WO1998048169A1 - Pompe a carburant haute pression - Google Patents

Pompe a carburant haute pression Download PDF

Info

Publication number
WO1998048169A1
WO1998048169A1 PCT/DE1998/000299 DE9800299W WO9848169A1 WO 1998048169 A1 WO1998048169 A1 WO 1998048169A1 DE 9800299 W DE9800299 W DE 9800299W WO 9848169 A1 WO9848169 A1 WO 9848169A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
pump
drive shaft
fuel pump
pressure fuel
Prior art date
Application number
PCT/DE1998/000299
Other languages
German (de)
English (en)
Inventor
Josef Guentert
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 EP98909323A priority Critical patent/EP0931219A1/fr
Priority to JP10544652A priority patent/JP2000512715A/ja
Publication of WO1998048169A1 publication Critical patent/WO1998048169A1/fr

Links

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
    • 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
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L41/00—Branching pipes; Joining pipes to walls
    • F16L41/08—Joining pipes to walls or pipes, the joined pipe axis being perpendicular to the plane of the wall or to the axis of another pipe
    • F16L41/10—Joining pipes to walls or pipes, the joined pipe axis being perpendicular to the plane of the wall or to the axis of another pipe the extremity of the pipe being screwed into the wall

Definitions

  • the invention is based on a high-pressure radial piston type fuel pump according to the features of the preamble of claim 1.
  • a high-pressure fuel pump known from the document US Pat. No. 4,952,121 has a plurality of pump pistons which are arranged at an angular distance from one another about a central drive shaft and which, by means of prestressed springs, bear with their radially inner ends on the circumferential surface of the drive shaft and which are each axially displaceable in a guide bore .
  • the pump pistons with their end faces facing away from the drive shaft, each delimit a pump work chamber in the guide bore, which can alternately be connected to a fuel-filled low pressure chamber and to a high pressure delivery line.
  • High fuel pressures of up to 2000 bar are built up in the pump workspace during the high-pressure delivery phase, so that the requirements placed on the sealing points and bores under high pressure are very high with regard to reliable sealing.
  • the known high-pressure fuel pump has the disadvantage that the high-pressure channels are characterized by a large number of Components of the high pressure pump extend, which considerably increases the effort with regard to a high pressure seal.
  • the large number of components on the known high-pressure fuel pump causes increased construction and assembly costs.
  • the high-pressure fuel pump according to the invention with the characterizing features of claim 1 has the advantage over the fact that all channels and sealing points subjected to high pressure are arranged in a single common, one-piece pump housing. In this way, in a structurally simple manner, the sealing points necessary on the additional components used are eliminated, which in addition to a reduction in the sealing points also results in a reduction in the construction work.
  • the pump pistons of the individual pump elements are axially movably guided in a simple manner in a guide bore, which is worked directly into the pump housing, so that additional
  • Cylinder liners can be dispensed with.
  • the sealing points required when closing the high-pressure lines in the pump housing and at a connection of a pressure port on the pump housing are also advantageously designed as “biting edges”, for which purpose the pair of sealing surfaces each have a flat sealing surface on a first component and a sharp sealing edge interacting with this on a second component When the components are braced against one another, a slight plastic deformation is achieved at the contact line between the sealing edge and the flat sealing surface, which ensures a very secure seal even at very high internal fuel pressures.
  • a further advantage of the high-pressure fuel pump according to the invention is provided by the exclusive loan Guiding the high pressure ducts within the pump housing ses one, so that additional, conductive components and seals on these components can be dispensed with.
  • the pressure valve on the pump work rooms that is necessary for the function and opens in the direction of the pressure port is completely in the respective high-pressure channel within the
  • Integrated pump housing Integrated pump housing.
  • the individual high-pressure ducts leading away from the respective pump work spaces lead via a common high-pressure manifold within the pump housing to the pressure connection nozzle, to which a high-pressure delivery line can be connected, which preferably opens into a high-pressure storage space, from which in turn injection lines to the injection valves projecting into the combustion chamber of the internal combustion engine dissipate (common rail).
  • Screw connections, fuel channels and pump pistons are arranged in a common pump housing, it is possible to decouple all high-pressure sealing points from one another and thus design them statically exact.
