 pm.
  • angle ⁇ of 17 ° to 25 °, it is possible in a simple manner to coat the lateral surface 42 of the part-cylindrical recess 20 in the plasma by means of carbon or carbon compounds. Since the formed in the roller shoe cover 34 edge 50 is only spaced from the roller 2 about 10 pm, which is separated from the roller 12 of the

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)

Abstract

L'invention concerne une pompe haute pression pour un dispositif d'injection de carburant d'un moteur à combustion interne. La pompe haute pression (2) comporte un carter de pompe (4) présentant un espace intérieur (6) rempli de carburant (100). Le carter de pompe (4) contient au moins un élément pompe comprenant un piston de pompe (8). Le piston de pompe (8) s'appuie indirectement sur une came (14) ou un excentrique d'un arbre d'entrée (16) au moyen d'un corps de coulisseau (10) et d'un galet (12). Le corps de coulisseau (10) peut être mis en mouvement oscillant (Z) en direction de l'axe central (I) au moyen de la came (14) ou de l'excentrique. Un patin à galet (18) est relié fixe au corps de coulisseau (10) en direction de l'axe central (I). Le patin à galet (18) présente un évidement (20) sensiblement cylindrique en partie pour le logement partiel du galet (12). Selon l'invention, le patin à galet (18) comporte au moins une chambre de lubrification (22) alimentant le galet (12) en carburant (100) provenant de l'espace intérieur (6) du carter de pompe lors du mouvement oscillant (Z) du corps de coulisseau (10).
PCT/EP2012/072105 2011-11-21 2012-11-08 Pompe haute pression WO2013075949A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2014542761A JP5897730B2 (ja) 2011-11-21 2012-11-08 高圧ポンプ
CN201280056396.0A CN103946535B (zh) 2011-11-21 2012-11-08 高压泵
EP12786954.3A EP2783099B1 (fr) 2011-11-21 2012-11-08 Pompe haute pression
BR112014012071A BR112014012071A8 (pt) 2011-11-21 2012-11-08 bomba de alta pressão

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011086703.1 2011-11-21
DE201110086703 DE102011086703A1 (de) 2011-11-21 2011-11-21 Hochdruckpumpe

Publications (1)

Publication Number Publication Date
WO2013075949A1 true WO2013075949A1 (fr) 2013-05-30

Family

ID=47178675

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/072105 WO2013075949A1 (fr) 2011-11-21 2012-11-08 Pompe haute pression

Country Status (6)

Country Link
EP (1) EP2783099B1 (fr)
JP (1) JP5897730B2 (fr)
CN (1) CN103946535B (fr)
BR (1) BR112014012071A8 (fr)
DE (1) DE102011086703A1 (fr)
WO (1) WO2013075949A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2548900A (en) * 2016-04-01 2017-10-04 Delphi Int Operations Luxembourg Sarl Tappet, high pressure pump comprising at least one tappet, engine comprising at least one tappet, engine comprising a high pressure pump having at least one

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012201302A1 (de) * 2012-01-31 2013-08-01 Robert Bosch Gmbh Hochdruckpumpe
DE102012019991A1 (de) * 2012-10-12 2014-04-17 Heidelberger Druckmaschinen Ag Antriebsvorrichtung und Stanzmaschine mit einer solchen Antriebsvorrichtung
DE102015210721A1 (de) * 2015-06-11 2016-12-15 Robert Bosch Gmbh Rollenstößel für eine Kolbenpumpe, Kolbenpumpe
GB201518964D0 (en) * 2015-10-27 2015-12-09 Delphi Internat Operations Luxembourg S À R L High pressure fuel pump
DE102016218909A1 (de) 2016-09-29 2018-03-29 Robert Bosch Gmbh Rollenstößel für eine Kolbenpumpe, Kolbenpumpe

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009029297A1 (de) * 2009-09-09 2011-03-10 Robert Bosch Gmbh Kolbenpumpe mit kavitationsfreiem Rollenschuh/Laufrollen-Verband
DE102010030202A1 (de) * 2010-06-17 2011-12-22 Robert Bosch Gmbh Stößelbaugruppe für eine Pumpe und Pumpe mit wenigstens einer Stößelbaugruppe
WO2012080330A1 (fr) * 2010-12-17 2012-06-21 Robert Bosch Gmbh Pompe haute pression

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Publication number Priority date Publication date Assignee Title
US5164356A (en) * 1991-11-12 1992-11-17 Appleton Papers Inc. Thermally-responsive record material
JPH05141216A (ja) * 1991-11-22 1993-06-08 Nippondenso Co Ltd 列型燃料噴射ポンプ
JPH05180116A (ja) * 1991-12-25 1993-07-20 Nippondenso Co Ltd 燃料噴射ポンプ
JPH05332222A (ja) * 1992-05-27 1993-12-14 Nippondenso Co Ltd 燃料噴射ポンプ
JP2004218459A (ja) * 2003-01-10 2004-08-05 Bosch Automotive Systems Corp 燃料供給用ポンプおよびタペット構造体
DE102007012705A1 (de) * 2007-03-16 2008-09-18 Robert Bosch Gmbh Hochdruckpumpe zur Förderung von Kraftstoff mit einem torsionsentkoppelten Druckfederelement in der Stößeleinrichtung
DE102008000699A1 (de) * 2008-03-17 2009-09-24 Robert Bosch Gmbh Kraftstoffhochdruckpumpe
DE102009028378A1 (de) * 2009-08-10 2011-02-17 Robert Bosch Gmbh Hochdruckpumpe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009029297A1 (de) * 2009-09-09 2011-03-10 Robert Bosch Gmbh Kolbenpumpe mit kavitationsfreiem Rollenschuh/Laufrollen-Verband
DE102010030202A1 (de) * 2010-06-17 2011-12-22 Robert Bosch Gmbh Stößelbaugruppe für eine Pumpe und Pumpe mit wenigstens einer Stößelbaugruppe
WO2012080330A1 (fr) * 2010-12-17 2012-06-21 Robert Bosch Gmbh Pompe haute pression

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2548900A (en) * 2016-04-01 2017-10-04 Delphi Int Operations Luxembourg Sarl Tappet, high pressure pump comprising at least one tappet, engine comprising at least one tappet, engine comprising a high pressure pump having at least one

Also Published As

Publication number Publication date
DE102011086703A1 (de) 2013-05-23
BR112014012071A2 (pt) 2017-06-13
EP2783099B1 (fr) 2016-08-31
BR112014012071A8 (pt) 2017-06-20
CN103946535B (zh) 2016-11-09
EP2783099A1 (fr) 2014-10-01
CN103946535A (zh) 2014-07-23
JP2015502484A (ja) 2015-01-22
JP5897730B2 (ja) 2016-03-30

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