  • the common pump housing (mono block) is preferably designed as a one-piece steel part. This common pump housing enables not only a high level of tightness due to the reduction in the number of components, but also a very compact design, so that the entire pump space required can be reduced.
  • the high-pressure fuel pump according to the invention can optionally be closed with a cover and preferably has a receiving device for a mounting flange, via which it can be attached to the respective engine housing.
  • the modular and modular design of the high-pressure fuel pump enables the attachment of various flange shapes, so that it can be easily adapted to different installation requirements.
  • This modular design is made possible by the provision of a steel housing monoblock in which all high-pressure-carrying parts are integrated. On This monoblock can now be fitted with various additional components, such as adapters, pre-feed pumps, etc., preferably made of aluminum, as required.
  • the drive shaft of the high-pressure fuel pump according to the invention is advantageously designed as an eccentric shaft, but there are also other drive shaft shapes, e.g. Camshafts possible.
  • FIG. 1 shows a longitudinal section through the high-pressure fuel pump according to the invention and
  • FIG. 2 shows a cross section of the high-pressure fuel pump according to FIG. 1 along the section line II.
  • the exemplary embodiment of the high-pressure fuel pump according to the invention shown in FIGS. 1 and 2 in two sectional views has an approximately triangular pump housing 1.
  • this pump housing 1 which is preferably made of steel, an annular central recess 3 is provided, which is open in one axial direction and closed by an inner housing end face 5 in a second axial direction.
  • a central axial through hole 7 is provided, which serves as a bearing bush of a central drive shaft 9.
  • the drive shaft 9 is rotatably guided with an end piece 11 in the through bore 7 and has, at its portion protruding into the recess 3 of the pump housing 1, an eccentric shaft part 13 forming a drive cam. This with its axis from the axis of the drive shaft 9 displaced eccentric shaft part 13 has on its circumference a drain ring 15 made of hardened material.
  • the pump housing 3 has guide bores 17 running radially to the drive shaft 9, which are arranged at the same angular distance from one another around the central drive shaft 9 and in each of which a pump piston 19 is slidably guided.
  • the pump pistons 19 At their ends facing away from the pump working spaces 21 and protruding from the respective guide bore 17, the pump pistons 19 each have a slide shoe 23, the pump pistons 19 thereby are formed in one piece in the form of a valve lifter.
  • the slide shoe 23, which is enlarged in cross section with respect to the pump piston 19, is held in contact with the end ring 15 of the eccentric shaft part 13 of the drive shaft 9 by means of a spring 25 with its end face remote from the pump work space.
  • the spring 25 engages on the ring end face of the slide shoe 23 facing the pump work space and, on the other hand, is supported on the ring end face of the pump housing 1 which delimits the recess 3. It is advantageous to arrange the spring 25 coaxially with the pump piston 19 and to guide it in a corresponding ring opening 27 in the pump housing 1.
  • the guide bores 17 receiving the pump pistons 19 are closed radially outward by a closure piece 29 which is screwed into the pump housing 1 and which, with its inside face of the pump, presses a spacer disk 31 axially against a housing shoulder formed on the guide bore 17.
  • the spacer disk 31, with its end face facing the pump piston 19, delimits the pump working space 21 and also forms with this end face a valve seat surface for a disk-shaped valve member 33 which is held in contact with the spacer disk 31 by means of a leaf spring 35.
  • the spacer 31 has an axial through-bore 37, from which a radial bore 39 leads, which opens into a fuel supply line 41, which, on the other hand, originates from a fuel-filled low-pressure chamber, not shown.
  • Flow cross section from the fuel supply line 41 in the pump work chamber 21 is kept closed by the disc-shaped valve member 33 by the leaf spring 35.
  • the leaf spring 35 is supported on a cranked spring plate 43, which is clamped with its upper edge between the housing shoulder and the spacer 31.
  • a radial high-pressure bore 45 leads from the guide bore 17 of each pump piston 19 in the area of the pump work chamber 21, which opens into a high-pressure duct 47, the individual high-pressure ducts 47 via a common manifold (not shown in detail) inside the pump housing 1 to one into the pump housing 1 screwed discharge nozzle 49 open.
  • a high-pressure delivery line can be connected to this pressure connection 49, which on the other hand opens into a high-pressure storage space (common rail), from which in turn discharge the individual injection lines to the injection valves (not shown) which project into the combustion chamber of the internal combustion engine to be supplied.
  • a pressure valve 51 which opens in the direction of the pressure connection 49, is inserted into each high-pressure bore 45 and, in the exemplary embodiment, is designed as a check valve with a spherical valve member 53.
  • This valve ball 53 is held on a conical valve seat by means of a spring plate 55 and a valve spring 57, the valve spring 57 being supported on a counter stop 59 that can be screwed into the pump housing 1.
  • the sealing surfaces on the counter stop 59 and on the end face of the pressure connection 49 screwed into the housing 1 are designed as so-called biting edges, in which a flat sealing surface on a first component interacts with a sharp-edged sealing edge (cutting edge) on a second component, whereby when the components are braced against each other, a sealing plastic deformation along the line of contact of the flat and sharp-edged sealing surface is set.
  • the pump housing 1 also has, at its open end facing away from the end piece 11 of the drive shaft 9, an axially projecting tube extension 61 which forms a receptacle for a fastening flange 63 which forms a pump cover.
  • This mounting flange 63 is pushed with a corresponding inner recess in a sealing manner onto the tubular extension 61 and is axially fastened to the latter.
  • the fastening flange 63 is centered on the tube extension 61 and is preferably clamped to the pump housing 1 by means of fastening screws which are screwed into corresponding holes 71 in the pump housing 1 which form screw holes.
  • the mounting flange 63 has an axial through opening through which the free end of the drive shaft 9 projects and is sealingly guided there. There are also 63 mounting holes on the mounting flange 65 provided with which the high-pressure fuel pump can be attached to an engine housing. In addition, a cone 67 is provided at the free end of the drive shaft 9, via which a motor-side drive part can be attached to the drive shaft 9 in a rotationally locking manner. At its end facing away from the free end of the drive shaft 9, the through bore 7 in the pump housing 1 receiving the drive shaft 9 is sealed by a cover 69.
  • the high-pressure fuel pump works in the following manner.
  • a prefeed pump (not shown) delivers fuel from a low-pressure chamber, preferably a fuel storage tank, to the valve member 33 via the fuel supply line 41 and the bores 39, 37 in the spacer disk 31, this valve working as a suction valve.
  • the pump pistons 19 resting on the eccentric shaft part 13 are shifted up and down alternately.
  • the fuel located in the pump work chamber 21 is compressed to a very high fuel pressure of up to 2000 bar and thereby opens the pressure valve 51 arranged in the high-pressure bore 45, so that the fuel under high pressure passes through the high-pressure channel 47 and the common manifold to the pressure port 49 can flow. From there, the high-pressure fuel reaches the common high-pressure storage space (common rail) via the high-pressure delivery line, where it is stored to supply the injection lines to the injection valves. After passing through top dead center
  • the pump piston 19 is again displaced radially inward, the pressure in the pump working space 21 drops below a certain opening pressure and the pressure valve 51 closes again.
  • the high-pressure bore 45 open into the guide bore 17 in such a way that the pump piston 19 closes the inlet opening of the high-pressure bore 45 with its lateral surface from a certain piston stroke position.
  • the fuel pressure in the pump work chamber 21 drops again below the fuel pressure in the supply line 41, so that the valve member 33 of the suction valve lifts again from its seat and fuel is fed via the leaf spring 35 and the spring plate 43 into the Pump work space 21 can flow.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne une pompe à carburant haute pression comportant plusieurs pistons de pompe (19) disposés, tout en étant séparés les uns des autres par un certain écart angulaire, autour d'un arbre d'entraînement (9) central. Ces pistons reposent, grâce à des ressorts (25) soumis à une pré-tension, contre la surface périphérique de l'arbre d'entraînement (9), par leurs extrémités se trouvant radialement à l'intérieur et sont chacun guidés de façon à pouvoir coulisser axialement dans un alésage de guidage. Ces pistons de pompe (19) délimitent avec leur face opposée à l'arbre d'entraînement (9) chacun une chambre de travail de pompe (21), dans l'alésage de guidage (17), chambre qui peut être mise en communication, de façon alternée, avec une chambre basse pression remplie de carburant et avec une conduite de refoulement haute pression. Dans cette pompe, pour améliorer l'étanchéité sous haute pression, les alésages de guidage (17) des pistons de pompe (19) et les canaux haute pression (45, 47) sont disposés directement dans un carter de pompe (1) commun aux deux blocs.
PCT/DE1998/000299 1997-04-18 1998-02-03 Pompe a carburant haute pression WO1998048169A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP98909323A EP0931219A1 (fr) 1997-04-18 1998-02-03 Pompe a carburant haute pression
JP10544652A JP2000512715A (ja) 1997-04-18 1998-02-03 燃料高圧ポンプ

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1997116242 DE19716242A1 (de) 1997-04-18 1997-04-18 Kraftstoffhochdruckpumpe
DE19716242.8 1997-04-18

Publications (1)

Publication Number Publication Date
WO1998048169A1 true WO1998048169A1 (fr) 1998-10-29

Family

ID=7826905

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1998/000299 WO1998048169A1 (fr) 1997-04-18 1998-02-03 Pompe a carburant haute pression

Country Status (4)

Country Link
EP (1) EP0931219A1 (fr)
JP (1) JP2000512715A (fr)
DE (1) DE19716242A1 (fr)
WO (1) WO1998048169A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1028252A3 (fr) * 1999-02-11 2001-01-24 Delphi Technologies, Inc. Pompe à pistons radiaux
WO2009059835A2 (fr) 2007-11-06 2009-05-14 Robert Bosch Gmbh Pompe à pistons radiaux à corps de base prismatique pour système d'injection de carburant

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19858861A1 (de) * 1998-12-19 2000-06-29 Bosch Gmbh Robert Common-Rail-System für Brennkraftmaschinen
DE19859188B4 (de) * 1998-12-21 2013-11-21 Continental Automotive Gmbh Hochdruckpumpe
DE19946842C2 (de) 1999-09-30 2001-08-23 Bosch Gmbh Robert Hochdruckpumpe
IT248791Y1 (it) * 1999-11-30 2003-02-20 Elasis Sistema Ricerca Fiat Pompa a pistoni radiali per l'alimentazione di combustibile ad alta pressione per un motore a combustione interna.
US6520755B1 (en) * 2000-10-10 2003-02-18 Beckman Coulter, Inc. Fluid-moving device with integrated valve
DE10247142A1 (de) * 2002-10-09 2004-04-22 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102008041536A1 (de) 2008-08-26 2010-03-04 Robert Bosch Gmbh Hochdruckpumpe
US9341151B2 (en) 2011-06-30 2016-05-17 Arens Gmbh Metallbau & Bauschlosserei Fuel pump
EP2726716B1 (fr) 2011-06-30 2016-11-02 Arens GmbH Metallbau & Bauschlosserei Bloc distributeur de carburant
DE102011119520A1 (de) 2011-06-30 2013-01-03 Arens GmbH Metallbau- und Bauschlosserei Motorensystem
DE102011078466A1 (de) 2011-06-30 2013-01-03 Arens GmbH Metallbau- und Bauschlosserei Motorensystem
DE102011119519A1 (de) 2011-06-30 2013-01-03 Arens GmbH Metallbau- und Bauschlosserei Motorensystem

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2678005A (en) * 1949-12-13 1954-05-11 Frank G Campbell High-pressure pump
US2679808A (en) * 1949-04-22 1954-06-01 Bernard M Thun Fluid pressure generator
US3434428A (en) * 1967-06-05 1969-03-25 White Motor Corp Intake control for multiple piston pump
US3578879A (en) * 1969-01-22 1971-05-18 Gillett Tool Co Spring actuated fuel pump for fuel injection systems
DE2243138A1 (de) * 1972-09-01 1974-03-07 Langen & Co Radialkolbenpumpe
DE2845072A1 (de) * 1978-10-16 1980-04-30 Heinrichs & Co Kg Schrauben Un Einschraubzapfen
DE3713677A1 (de) * 1987-04-24 1988-11-17 Teves Gmbh Alfred Schraubverbindung mit einer schraube, einer mutter und einer dichtung
EP0304750A1 (fr) * 1987-08-25 1989-03-01 WEBER S.r.l. Pompe à piston axiaux, particulièrement pompe d'injection de combustible des moteur diesel
US4952121A (en) 1987-08-25 1990-08-28 Weber S.R.L. Radial piston pump with means preventing ovalization of piston chamber

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2679808A (en) * 1949-04-22 1954-06-01 Bernard M Thun Fluid pressure generator
US2678005A (en) * 1949-12-13 1954-05-11 Frank G Campbell High-pressure pump
US3434428A (en) * 1967-06-05 1969-03-25 White Motor Corp Intake control for multiple piston pump
US3578879A (en) * 1969-01-22 1971-05-18 Gillett Tool Co Spring actuated fuel pump for fuel injection systems
DE2243138A1 (de) * 1972-09-01 1974-03-07 Langen & Co Radialkolbenpumpe
DE2845072A1 (de) * 1978-10-16 1980-04-30 Heinrichs & Co Kg Schrauben Un Einschraubzapfen
DE3713677A1 (de) * 1987-04-24 1988-11-17 Teves Gmbh Alfred Schraubverbindung mit einer schraube, einer mutter und einer dichtung
EP0304750A1 (fr) * 1987-08-25 1989-03-01 WEBER S.r.l. Pompe à piston axiaux, particulièrement pompe d'injection de combustible des moteur diesel
US4952121A (en) 1987-08-25 1990-08-28 Weber S.R.L. Radial piston pump with means preventing ovalization of piston chamber

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1028252A3 (fr) * 1999-02-11 2001-01-24 Delphi Technologies, Inc. Pompe à pistons radiaux
US6302659B1 (en) 1999-02-11 2001-10-16 Stephen Michael Parker Multi-chamber positive displacement pump
WO2009059835A2 (fr) 2007-11-06 2009-05-14 Robert Bosch Gmbh Pompe à pistons radiaux à corps de base prismatique pour système d'injection de carburant
WO2009059835A3 (fr) * 2007-11-06 2009-06-25 Bosch Gmbh Robert Pompe à pistons radiaux à corps de base prismatique pour système d'injection de carburant

Also Published As

Publication number Publication date
EP0931219A1 (fr) 1999-07-28
JP2000512715A (ja) 2000-09-26
DE19716242A1 (de) 1998-10-22

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